CN111894917A - Hydraulic control device and system - Google Patents
Hydraulic control device and system Download PDFInfo
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- CN111894917A CN111894917A CN201910370722.9A CN201910370722A CN111894917A CN 111894917 A CN111894917 A CN 111894917A CN 201910370722 A CN201910370722 A CN 201910370722A CN 111894917 A CN111894917 A CN 111894917A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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Abstract
The invention provides a hydraulic control device and system, the device includes: the end A of the proportional servo valve is connected with one end of the second hydraulic control one-way valve, the end B of the proportional servo valve is connected with one end of the third hydraulic control one-way valve, and the end P of the proportional servo valve is connected with one end of the first hydraulic control one-way valve; x ends of the first hydraulic control one-way valve, the second hydraulic control one-way valve and the third hydraulic control one-way valve are connected with an end A of the two-position three-way electromagnetic valve; the end A of the first two-position four-way electromagnetic valve is connected with one end of a fourth hydraulic control one-way valve; the end B of the second two-position four-way electromagnetic valve is connected with one end of a fifth hydraulic control one-way valve; the P ends of the first two-position four-way electromagnetic valve and the second two-position four-way electromagnetic valve are connected with a first hydraulic source port; the P end of the two-position three-way electromagnetic valve is connected with the port of a second hydraulic source; two ends of the fourth hydraulic control one-way valve are connected with the first main path, and the X end is connected with one end of the fifth hydraulic control one-way valve and the B end of the second two-position four-way electromagnetic valve; the second end of the fifth hydraulic control one-way valve is connected with the second main path, and the X end is connected with one end of the fourth hydraulic control one-way valve and the A end of the first two-position four-way electromagnetic valve, so that the function of quickly reaching the position can be realized.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a hydraulic control device and system.
Background
The competition of the current market is the competition of technology and efficiency, and the diversity, high quality, high specification and high standard are pursued in the planning and design of new products, so that higher requirements are put forward on production equipment of the products, energy conservation, high efficiency, high precision and maintenance-free are needed, multiple functions and multiple yield are required on one machine on the diversity and high quality of the products, and a great deal of superposition and expansion are realized on the parameter control. The existing production equipment is mostly controlled by a single loop, such as a loop formed by conventional valves, and has the defects of low precision, low automation degree, poor stability, complex structure and the like; although the loop formed by the proportional servo valves is guaranteed in single pressure or position control precision, the loop is difficult to give consideration to multiple parameter control superposition and occasions suitable for multiple working conditions, and the production link is difficult to be guaranteed not to be interrupted. If a plurality of sets of proportional servo loops are configured to realize the accurate control of each parameter, the investment waste and the maintenance operation aggravation are caused.
Disclosure of Invention
The embodiment of the invention mainly aims to provide a hydraulic control device and a hydraulic control system, so as to realize a function of quickly locating, ensure that a production link is not interrupted, improve the working efficiency and reduce the maintenance cost.
In order to achieve the above object, an embodiment of the present invention provides a hydraulic control device, which is connected to a hydraulic source and a hydraulic cylinder, respectively, and includes:
the hydraulic control system comprises a proportional servo valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve, a first two-position four-way electromagnetic valve, a second two-position four-way electromagnetic valve, a two-position three-way electromagnetic valve, a fourth hydraulic control one-way valve, a fifth hydraulic control one-way valve, a first hydraulic source port, a second hydraulic source port and a fourth hydraulic source port which are connected with a hydraulic source, and a first hydraulic cylinder port and a second hydraulic cylinder port which are connected with a hydraulic cylinder;
the port A of the proportional servo valve is connected with the first end of the second hydraulic control one-way valve, the port B of the proportional servo valve is connected with the first end of the third hydraulic control one-way valve, the port P of the proportional servo valve is connected with the first end of the first hydraulic control one-way valve, and the port T of the proportional servo valve is connected with the fourth hydraulic source port;
the second end of the first hydraulic control one-way valve is connected with a second hydraulic source port;
the second end of the second hydraulic control one-way valve is connected with the port of the first hydraulic cylinder; a pipeline between the second end of the second hydraulic control one-way valve and the port of the first hydraulic cylinder is a first main pipeline;
the second end of the third hydraulic control one-way valve is connected with the port of the second hydraulic cylinder; a pipeline between the second end of the third hydraulic control one-way valve and the port of the second hydraulic cylinder is a second main pipeline;
the X port of the first hydraulic control one-way valve, the X port of the second hydraulic control one-way valve and the X port of the third hydraulic control one-way valve are connected with the A port of the two-position three-way electromagnetic valve;
the port A of the first two-position four-way electromagnetic valve is connected with the first end of the fourth hydraulic control one-way valve;
the port B of the second two-position four-way electromagnetic valve is connected with the first end of the fifth hydraulic control one-way valve;
the P port of the first two-position four-way solenoid valve and the P port of the second two-position four-way solenoid valve are connected with a first hydraulic source port, and the T port of the first two-position four-way solenoid valve, the T port of the second two-position four-way solenoid valve and the T port of the second two-position three-way solenoid valve are connected with a fourth hydraulic source port;
the P port of the two-position three-way electromagnetic valve is connected with the port of the second hydraulic source;
the second end of the fourth hydraulic control one-way valve is connected with the first main path, and the X port of the fourth hydraulic control one-way valve is connected with the first end of the fifth hydraulic control one-way valve and the B port of the second two-position four-way electromagnetic valve;
the second end of the fifth hydraulic control one-way valve is connected with the second main path, and the X port of the fifth hydraulic control one-way valve is connected with the first end of the fourth hydraulic control one-way valve and the A port of the first two-position four-way electromagnetic valve.
In one embodiment, the method further comprises the following steps: a first check valve;
and a first end of the first check valve is connected with a T port of the proportional servo valve, and a second end of the first check valve is connected with a fourth hydraulic source port.
