CN112855637A - High-reliability hydraulic rigid synchronization system and working method thereof - Google Patents
High-reliability hydraulic rigid synchronization system and working method thereof Download PDFInfo
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- CN112855637A CN112855637A CN202011637676.3A CN202011637676A CN112855637A CN 112855637 A CN112855637 A CN 112855637A CN 202011637676 A CN202011637676 A CN 202011637676A CN 112855637 A CN112855637 A CN 112855637A
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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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/22—Synchronisation of the movement of two or more servomotors
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/005—Leakage; Spillage; Hose burst
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Abstract
The invention discloses a high-reliability hydraulic rigid synchronization system and a working method thereof, wherein the system comprises an electromagnetic directional valve, a balance valve, N hydraulic control one-way valves, N overflow valves and N oil cylinders, an A port of the electromagnetic directional valve is communicated with a pilot port of the balance valve, a pilot port of each hydraulic control one-way valve and a rod cavity of each oil cylinder, a B port of the electromagnetic directional valve is communicated with an oil inlet of the balance valve, a load port of the balance valve is communicated with an oil inlet of each hydraulic control one-way valve, a load port of each hydraulic control one-way valve is communicated with a rodless cavity of the corresponding oil cylinder, an oil inlet of each overflow valve is communicated with a load port of the corresponding hydraulic control one-way valve and a rodless cavity of the corresponding oil cylinder, a pressure sensor is arranged between an oil inlet of the N hydraulic control one-way valves and the load port of the balance valve. The invention realizes rigid synchronization of a plurality of oil cylinders by using a conventional hydraulic element, has high synchronization precision and high safety, is not influenced by environmental temperature change, considers two working modes of large flow of the electric pump and small flow of the manual pump and has high integral reliability.
Description
Technical Field
The invention belongs to the technical field of hydraulic pressure, and particularly relates to a high-reliability hydraulic rigid synchronization system and a working method thereof.
Background
In some hydraulic lifting and lodging mechanisms of large heavy-duty equipment, two cylinders or multiple cylinders are adopted for driving simultaneously in order to realize larger thrust. Two cylinders or multiple cylinders need synchronous action to ensure that the mechanism can stably and safely operate. Meanwhile, in many fields, particularly military fields, hard requirements are placed on the environmental temperature adaptability of equipment and the manual emergency operation function under the condition of power loss, and a hydraulic system still needs to ensure good synchronization precision under the conditions.
Synchronous control in the prior hydraulic technology generally adopts synchronous motor synchronization, proportional speed regulating valve and position sensor closed-loop control synchronization and rigid synchronization.
Synchronous motors synchronously utilize equal output flow of all output ports of the motors to realize synchronization, the price of the synchronous motors is high, and due to mechanical manufacturing errors, internal leakage and the like, inherent errors exist in the output flow among all the output ports of the synchronous motors, and the errors are accumulated, so that the synchronization errors are overlarge finally. Meanwhile, the flow of the inlet of the synchronous motor has a limited range, and the flow of the manual pump is far lower than that of the electric pump, so that the limited range of the flow of the inlet of the synchronous motor cannot cover the flow of the electric pump and the flow of the manual pump, so that the synchronous precision is greatly reduced during manual emergency operation, and the risk of damaging equipment is caused.
The proportional speed regulating valve is in closed-loop control synchronization with the position sensor, the position sensor is installed on each oil cylinder, and the proportional speed regulating valve is used for independently controlling the speed of each oil cylinder, so that the displacement of each oil cylinder is the same, and synchronization is guaranteed. The method has high synchronization precision, but increases the number of valves and sensors, and has higher cost and lower reliability. And under the condition of power loss, the proportional speed regulating valve and the sensor cannot work, and manual emergency operation cannot be carried out.
The rigid synchronization utilizes a rigid mechanism to rigidly connect two or more oil cylinders with oil passages connected in parallel, and the flow is not actively controlled. When two or more oil cylinder pistons are in a stress balance state, the oil cylinder pistons perform uniform linear motion, and the oil cylinders act synchronously. When any one oil cylinder piston is unbalanced in stress to generate acceleration, the oil cylinders start to move asynchronously, the rigid connecting mechanism between the oil cylinders is elastically deformed, the elastic stress generated along with the elastic deformation enables the oil cylinder piston to be balanced in stress, and the oil cylinders restore to move synchronously. The rigid synchronization structure is simple, the precision is high, the cost is low, and the flow size has no influence on the synchronization precision.