In one embodiment, the method further comprises the following steps: a second one-way valve;
and a first end of the second one-way valve is connected with a T port of the two-position three-way electromagnetic valve, and a second end of the second one-way valve is connected with a fourth hydraulic source port.
In one embodiment, a pipeline between the T port of the proportional servo valve and the first end of the first one-way valve is a third main pipeline;
the hydraulic control apparatus further includes: a third check valve, a fourth check valve and a safety valve;
the first end of the third one-way valve is connected with the first main path, and the second end of the third one-way valve is connected with the first end of the safety valve;
the first end of the fourth one-way valve is connected with the second main path, and the second end of the fourth one-way valve is connected with the first end of the safety valve and the second end of the third one-way valve;
and the second end of the safety valve is connected with the third main path.
In one embodiment, the method further comprises the following steps: a third hydraulic source port;
and the Y port of the first hydraulic control one-way valve, the Y port of the second hydraulic control one-way valve and the Y port of the third hydraulic control one-way valve are connected with a third hydraulic source port.
In one embodiment, the method further comprises the following steps:
an electrical interface;
the proportional servo valve, the first two-position four-way electromagnetic valve, the second two-position four-way electromagnetic valve and the two-position three-way electromagnetic valve are all connected with an external electric control device through electric interfaces.
In one embodiment, when the first two-position four-way solenoid valve is powered on, the port A of the first two-position four-way solenoid valve is connected with the port T of the first two-position four-way solenoid valve, and the port B of the first two-position four-way solenoid valve is connected with the port P of the first two-position four-way solenoid valve;
when the first two-position four-way solenoid valve is powered off, the port A of the first two-position four-way solenoid valve is connected with the port P of the first two-position four-way solenoid valve, and the port B of the first two-position four-way solenoid valve is connected with the port T of the first two-position four-way solenoid valve.
In one embodiment, when the second two-position four-way solenoid valve is electrified, the port B of the second two-position four-way solenoid valve is connected with the port P of the second two-position four-way solenoid valve, and the port A of the second two-position four-way solenoid valve is connected with the port T of the second two-position four-way solenoid valve;
when the second two-position four-way solenoid valve is de-energized, the port B of the second two-position four-way solenoid valve is connected with the port T of the second two-position four-way solenoid valve, and the port A of the second two-position four-way solenoid valve is connected with the port P of the second two-position four-way solenoid valve.
In one embodiment, when the two-position three-way electromagnetic valve is electrified, the port A of the two-position three-way electromagnetic valve is connected with the port P of the two-position three-way electromagnetic valve;
when the two-position three-way electromagnetic valve is powered off, the A port of the two-position three-way electromagnetic valve is connected with the T port of the two-position three-way electromagnetic valve.
In one embodiment, when the proportional servo valve is powered off, the port A of the proportional servo valve and the port B of the proportional servo valve are both connected with the port T of the proportional servo valve;
when the electric signal received by the proportional servo valve through the electric interface is in a first preset range, the port A of the proportional servo valve is connected with the port T of the proportional servo valve, and the port B of the proportional servo valve is connected with the port P of the proportional servo valve;
when the electric signal received by the proportional servo valve through the electric interface is in a second preset range, the port A of the proportional servo valve is connected with the port P of the proportional servo valve, and the port B of the proportional servo valve is connected with the port T of the proportional servo valve.
The hydraulic control device of the embodiment of the invention comprises: proportional servo valve, first liquid accuse check valve, the second liquid accuse check valve, the third liquid accuse check valve, first two-position four-way solenoid valve, the second two-position four-way solenoid valve, two-position three-way solenoid valve, the fourth liquid accuse check valve, the fifth liquid accuse check valve, the first hydraulic pressure source port of being connected with the hydraulic pressure source, second hydraulic pressure source port and fourth hydraulic pressure source port, and the first pneumatic cylinder port and the second pneumatic cylinder port of being connected with the pneumatic cylinder, can realize the function of targetting in place fast, guarantee that the production link is not interrupted, the operating efficiency is promoted, the maintenance cost is reduced.
An embodiment of the present invention further provides a hydraulic control system, including:
the hydraulic control apparatus, the hydraulic pressure source, and the hydraulic cylinder as described above;
the hydraulic source is connected with the first hydraulic source port, the second hydraulic source port and the fourth hydraulic source port;
the hydraulic cylinder is connected with the first hydraulic cylinder port and the second hydraulic cylinder port.
The hydraulic control system of the embodiment of the invention comprises the hydraulic control device, a hydraulic source and a hydraulic cylinder; the hydraulic source is connected with the first hydraulic source port, the second hydraulic source port and the fourth hydraulic source port; the hydraulic cylinder is connected with the first hydraulic cylinder port and the second hydraulic cylinder port, so that the function of quickly achieving the aim can be realized, the production link is guaranteed not to be interrupted, the operation efficiency is improved, and the maintenance cost is reduced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained based on these drawings without creative efforts.
FIG. 1 is a schematic diagram of a hydraulic control apparatus and system according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of a hydraulic control apparatus and system according to a second embodiment of the present invention;
FIG. 3 is a schematic diagram of a hydraulic control apparatus and system according to a third embodiment of the present invention;
FIG. 4 is a schematic diagram of a hydraulic control apparatus and system according to a fourth embodiment of the present invention;
FIG. 5 is a block diagram of position control according to an embodiment of the present invention;
FIG. 6 is a block diagram of pressure control according to an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In view of the difficulty in ensuring that the production link is not interrupted and the maintenance cost is high in the existing production equipment, the embodiment of the invention provides the hydraulic control device to realize the function of quickly achieving the target position, ensure that the production link is not interrupted, improve the operation efficiency and reduce the maintenance cost. The present invention will be described in detail below with reference to the accompanying drawings.
Fig. 1 is a schematic diagram of a hydraulic control apparatus and system according to a first embodiment of the present invention. As shown in fig. 1, the hydraulic control apparatus is connected to a hydraulic pressure source 19 and a hydraulic cylinder 20, respectively, and includes:
the hydraulic control system comprises a proportional servo valve 1, a first hydraulic control one-way valve 2, a second hydraulic control one-way valve 3, a third hydraulic control one-way valve 4, a first two-position four-way electromagnetic valve 7, a second two-position four-way electromagnetic valve 8, a two-position three-way electromagnetic valve 9, a fourth hydraulic control one-way valve 10, a fifth hydraulic control one-way valve 11, a first hydraulic source port 100, a second hydraulic source port 200 and a fourth hydraulic source port 400 which are connected with a hydraulic source 19, and a first hydraulic cylinder port 500 and a second hydraulic cylinder port 600 which are connected with a hydraulic cylinder 20.
Wherein the first hydraulic source port 100 is connected to the P of the hydraulic source 191Interface second Hydraulic Source Port 200 with P of Hydraulic Source 192The interface connection, the T interface connection of fourth hydraulic pressure source port 400 and hydraulic pressure source 19, the Ac interface connection of first pneumatic cylinder port 500 and pneumatic cylinder 20, the Bc interface connection of second pneumatic cylinder port 600 and pneumatic cylinder 20. P1Interface and P2The interfaces are high-pressure interfaces with different pressures respectively, and the T interface is an oil return interface. The hydraulic cylinder 20 is installed on a mechanical device to be controlled, and the specification and performance of the hydraulic cylinder 20 are verified and calculated, so that the single body characteristic and the valve control cylinder characteristic meet the requirements.
The port A of the proportional servo valve 1 is connected with the first end of the second hydraulic control one-way valve 3, the port B of the proportional servo valve 1 is connected with the first end of the third hydraulic control one-way valve 4, the port P of the proportional servo valve 1 is connected with the first end of the first hydraulic control one-way valve 2, and the port T of the proportional servo valve 1 is connected with the fourth hydraulic source port 400. The proportional servo valve 1 may be a normal proportional valve, a servo valve or a high frequency response proportional valve interposed between a proportional valve and a servo valve.
A second end of the first pilot operated check valve 2 is connected to the second hydraulic pressure source port 200.
The second end of the second hydraulic control one-way valve 3 is connected with the first hydraulic cylinder port 500; a pipeline between the second end of the second hydraulic check valve 3 and the first cylinder port 500 is a first main path.
The second end of the third pilot-controlled check valve 4 is connected with the second hydraulic cylinder port 600; the pipeline between the second end of the third pilot-controlled check valve 4 and the second hydraulic cylinder port 600 is a second main pipeline.
The X port of the first hydraulic control one-way valve 2, the X port of the second hydraulic control one-way valve 3 and the X port of the third hydraulic control one-way valve 4 are connected with the A port of the two-position three-way electromagnetic valve 9. As shown in fig. 1, the X port of the first pilot-operated check valve 2, the X port of the second pilot-operated check valve 3, and the X port of the third pilot-operated check valve 4 may be merged into a pipeline, and then connected to the a port of the two-position three-way solenoid valve 9, where the pipeline is an X oil path.
The port A of the first two-position four-way electromagnetic valve 7 is connected with the first end of the fourth hydraulic control one-way valve 10; a branch formed by the first two-position four-way electromagnetic valve 7, the fourth hydraulic control one-way valve 10 and connecting pipelines thereof is a first compensation oil way.
The port B of the second two-position four-way electromagnetic valve 8 is connected with the first end of a fifth hydraulic control one-way valve 11; and a branch consisting of the second two-position four-way electromagnetic valve 8, the fifth hydraulic control one-way valve 11 and a connecting pipeline thereof is a second compensation oil way.
The P port of the first two-position four-way solenoid valve 7 and the P port of the second two-position four-way solenoid valve 8 are connected with a first hydraulic source port 100, and the T port of the first two-position four-way solenoid valve 7, the T port of the second two-position four-way solenoid valve 8 and the T port of the second two-position three-way solenoid valve 9 are connected with a fourth hydraulic source port 400.
The P port of the two-position three-way solenoid valve 9 is connected to the second hydraulic pressure source port 200.
The second end of the fourth pilot-controlled check valve 10 is connected with the first main path, and the X port of the fourth pilot-controlled check valve 10 is connected with the first end of the fifth pilot-controlled check valve 11 and the B port of the second two-position four-way solenoid valve 8.
The second end of the fifth pilot-controlled check valve 11 is connected with the second main path, and the X port of the fifth pilot-controlled check valve 11 is connected with the first end of the fourth pilot-controlled check valve 10 and the A port of the first two-position four-way electromagnetic valve 7.
Fig. 2 is a schematic diagram of a hydraulic control apparatus and system according to a second embodiment of the present invention. As shown in fig. 2, the hydraulic control apparatus further includes:
a first check valve 5; a first end of the first check valve 5 is connected to the T port of the proportional servo valve 1, and a second end of the first check valve 5 is connected to the fourth hydraulic pressure source port 400.
A second check valve 6; a first end of the second check valve 6 is connected to the T port of the two-position three-way solenoid valve 9, and a second end of the second check valve 6 is connected to the fourth hydraulic source port 400.
And a pipeline between the T port of the proportional servo valve 1 and the first end of the first one-way valve 5 is a third main path. And a pipeline between the P port of the proportional servo valve 1 and the first end of the first pilot-controlled check valve 2 is a fourth main pipeline. And a loop formed by the first main path, the second main path, the third main path and the fourth main path is a main control loop. The proportional servo valve 1 operates a control master loop to achieve a master control function.
Fig. 3 is a schematic diagram of a hydraulic control apparatus and system according to a third embodiment of the present invention. As shown in fig. 3, the hydraulic control apparatus further includes:
a third check valve 12, a fourth check valve 13 and a relief valve 14.
A first end of the third check valve 12 is connected to the first main circuit and a second end of the third check valve 12 is connected to a first end of the relief valve 14.