Under the condition that the elastic stress required by the stress balance of the oil cylinder piston of the rigid synchronous mechanism is certain, the higher the rigidity of the mechanism is, the smaller the elastic deformation amount is, and the higher the synchronous precision is. Because self weight is great, in order to prevent that equipment from warping and improving stability, the overall rigidity is very high in the design, in order to satisfy the requirement that can manual emergency operation, is fit for adopting the rigidity synchronization mode simultaneously. The smaller the stress difference between two or more oil cylinder pistons of the rigid synchronization mechanism is, the smaller the elastic stress required by stress balance is, the smaller the elastic deformation of the mechanism is, and the higher the synchronization precision is. In order to minimize the stress difference between two or more oil cylinder pistons, the rigid synchronization generally adopts an equal-load and equal-pressure design. The load of the equipment is uniformly distributed on the structure, and the oil cylinders are uniformly distributed relative to the load, so that the load force acting on the piston of each oil cylinder is equal. The hydraulic schematic diagram of the existing hydraulic rigid synchronous system is shown in fig. 1, two oil cylinders have the same specification, oil paths are connected in parallel, rod cavities are communicated with each other, a rodless cavity is a bearing cavity, two oil cylinder rodless cavities are respectively provided with a balance valve as a safety and speed control valve, and the rodless cavities are communicated with each other after passing through the balance valves. When the lifting mechanism is lifted, the oil cylinders extend out, the oil passages of the rodless cavities are pressurized, the balance valves are opened in the positive direction, the opening pressure is very low, the pressure loss and the difference caused by the pressure loss can be ignored, the pressure of the rodless cavities of the two cylinders is equal, and the thrust of the rodless cavities is equal. When the device is laid down, the oil cylinders retract, the oil passages with rod cavities pressurize, the rod cavities of the two cylinders are communicated with each other, the pressure is equal, and the thrust of the rod cavities is equal. When the equipment is lodged, the balance valves are reversely opened to form balance pressure in the rodless cavity, the set values of the balance pressures of the two cylinder balance valves are the same, the balance pressure acts on the piston to form balance force, the balance force is generally at least 1.3 times of the load force, and the stall of the equipment is prevented from playing a role in speed control; when the oil cylinder stops at any position or the oil pipe bursts, the balance valve is closed, so that the oil cylinder stops at the current position and does not fall down to ensure safety. When lifting, the oil cylinder piston is mainly stressed by rodless cavity thrust and loading force, the rodless cavity thrust and the loading force on the two cylinder pistons are equal, the two cylinder pistons are stressed differently due to the influence of factors such as load deviation and friction force, but the stress difference caused by the load deviation and the friction force is smaller, the mechanism only needs micro elastic deformation, the generated elastic stress can balance the stress of the two cylinder pistons, and the synchronization precision is high. When the piston is laid down, the oil cylinder piston is mainly stressed by the rod cavity thrust, the loading force and the balance force, the rod cavity thrust, the loading force and the balance force of the two cylinder pistons are equal, and the two cylinder pistons are stressed differently due to the influence of factors such as loading deviation, balance force error and friction force. The stress difference caused by the load deviation and the friction force is small, the proportion of the balance force in the stress of the oil cylinder piston is large, and the stress difference caused by the balance force error is relatively large. Compared with lifting, the mechanism needs to generate larger elastic deformation when lodging, the generated elastic stress can enable the two cylinder pistons to be stressed in balance, synchronization can be ensured, but the precision is relatively low in lifting. The hydraulic system is provided with a multi-stage filter, but impurities inevitably exist in hydraulic oil after long-term operation. The spring valve core mechanism is arranged in the balance valve, the spring valve core mechanism is relatively precise and is easily influenced by impurities, the balance force is greatly changed, the stress difference of the two cylinder pistons is increased when the balance valve is laid down, the elastic stress required by stress balance is increased, and the elastic deformation of the mechanism is increased. According to practical engineering experience, when the balance force applied to the two-cylinder piston is influenced by impurities to generate difference, the situation that the elastic stress still cannot balance the stress of the two-cylinder piston after the mechanism reaches the elastic deformation limit easily occurs, the mechanism is continuously deformed until plastic deformation or even breakage occurs, and permanent damage to equipment is caused.