A first end of the fourth check valve 13 is connected to the second main circuit, and a second end of the fourth check valve 13 is connected to a first end of the relief valve 14 and a second end of the third check valve 12. As shown in fig. 3, a second end of the third check valve 12 and a second end of the fourth check valve 13 are combined and connected to a first end of the relief valve 14.
A second end of the relief valve 14 is connected to the third main passage.
And a branch formed by the third check valve 12, the fourth check valve 13, the safety valve 14 and a connecting pipeline thereof is a pressure relief oil path. When the pressure of the first main path or the second main path is released due to the fact that the pressure of the first main path or the second main path exceeds the set pressure of the safety valve, the first main path or the second main path and the pressure release oil path form an oil release loop, and oil release is carried out to achieve the pressure release function in order to guarantee that the hydraulic control device can work normally.
Fig. 4 is a schematic diagram of a hydraulic control apparatus and system according to a fourth embodiment of the present invention. As shown in fig. 4, the hydraulic control apparatus further includes: and a third hydraulic source port 300. The third hydraulic source port 300 is connected to an L interface of the hydraulic source 19, and the L interface is an oil drainage interface.
The Y port of the first pilot-controlled check valve 2, the Y port of the second pilot-controlled check valve 3 and the Y port of the third pilot-controlled check valve 4 are all connected with a third hydraulic source port 300. As shown in fig. 4, the Y port of the first pilot check valve 2, the Y port of the second pilot check valve 3, and the Y port of the third pilot check valve 4 may be connected to the third hydraulic source port 300 for a drain operation after being merged into one line.
In one embodiment, the hydraulic control apparatus further includes: an electrical interface 16; the proportional servo valve 1, the first two-position four-way solenoid valve 7, the second two-position four-way solenoid valve 8 and the two-position three-way solenoid valve 9 are all connected with an external electric control device through an electric interface 16.
In specific implementation, when the electromagnet on the a side of the first two-position four-way solenoid valve 7 is electrified, the port A of the first two-position four-way solenoid valve 7 is connected with the port T of the first two-position four-way solenoid valve 7, and the port B of the first two-position four-way solenoid valve 7 is connected with the port P of the first two-position four-way solenoid valve 7; when the electromagnet on the a side of the first two-position four-way solenoid valve 7 loses power, the port A of the first two-position four-way solenoid valve 7 is connected with the port P of the first two-position four-way solenoid valve 7, and the port B of the first two-position four-way solenoid valve 7 is connected with the port T of the first two-position four-way solenoid valve 7.
When the electromagnet on the a side of the second two-position four-way solenoid valve 8 is electrified, the port B of the second two-position four-way solenoid valve 8 is connected with the port P of the second two-position four-way solenoid valve 8, and the port A of the second two-position four-way solenoid valve 8 is connected with the port T of the second two-position four-way solenoid valve 8; when the electromagnet on the a side of the second two-position four-way solenoid valve 8 is de-energized, the port B of the second two-position four-way solenoid valve 8 is connected to the port T of the second two-position four-way solenoid valve 8, and the port A of the second two-position four-way solenoid valve 8 is connected to the port P of the second two-position four-way solenoid valve 8.
When the first two-position four-way solenoid valve 7 and the second two-position four-way solenoid valve 8 are powered on or powered off at the same time, the hydraulic cylinders 20 located at the tail ends of the first main path and the second main path are both caused to act, so that a pipeline formed by the first compensation oil path, the second compensation oil path, the first main path, the second main path and the hydraulic cylinders 20 is called an auxiliary action loop, and the function realized by the auxiliary action loop is an auxiliary control function.
When the first compensation oil path is connected with the second compensation oil path1When the interface has the accident power source function, the control mode that the hydraulic control device can carry out accident operation according to the set requirement in the accident state is an accident control function. When the first two-position four-way solenoid valve 7 on the first compensation oil path is electrified and the second two-position four-way solenoid valve 8 on the second compensation oil path is not electrified, P1The pressure oil source of the interface is respectively stopped by the first two-position four-way electromagnetic valve 7 and the second two-position four-way electromagnetic valve 8, and cannot enter the first compensation oil path and the second compensation oil path, and the check function of the fourth hydraulic control one-way valve 10 and the fifth hydraulic control one-way valve 11 is started. If the check function of the pilot operated check valves located on the first main path and the second main path is also activated at this time, the hydraulic cylinder 20 is locked, and the manner in which the hydraulic cylinder 20 is statically braked is controlled as the locking function.
When the electromagnet on the b side of the two-position three-way electromagnetic valve 9 is electrified, the port a of the two-position three-way electromagnetic valve 9 is connected with the port P of the two-position three-way electromagnetic valve 9, at this time, oil from the first hydraulic source port 100 enters the port X of the first hydraulic control one-way valve 2, the port X of the second hydraulic control one-way valve 3 and the port X of the third hydraulic control one-way valve 4, and the check function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4 fails. When the electromagnet on the side b of the two-position three-way electromagnetic valve 9 is powered off, the port A of the two-position three-way electromagnetic valve 9 is connected with the port T of the two-position three-way electromagnetic valve 9, at the moment, oil returns through a pipeline connected with the port X of the first hydraulic control one-way valve 2, the port X of the second hydraulic control one-way valve 3 and the port X of the third hydraulic control one-way valve 4, and the check function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4; therefore, a pipeline formed by the two-position three-way electromagnetic valve 9, the X port of the first hydraulic control one-way valve 2, the X port of the second hydraulic control one-way valve 3 and the X port of the third hydraulic control one-way valve 4 is set as an external control loop.
When the proportional servo valve 1 is powered off or the valve core returns to the middle position, the port A of the proportional servo valve 1 and the port B of the proportional servo valve 1 are both connected with the port T of the proportional servo valve 1. As shown in fig. 4, when the electric signal received by the proportional servo valve 1 through the electric interface 16 is within a first preset range, the proportional servo valve 1 is in the C state, at this time, the port a of the proportional servo valve 1 is connected to the port T of the proportional servo valve 1, and the port B of the proportional servo valve 1 is connected to the port P of the proportional servo valve 1; when the electric signal received by the proportional servo valve 1 through the electric interface 16 is within the second preset range, the proportional servo valve 1 is in the D state, at this time, the port a of the proportional servo valve 1 is connected to the port P of the proportional servo valve 1, and the port B of the proportional servo valve 1 is connected to the port T of the proportional servo valve 1.
As shown in fig. 4, the hydraulic control apparatus further includes: a displacement sensor 15 located on the hydraulic cylinder 20, a first pressure sensor 17 connected to the first main circuit, and a second pressure sensor 18 connected to the first main circuit. FIG. 5 is a block diagram of position control according to an embodiment of the present invention. FIG. 6 is a block diagram of pressure control according to an embodiment of the present invention. As shown in fig. 5, the position control flow is: the first slope curve 21 is input, the first slope curve 21 is adjusted according to a calibration value and a feedback value of the displacement sensor 15, and an electric signal is output to the proportional servo valve 1 after passing through the PI pressure regulator 22 and the limiter 23. The proportional servo valve 1 amplifies the electrical signal by an amplifier (not shown in fig. 4), and the amplified electrical signal controls an electromagnet of the proportional servo valve 1 to realize a position control function.
As shown in fig. 6, the pressure control flow is: the second slope curve 24 is input, the second slope curve 24 is adjusted according to a calibration value and a feedback value of the first pressure sensor 17 (or the second pressure sensor 18), and an electric signal is output to the proportional servo valve 1 after passing through the PI pressure regulator 22 and the limiter 23. The proportional servo valve 1 amplifies the electrical signal by an amplifier (not shown in fig. 4), and the amplified electrical signal controls an electromagnet of the proportional servo valve 1 to realize a pressure control function.
The operation process of the application is as follows:
1. the equipment is first repositioned and calibrated. If the hydraulic cylinder 20 is returned, the piston rod is in a retracted state. For example, a first preset range of the electrical signal received by the proportional servo valve 1 is set to be greater than or equal to 4mA, less than 12 mA; the second preset range is set to be greater than 12mA and less than or equal to 20 mA. When the enable signal of the proportional servo valve 1 is turned on, the given value of the electrical signal is 12mA, and the port a of the proportional servo valve 1 and the port B of the proportional servo valve 1 are both connected to the port T of the proportional servo valve 1. The power supply of the first two-position four-way electromagnetic valve 7 is switched on, the electromagnet a is electrified, the valve core is positioned on the left side, and the first compensation oil path is communicated to a T interface for oil return through a fourth hydraulic source port 400; the second two-position four-way solenoid valve 8 and the two-position three-way solenoid valve 9 are powered off, the valve cores of the two-position four-way solenoid valve are in a normal position, and the second compensation oil path and the X oil path are communicated to the T interface through a fourth hydraulic source port 400; the hydraulic cylinder 20 is temporarily in a locked state.
2. And calibrating the sensor. The sensors include a displacement sensor 15, a first pressure sensor 17 and a second pressure sensor 18. The current measurement value can be corresponding to the feedback pulse of the current sensor through a mechanical measurement method, for example, the displacement value of the hydraulic cylinder in the fully retracted state is set to be 0, and the pressure sensor sets the pressure value to be 0.
3. The hydraulic cylinder 20 is rapidly moved to a designated working position. The first two-position four-way electromagnetic valve 7 loses power, the valve core resets, and P of the hydraulic source 191The interface is communicated with the first compensation oil way, the hydraulic medium enters the first compensation oil way from the first two-position four-way electromagnetic valve 7, enters the first main path through the fourth hydraulic control one-way valve 10, and finally enters the rodless cavity of the hydraulic cylinder 20 from the Ac interface. The hydraulic source 19 builds up a working pressure matched to the load due to the load, the piston of the hydraulic cylinder 20 is extended, and the fifth fluid installed on the second compensating fluid path is then dischargedThe check valve 11 opens the reverse function under the action of the high-pressure medium due to the pressure of the first compensation oil path, the check function fails, the hydraulic medium stored in the rod cavity of the hydraulic cylinder 20 flows outwards along with the movement of the piston, flows into the second main path through the Bc interface, flows through the fifth hydraulic control check valve 11, and then flows to the T interface of the hydraulic source 19 through the second two-position four-way electromagnetic valve 8 which is de-energized, so that the function of quick in-place is realized, and the production link is not interrupted.
Wherein there is pressure monitoring or displacement monitoring during the movement of the hydraulic cylinder 20. When the feedback value of the displacement sensor 15, the feedback value of the first pressure sensor 17, or the feedback value of the second pressure sensor 18 reaches a set value, the first two-position four-way solenoid valve 7 is switched from the power-off state to the power-on state, the fourth hydraulic control check valve 10 and the fifth hydraulic control check valve 11 are restored to the one-way communication and reverse check state, and the hydraulic cylinder 20 is rapidly in the locking state. When the first two-position four-way solenoid valve 7 is powered on, the two-position three-way solenoid valve 9 is also powered on, the two-way circulation function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4 is started, and the reverse check function is disabled. The proportional servo valve 1 may be controlled by a feedback value of the displacement sensor 15 to implement a position control function, and the proportional servo valve 1 may be controlled by a feedback value of the first pressure sensor 17 or a feedback value of the second pressure sensor 18 to implement a pressure control function. The slope curve, calibration value, PI adjusting gain and the like can be parameterized on an external human-computer interface in both position control and pressure control. In addition, a fault alarm signal prompt, a fault removal method prompt, a traceable record query window and the like are also arranged on the human-computer interface.