Disclosure of Invention
In order to solve the problems, the invention provides a high-reliability hydraulic rigid synchronization system and a working method thereof.
The technical solution for achieving the above purpose is as follows:
a high-reliability hydraulic rigid synchronization system comprises an electromagnetic directional valve, a balance valve, N hydraulic control one-way valves, N overflow valves and N oil cylinders.
The port A of the electromagnetic directional valve is communicated with a pilot port of the balance valve, a pilot port of each hydraulic control one-way valve and a rod cavity of each oil cylinder, the port B of the electromagnetic directional valve is communicated with an oil inlet of the balance valve, a load port of the balance valve is communicated with an oil inlet of each hydraulic control one-way valve, a load port of each hydraulic control one-way valve is communicated with a rodless cavity of the corresponding oil cylinder, and N is more than or equal to 2.
Further, still include pressure sensor, pressure sensor connect in between N pilot operated check valve oil inlet and the balanced valve load mouth.
And the oil inlet of each overflow valve is communicated with the load port of the corresponding hydraulic control one-way valve and the rodless cavity of the corresponding oil cylinder, and the oil outlet of each overflow valve is communicated with the oil tank.
Furthermore, the overflow pressure of each overflow valve is 5% -10% higher than the working pressure of the system.
Furthermore, the valve core of the overflow valve is of a cone valve structure.
Further, N is 2.
Furthermore, each hydraulic control one-way valve and the corresponding overflow valve are arranged on the corresponding oil cylinder in an integrated valve block mode.
Further, the N oil cylinders are oil cylinders with the same specification.
Further, the N oil cylinders are uniformly arranged relative to the load.
According to the working method of the high-reliability hydraulic rigid synchronous system, the method comprises a lifting process and a lodging process, wherein the lifting process comprises the following steps:
the electromagnetic directional valve is electrified and switched to a left functional position, a port P of the electromagnetic directional valve is communicated with a port B, a port T is communicated with a port A, pressure oil is output from the port B of the electromagnetic directional valve, the pressure oil is opened in the forward direction and respectively enters corresponding rodless cavities of N oil cylinders through the balance valve and the N hydraulic control one-way valves, the N overflow valves are in a closed state and have no leakage, hydraulic oil in rod cavities of the N oil cylinders returns to the port T through the port A of the electromagnetic directional valve, once a rodless cavity oil pipe between the balance valve and the hydraulic control one-way valves bursts in the lifting process, the pressure at an oil inlet of the hydraulic control one-way valves is sharply reduced until no pressure exists, the hydraulic control one-way valves are closed, the hydraulic oil in the rodless cavities of the oil cylinders cannot leak, and the;
the lodging process is as follows:
the electromagnetic directional valve is switched to a right functional position by electrifying, a port P of the electromagnetic directional valve is communicated with a port A, a port T is communicated with a port B, pressure oil is output to a pilot port of a balance valve from the port A of the electromagnetic directional valve, pilot ports of N hydraulic control one-way valves and rod cavities of N oil cylinders, the N hydraulic control one-way valves and the balance valve are reversely opened under the action of pilot pressure, a load port of the balance valve generates balance pressure, N overflow valves are closed and do not leak, hydraulic oil in the rod-free cavities of the N oil cylinders reversely passes through the corresponding hydraulic control one-way valves and the balance valve and returns to the port T through the port B of the electromagnetic directional valve, once an oil pipe of the rod-free cavity bursts, the balance pressure of the balance valve is released, a pressure sensor detects that the pressure is sharply reduced, the lodging action is closed, no pressure is arranged at the pilot port of the hydraulic control one-way valves, the hydraulic control one-way valves are closed, so, the hydraulic cylinder stops at the current position to ensure safety, when the hydraulic cylinder is in a lifting state to collapse, if the hydraulic cylinder stands for a long time and the environmental temperature rises, the volume of hydraulic oil in the rodless cavity of the hydraulic cylinder expands, pressure is formed in the rodless cavity of the hydraulic cylinder due to the sealing effect of the hydraulic control one-way valve, and the hydraulic cylinder starts to overflow when the pressure is higher than the set value of the overflow valve, so that the pressure of a load port of the hydraulic control one-way valve cannot exceed the limit value, the hydraulic control one-way valve can be reversely opened under the working pressure of.
Compared with the prior art, the invention has the beneficial effects that:
(1) the rodless cavities of the oil cylinders are respectively provided with an integrated valve block mounting type hydraulic control one-way valve as a safety valve, the hydraulic control one-way valves are closed when the oil cylinders stop at any position or an oil pipe bursts, so that the oil cylinders stop at the current position and do not drop to ensure safety, the hydraulic control one-way valves of the oil cylinders are connected in parallel and then connected in series with a balance valve, the balance valve plays a role in controlling speed to prevent equipment from stalling when the equipment is laid down, the rodless cavities of the oil cylinders are mutually communicated through the hydraulic control one-way valves to ensure that the balance pressure is equal when the equipment is laid down, so that the stress of the piston of the oil cylinder cannot generate difference due to the;
(2) an overflow valve is arranged between a load port of the hydraulic control one-way valve and a rodless cavity of the oil cylinder, a valve core of the overflow valve is of a cone valve structure, the overflow pressure is 5% -10% higher than the working pressure of the system, the overflow valve is guaranteed to be reliably closed and leak-free when in normal working, the normal action of the oil cylinder is not influenced, when the volume of hydraulic oil in the rodless cavity of the oil cylinder is expanded due to the rise of the environmental temperature, the overflow valve starts to overflow when the pressure generated by thermal expansion reaches the overflow pressure, so that the pressure of the load port of the hydraulic control one-way valve cannot exceed the limit value, the;
(3) a pressure sensor is arranged between the oil inlet of the hydraulic control one-way valve and the load port of the balance valve, if the oil pipe bursts in the action process, the control module can timely detect pressure change and close the action, and the safety is improved.
Drawings
Fig. 1 is a hydraulic schematic diagram of a conventional hydraulic rigid synchronous system.
Fig. 2 is a hydraulic schematic diagram of the high reliability hydraulic rigid synchronization system of the present invention.
In the figure: the system comprises an electromagnetic directional valve 1, a balance valve 2, a pressure sensor 3, a hydraulic control one-way valve 4 a, a hydraulic control one-way valve 5 b, an overflow valve 6 a, an overflow valve 7 b, an oil cylinder 8 a, an oil cylinder 9 b, an oil tank 10 and an oil pipe 11 without a rod cavity.
Detailed Description
The invention is described in further detail below with reference to fig. 2.
In the following, the two numbers of the pilot operated check valves, the relief valves and the cylinders are described as an example, but the number of the above components of the present invention may be more than two.
Referring to fig. 2, a high-reliability hydraulic rigid synchronization system includes a solenoid directional valve 1, a balance valve 2, a pressure sensor 3, a pilot operated check valve a4, a pilot operated check valve b5, an overflow valve a6, an overflow valve b7, an oil cylinder a8, and an oil cylinder b 9. The port 1A of the electromagnetic directional valve is communicated with a pilot port of a balance valve 2, a pilot port of a hydraulic control one-way valve a4, a pilot port of a hydraulic control one-way valve B5, a rod cavity of an oil cylinder a8 and a rod cavity of an oil cylinder B9, the port 1B of the electromagnetic directional valve is communicated with an oil inlet of the balance valve 2, a load port of the balance valve 2 is communicated with an oil inlet of a hydraulic control one-way valve a4 and an oil inlet of a hydraulic control one-way valve B5, a load port of a hydraulic control one-way valve a4 is communicated with a rodless cavity of the oil cylinder a8, a load port of a hydraulic control one-way valve B5 is communicated with a rodless cavity of an oil cylinder B9, and the pressure sensor 3 is positioned between an.
Preferably, the oil inlet of the overflow valve a6 is communicated with a hydraulic control one-way valve a4 load port and a rodless cavity of the oil cylinder a8, and the oil outlet of the overflow valve a6 is communicated with the oil tank 10. The oil inlet of the overflow valve b7 is communicated with a hydraulic control one-way valve b5 load port and an oil cylinder b9 rodless cavity, and the oil outlet of the overflow valve b7 is communicated with the oil tank 10.
Preferably, the relief valves a and b set the relief pressure to be 5% -10% higher than the system working pressure.
Preferably, the valve cores of the relief valves a6 and b7 are cone valves.
Preferably, the hydraulic control check valve a4 and the overflow valve a6 are arranged on the oil cylinder a in an integrated valve block mode. And the hydraulic control check valve b5 and the overflow valve b7 are arranged on the oil cylinder b in an integrated valve block mode.