After the fault is prompted, if a fault of the displacement sensor 15, a fault of the first pressure sensor 17, a fault of the second pressure sensor 18 or a fault of the proportional servo valve 1 which cannot be eliminated within a given time range is encountered, the hydraulic control device automatically switches to a compensation oil circuit for control. At the moment, the two-position three-way electromagnetic valve 9 is de-energized, the two-way circulation function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4 is closed, the locking function is started, the valve core of the proportional servo valve 1 is reset, and the second hydraulic control one-way valve 4 is openedThe two-position four-way electromagnetic valve 7 is switched from an electrified state to an unpowered state, the fifth hydraulic control one-way valve 11 starts the two-way circulation function, and a rodless cavity of the hydraulic cylinder 20 enters a high-pressure medium to ensure that the load does not lose the driving force. P of the hydraulic source 19 if the load requires a particular pressure1The interface can also be switched in to a particular pressure.
4. The device is reset quickly. The quick resetting of the device is required before the position control or the pressure control is finished. At this time, the two-position three-way electromagnetic valve 9 is de-energized, the two-way circulation function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4 is closed, and the locking function is started. The given value of the electric signal of the proportional servo valve 1 is 12mA, and the valve core is reset. The first two-position four-way electromagnetic valve 7 is kept electrified, the second two-position four-way electromagnetic valve 8 is switched from an electrified state to an electrified state, and the P of the hydraulic source 191The interface is communicated with a second compensation oil path, a hydraulic medium enters the second compensation oil path from the second two-position four-way solenoid valve 8, enters a second main path through the fifth hydraulic control one-way valve 11, and finally enters the rod cavity of the hydraulic cylinder 20 from the Bc interface of the hydraulic cylinder 20. Due to the load, the hydraulic pressure source 19 builds up a working pressure matching the load, driving the piston of the hydraulic cylinder 20 to retract. At this time, the fourth hydraulic control check valve 10 installed on the first compensation oil path has the reverse function opened by the X port thereof under the action of the high-pressure medium due to the pressure of the second compensation oil path, and the check function is disabled. The hydraulic medium stored in the rod-less chamber of the hydraulic cylinder 20 at this time flows out as the piston moves, flows into the first main passage through the Ac port, flows through the fourth pilot-operated check valve 10, and then flows into the T port through the a port and the T port of the first two-position four-way solenoid valve 7. After the hydraulic cylinder 20 is completely retracted to the right position, the second two-position four-way solenoid valve 8 is kept powered off, the first two-position four-way solenoid valve 7 is kept powered on continuously, and the hydraulic cylinder 20 is in a locking state again.
For example, the hydraulic control device of the embodiment of the invention can be used for a withdrawal and straightening machine of a continuous casting machine. The hydraulic control device provided by the invention needs to be subjected to pressure test and performance test after being manufactured, and is installed in a continuous casting workshop after the test is qualified, the distance between the hydraulic control device and the withdrawal and straightening unit body equipment is as short as possible, and the distance can be measured and is rigid. Meanwhile, a hydraulic cylinder 20 is installed according to the requirement, the specification and the performance of the hydraulic cylinder 20 are verified in the design stage, the hydraulic cylinder 20 is matched with the proportional servo valve 1, and the integral mathematical model is written into an external electric control device. At the same time, the line connections between the hydraulic pressure source 19, the hydraulic control device and the hydraulic cylinder 20 are made. Before use, the pipeline is flushed and pressure tested, the power of the hydraulic source 19 is 18.5Kw, and the output pressure is 20 MPa.
Firstly, carrying out the test of a program and the calibration of a sensor: the end of the hydraulic cylinder 20 is connected with the driving roller, and the fully retracted state of the hydraulic cylinder 20 is an initial position and is defined as a high position according to the process operation instruction. When the displacement sensor 15 is calibrated, the position calibration button is operated, and the first two-position four-way solenoid valve 7 and the second two-position four-way solenoid valve 8 are de-energized, so that the port A of the first two-position four-way solenoid valve 7 is connected with the port P of the first two-position four-way solenoid valve 7, and the port B of the first two-position four-way solenoid valve 7 is connected with the port T of the first two-position four-way solenoid valve 7; the port B of the second two-position four-way solenoid valve 8 is connected with the port T of the second two-position four-way solenoid valve 8, the port A of the second two-position four-way solenoid valve 8 is connected with the port P of the second two-position four-way solenoid valve 8, and the port B of the first two-position four-way solenoid valve 7 and the port A of the second two-position four-way solenoid valve 8 are in a dead-closed state. The hydraulic medium in the second compensating oil path may return to the T-connection of the hydraulic source 19, at which time the hydraulic cylinder 20 is lowered to a predetermined position, ensuring that the drive roller and the calibration block have come into contact and are stressed, and then the thickness of the calibration block is used to correct the output value of the displacement sensor 15, which are linearly matched. The pressure at the first cylinder port 500 and the pressure at the second cylinder port 600 are measured by mechanical pressure gauges, and the readings are used to correct the output of the first pressure sensor 17 and the output of the second pressure sensor 18, respectively, to match linearly.
Then the pressure control or the position control is put into the process flow. The pressure control is to ensure that the casting blank has proper positive pressure at the temperature of 900 ℃ to ensure that the casting blank can be continuously drawn out according to the set speed, in addition, the pressing force cannot be too large, otherwise, the deformation rate of the casting blank is out of tolerance, and the control precision is about +/-0.1 MPa. The first two-position four-way electromagnetic valve 7 is electrified and the second one is in a pressure mode by operating a buttonThe two-position four-way solenoid valve 8 is still in a power-off state, the two-position three-way solenoid valve 9 is powered on, and the proportional servo valve 1 enters an adjusting link according to a preset second preset curve. Both "pressure mode" and "position mode" may be used, depending on the process requirements. The position control aims to improve the quality of the core part of the casting blank and ensure that the shape size of the casting blank is controlled within a tolerance range, and the control precision is about +/-50 mu m. When the position mode is operated, the first two-position four-way solenoid valve 7 is powered on, the second two-position four-way solenoid valve 8 is still in a power-off state, the two-position three-way solenoid valve 9 is powered on, and the proportional servo valve 1 enters an adjusting link according to a preset first slope curve. When the production approaches the end sound, the control panel of the external electric control device is operated, the stop button is pressed, and the driving roller of the tension leveler stops running and starts to rise. The power-on sequence of the electromagnetic valve is as follows: the two-position three-way electromagnetic valve 9 is de-energized, the two-way circulation function of the first hydraulic control one-way valve 2, the second hydraulic control one-way valve 3 and the third hydraulic control one-way valve 4 is closed, the locking function is started, the given value of the proportional servo valve 1 is 12mA, and the valve core returns to the middle position. Meanwhile, the first two-position four-way electromagnetic valve 7 is kept electrified, and the first compensation oil way is communicated with a T interface of the hydraulic source 19; the second two-position four-way electromagnetic valve 8 is switched from the power-off state to the power-on state, and the P of the hydraulic source 191The interface is communicated with the second compensation oil way. After the hydraulic cylinder 20 is completely retracted to the right position, the second two-position four-way solenoid valve 8 is kept powered off, the first two-position four-way solenoid valve 7 is kept powered on continuously, and the hydraulic cylinder 20 is in a locking state again.