Preferably, the oil cylinder a8 and the oil cylinder b9 are oil cylinders with the same specification.
Preferably, the oil cylinder a8 and the oil cylinder b9 are evenly arranged relative to the load.
The rodless cavities of the oil cylinder a8 and the oil cylinder b9 are bearing cavities, extend out when lifted and retract when laid down.
Lifting working principle: the electromagnetic directional valve 1 is switched to a left functional position in an electrified mode, a port P of the electromagnetic directional valve 1 is communicated with a port B, a port T is communicated with a port A, pressure oil is output from the port B of the electromagnetic directional valve 1, the pressure oil is opened in the forward direction and passes through the balance valve 2, the hydraulic control one-way valve a4 and the hydraulic control one-way valve B5, the overflow valve a6 and the overflow valve B7 are in a closed state and are not leaked, the pressure oil enters a rodless cavity of the oil cylinder a8 and a rodless cavity of the oil cylinder B9, a rod cavity of the oil cylinder a8 and a rod cavity of the oil cylinder B9, and hydraulic oil in the rod cavity returns to. The piston areas of the oil cylinder a8 and the oil cylinder b9 are the same, the pressure of two communicated cavities of a8 rodless cavity and an oil cylinder b9 rodless cavity is the same, and the thrust of the rodless cavity borne by the piston of the oil cylinder a8 and the piston of the oil cylinder b9 are the same; the oil cylinder a8 and the oil cylinder b9 are equal in load force borne by the piston and evenly distributed relative to the bearing equipment. When lifting, the oil cylinder piston mainly bears the force of rodless cavity thrust and load force, so the difference of the two cylinder pistons is small, the two cylinder pistons can bear balanced stress only by small elastic stress, the two cylinders synchronously extend out, the elastic deformation of the mechanism is small, and the synchronous precision is high.
In the lifting process, once the rodless cavity oil pipe 11 bursts, the pressure at the oil inlets of the hydraulic control one-way valve a4 and the hydraulic control one-way valve b5 is sharply reduced until no pressure exists, the hydraulic control one-way valve a4 and the hydraulic control one-way valve b5 are closed, hydraulic oil in the rodless cavity of the oil cylinder a8 and the rodless cavity of the oil cylinder b9 cannot leak, and the oil cylinder a8 and the oil cylinder b9 stop at the current positions to guarantee safety.
Lodging working principle: the electromagnetic directional valve 1 is switched to a right functional position by electrifying, a port A is communicated with a port P of the electromagnetic directional valve 1, a port B is communicated with a port T, pressure oil is output to a rod cavity of an oil cylinder a8 from the port A of the electromagnetic directional valve 1, a rod cavity of an oil cylinder B9, a pilot port of a hydraulic control one-way valve a4, a pilot port of a hydraulic control one-way valve B5 and a pilot port of a balance valve 2, the hydraulic control one-way valve a4, the hydraulic control one-way valve B5 and the balance valve 2 are opened reversely under the action of pilot pressure, a load port of the balance valve 2 generates balance pressure, an overflow valve a6 and an overflow valve B7 are in a closed state and have no leakage, hydraulic oil in a8 rodless cavity of the oil cylinder a 9 rodless cavity reversely passes through the hydraulic control one-way valve a4, the hydraulic control one-way valve B5 and the. The piston areas of the oil cylinder a8 and the oil cylinder b9 are the same, the pressure of a rod cavity of the oil cylinder a8 is equal to that of two communicated cavities of a rod cavity of the oil cylinder b9, and the thrust of the rod cavities of the oil cylinder a8 and the oil cylinder b9 is equal; the oil cylinder a8 and the oil cylinder b9 are uniformly distributed relative to the bearing equipment, and the load forces borne by the pistons are equal; the balance pressure of the two communicated cavities of the rodless cavity of the oil cylinder a8 and the rodless cavity of the oil cylinder b9 is equal, and the balance force borne by the piston of the oil cylinder a8 and the piston of the oil cylinder b9 is equal. When the mechanism is laid down, the oil cylinder piston is mainly stressed by the rod cavity thrust force, the loading force and the balance force, so that the stress difference of the two cylinder pistons is very small, the two cylinder pistons can be stressed in a balanced manner only by small elastic stress, the two cylinders retract synchronously, the elastic deformation of the mechanism is small, and the synchronous precision is high.