Based on the same inventive concept, the embodiment of the invention also provides a hydraulic control system, and as the principle of solving the problems of the system is similar to that of a hydraulic control device, the implementation of the system can be referred to the implementation of the device, and repeated parts are not described again.
As shown in fig. 1 to 4, the hydraulic control system includes the hydraulic control apparatus as described above, a hydraulic pressure source 19 and a hydraulic cylinder 20; the hydraulic pressure source 19 is connected to the first hydraulic pressure source port 100, the second hydraulic pressure source port 200, the third hydraulic pressure source port 300, and the fourth hydraulic pressure source port 400; the hydraulic cylinder 20 is connected with the first hydraulic cylinder port 500 and the second hydraulic cylinder port 600, so that the function of quickly achieving the aim can be realized, the production link is guaranteed not to be interrupted, the operation efficiency is improved, and the maintenance cost is reduced.
In summary, the hydraulic control device and the hydraulic control system of the embodiment of the invention combine the proportional servo system with the conventional system, and can meet various requirements of the production process. If the accident function is adopted, the casting flow is cut off under the condition of power failure, and personal safety and equipment safety are protected; the function of quick in-place saves the time from the shutdown position to the working position, and ensures that the production link synchronous with the shutdown position is not interrupted and is performed orderly; the pressure control function corresponds to the static pressure of the casting flow, and the accurate pressure control ensures that the casting flow is not cut off and the driving force is not lost; and the position control function ensures that the specification size and the deformation rate of the casting are within an acceptable range. The realization of the multiple functions is not the simple accumulation of the redundant loop, but the advantages of the proportional servo system and the conventional system are skillfully utilized to organically combine the functions, compensate each other and depend on each other, so that the operation requirements under the normal working condition and the accident working condition can be completely covered. The multifunctional multi-purpose machine has the advantages that the multifunctional multi-purpose machine and the multi-purpose machine are functionally and completely realized, manual intervention is reduced, the operation efficiency is further improved, the manufacturing cost and the maintenance cost are reduced, the multifunctional multi-purpose machine is suitable for occasions with high-end control precision, and the multifunctional multi-purpose machine is worthy of being popularized and used in multiple industries and multiple fields.
The above-mentioned embodiments are intended to illustrate the objects, technical solutions and advantages of the present invention in further detail, and it should be understood that the above-mentioned embodiments are only exemplary embodiments of the present invention, and are not intended to limit the scope of the present invention, and any modifications, equivalent substitutions, improvements and the like made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (11)
1. A hydraulic control device connected to a hydraulic source (19) and a hydraulic cylinder (20), respectively, comprising:
the hydraulic control system comprises a proportional servo valve (1), a first hydraulic control one-way valve (2), a second hydraulic control one-way valve (3), a third hydraulic control one-way valve (4), a first two-position four-way electromagnetic valve (7), a second two-position four-way electromagnetic valve (8), a two-position three-way electromagnetic valve (9), a fourth hydraulic control one-way valve (10), a fifth hydraulic control one-way valve (11), a first hydraulic source port (100), a second hydraulic source port (200) and a fourth hydraulic source port (400) which are connected with a hydraulic source (19), and a first hydraulic cylinder port (500) and a second hydraulic cylinder port (600) which are connected with a hydraulic cylinder (20);
the port A of the proportional servo valve (1) is connected with the first end of the second hydraulic control one-way valve (3), the port B of the proportional servo valve (1) is connected with the first end of the third hydraulic control one-way valve (4), the port P of the proportional servo valve (1) is connected with the first end of the first hydraulic control one-way valve (2), and the port T of the proportional servo valve (1) is connected with the fourth hydraulic source port (400);
the second end of the first hydraulic control one-way valve (2) is connected with the second hydraulic pressure source port (200);
the second end of the second hydraulic control one-way valve (3) is connected with the first hydraulic cylinder port (500); a pipeline between the second end of the second hydraulic control one-way valve (3) and the first hydraulic cylinder port (500) is a first main pipeline;
the second end of the third hydraulic control one-way valve (4) is connected with the second hydraulic cylinder port (600); a pipeline between the second end of the third hydraulic control one-way valve (4) and the second hydraulic cylinder port (600) is a second main pipeline;
the X port of the first hydraulic control one-way valve (2), the X port of the second hydraulic control one-way valve (3) and the X port of the third hydraulic control one-way valve (4) are connected with the A port of the two-position three-way electromagnetic valve (9);
the port A of the first two-position four-way electromagnetic valve (7) is connected with the first end of the fourth hydraulic control one-way valve (10);
the port B of the second two-position four-way electromagnetic valve (8) is connected with the first end of the fifth hydraulic control one-way valve (11);
a P port of the first two-position four-way solenoid valve (7) and a P port of the second two-position four-way solenoid valve (8) are both connected with the first hydraulic source port (100), and a T port of the first two-position four-way solenoid valve (7), a T port of the second two-position four-way solenoid valve (8) and a T port of the two-position three-way solenoid valve (9) are all connected with the fourth hydraulic source port (400);
the P port of the two-position three-way electromagnetic valve (9) is connected with the second hydraulic source port (200);
the second end of the fourth hydraulic control one-way valve (10) is connected with the first main path, and the X port of the fourth hydraulic control one-way valve (10) is connected with the first end of the fifth hydraulic control one-way valve (11) and the B port of the second two-position four-way electromagnetic valve (8);
the second end of the fifth hydraulic control one-way valve (11) is connected with the second main path, and the X port of the fifth hydraulic control one-way valve (11) is connected with the first end of the fourth hydraulic control one-way valve (10) and the A port of the first two-position four-way electromagnetic valve (7).
2. The hydraulic control apparatus according to claim 1, characterized by further comprising: a first check valve (5);
and a first end of the first check valve (5) is connected with a T port of the proportional servo valve (1), and a second end of the first check valve (5) is connected with the fourth hydraulic source port (400).
3. The hydraulic control apparatus according to claim 1, characterized by further comprising: a second check valve (6);
and the first end of the second one-way valve (6) is connected with the T port of the two-position three-way electromagnetic valve (9), and the second end of the second one-way valve (6) is connected with the fourth hydraulic source port (400).
4. The hydraulic control apparatus according to claim 2,
a pipeline between a T port of the proportional servo valve (1) and a first end of the first one-way valve (5) is a third main pipeline;
the hydraulic control apparatus further includes: a third check valve (12), a fourth check valve (13) and a safety valve (14);
a first end of the third one-way valve (12) is connected to the first main circuit, and a second end of the third one-way valve (12) is connected to a first end of the safety valve (14);
a first end of the fourth one-way valve (13) is connected to the second main circuit, and a second end of the fourth one-way valve (13) is connected to a first end of the safety valve (14) and a second end of the third one-way valve (12);
the second end of the safety valve (14) is connected to the third main path.
5. The hydraulic control apparatus according to claim 1, characterized by further comprising: a third hydraulic source port (300);
and the Y port of the first hydraulic control one-way valve (2), the Y port of the second hydraulic control one-way valve (3) and the Y port of the third hydraulic control one-way valve (4) are all connected with the third hydraulic source port (300).
6. The hydraulic control apparatus according to claim 1, characterized by further comprising:
an electrical interface (16);
the proportional servo valve (1), the first two-position four-way electromagnetic valve (7), the second two-position four-way electromagnetic valve (8) and the two-position three-way electromagnetic valve (9) are all connected with an external electric control device through the electric interface (16).
7. The hydraulic control apparatus of claim 6,
when the first two-position four-way electromagnetic valve (7) is electrified, the port A of the first two-position four-way electromagnetic valve (7) is connected with the port T of the first two-position four-way electromagnetic valve (7), and the port B of the first two-position four-way electromagnetic valve (7) is connected with the port P of the first two-position four-way electromagnetic valve (7);
when the first two-position four-way electromagnetic valve (7) is powered off, the port A of the first two-position four-way electromagnetic valve (7) is connected with the port P of the first two-position four-way electromagnetic valve (7), and the port B of the first two-position four-way electromagnetic valve (7) is connected with the port T of the first two-position four-way electromagnetic valve (7).
8. The hydraulic control apparatus of claim 6,
when the second two-position four-way electromagnetic valve (8) is electrified, the port B of the second two-position four-way electromagnetic valve (8) is connected with the port P of the second two-position four-way electromagnetic valve (8), and the port A of the second two-position four-way electromagnetic valve (8) is connected with the port T of the second two-position four-way electromagnetic valve (8);
when the second two-position four-way electromagnetic valve (8) is powered off, the port B of the second two-position four-way electromagnetic valve (8) is connected with the port T of the second two-position four-way electromagnetic valve (8), and the port A of the second two-position four-way electromagnetic valve (8) is connected with the port P of the second two-position four-way electromagnetic valve (8).
9. The hydraulic control apparatus of claim 6,
when the two-position three-way electromagnetic valve (9) is electrified, the port A of the two-position three-way electromagnetic valve (9) is connected with the port P of the two-position three-way electromagnetic valve (9);
when the two-position three-way electromagnetic valve (9) is powered off, the port A of the two-position three-way electromagnetic valve (9) is connected with the port T of the two-position three-way electromagnetic valve (9).
10. The hydraulic control apparatus of claim 6,
when the proportional servo valve (1) is powered off, the port A of the proportional servo valve (1) and the port B of the proportional servo valve (1) are both connected with the port T of the proportional servo valve (1);
when the electric signal received by the proportional servo valve (1) through the electric interface (16) is in a first preset range, the port A of the proportional servo valve (1) is connected with the port T of the proportional servo valve (1), and the port B of the proportional servo valve (1) is connected with the port P of the proportional servo valve (1);
when the electric signal received by the proportional servo valve (1) through the electric interface (16) is in a second preset range, the port A of the proportional servo valve (1) is connected with the port P of the proportional servo valve (1), and the port B of the proportional servo valve (1) is connected with the port T of the proportional servo valve (1).
11. A hydraulic control system, comprising:
the hydraulic control apparatus according to any one of claims 1 to 10, a hydraulic pressure source (19) and a hydraulic cylinder (20);
the hydraulic source (19) is connected to the first hydraulic source port (100), the second hydraulic source port (200), and the fourth hydraulic source port (400);
the hydraulic cylinder (20) is connected to the first cylinder port (500) and the second cylinder port (600).
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| CN209892537U (en) * | 2019-05-06 | 2020-01-03 | 中冶京诚工程技术有限公司 | Hydraulic control device and system |
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| JPH09133107A (en) * | 1995-11-07 | 1997-05-20 | Tokyo Seimitsu Sokki Kk | Electromagnetic proportional servo valve |
| JP2000297866A (en) * | 1999-04-14 | 2000-10-24 | Amada Eng Center Co Ltd | Rotary servo valve, and hydraulic servo device for punch press using same valve |
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