In the lodging process, once the rodless cavity oil pipe 11 bursts, the balance pressure of the balance valve 2 is released, the pressure sensor 3 detects that the pressure is rapidly reduced, the control module closes the lodging action, the pilot pressure ports of the hydraulic control one-way valve a4 and the hydraulic control one-way valve b5 are not pressurized, the hydraulic control one-way valve a4 and the hydraulic control one-way valve b5 are closed, hydraulic oil in the rodless cavity of the oil cylinder a8 and the rodless cavity of the oil cylinder b9 cannot leak, and the oil cylinder a8 and the oil cylinder b9 stop at the current positions to ensure safety.
When the lifting type hydraulic control device is in a lifting state for lodging, if the lifting type hydraulic control device stands for a long time and the environmental temperature is increased, the hydraulic oil in the rodless cavity of the oil cylinder a8 and the hydraulic oil in the rodless cavity of the oil cylinder b9 expand in volume, due to the sealing effect of the hydraulic control one-way valve a4 and the hydraulic control one-way valve b5, pressure is formed in the rodless cavity of the oil cylinder a8 and the rodless cavity of the oil cylinder b9, when the pressure is higher than the set values of the overflow valve a6 and the overflow valve b7, the pressure of the hydraulic control one-way valve a4 load port and the pressure of the hydraulic control one-way valve b5 load port cannot exceed the limit value, the system working pressure can be ensured to reversely.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. The high-reliability hydraulic rigid synchronization system is characterized by comprising an electromagnetic directional valve (1), a balance valve (2), N hydraulic control one-way valves, N overflow valves and N oil cylinders.
The port A of the electromagnetic directional valve (1) is communicated with the pilot port of the balance valve (2), the pilot port of each hydraulic control one-way valve and the rod cavity of each oil cylinder, the port B of the electromagnetic directional valve (1) is communicated with the oil inlet of the balance valve (2), the load port of the balance valve (2) is communicated with the oil inlet of each hydraulic control one-way valve, the load port of each hydraulic control one-way valve is communicated with the rodless cavity of the corresponding oil cylinder, and N is more than or equal to 2.
2. The high-reliability hydraulic rigid synchronization system according to claim 1, further comprising a pressure sensor (3), wherein the pressure sensor (3) is connected between the oil inlet of the N pilot-controlled check valves and the load port of the balance valve (2).
3. The high-reliability hydraulic rigid synchronization system according to claim 2, further comprising an oil tank (10), wherein an oil inlet of each overflow valve is communicated with a load port of a corresponding hydraulic control one-way valve and a rodless cavity of a corresponding oil cylinder, and an oil outlet of each overflow valve is communicated with the oil tank (10).
4. The high reliability hydraulic rigid synchronous system of claim 3, wherein the relief pressure of each relief valve is 5-10% higher than the system working pressure.
5. The high reliability hydraulic rigid synchronization system of claim 3, wherein the spool of the relief valve is of a cone valve structure.
6. The high reliability hydraulic rigid synchronization system of claim 3, wherein N-2.
7. The high-reliability hydraulic rigid synchronization system according to any one of claims 2 to 6, wherein each hydraulic control check valve and the corresponding overflow valve are mounted on the corresponding cylinder in an integrated valve block manner.
8. The high reliability hydraulic rigid synchronization system of claim 7, wherein the N cylinders are cylinders of the same specification.
9. The high reliability hydraulic rigid synchronization system of claim 8, wherein the N cylinders are evenly arranged with respect to the load.
10. The method of claim 9, wherein the method comprises a lifting process and a lodging process, and the lifting process is:
the electromagnetic directional valve (1) is electrified and switched to a left functional position, a port P of the electromagnetic directional valve (1) is communicated with a port B, a port T is communicated with a port A, pressure oil is output from the port B of the electromagnetic directional valve (1), the pressure oil is opened in the forward direction and respectively enters corresponding rodless cavities of N oil cylinders through the balance valve (2) and the N hydraulic control one-way valves, N overflow valves are closed and do not leak, hydraulic oil in rod cavities of the N oil cylinders returns to the port T through the port A of the electromagnetic directional valve (1), once a rodless cavity oil pipe (11) between the balance valve (2) and the hydraulic control one-way valves bursts, the pressure at an oil inlet of the hydraulic control one-way valves is sharply reduced until no pressure exists, the hydraulic control one-way valves are closed, the hydraulic oil in the rodless cavities of the oil cylinders cannot leak, and the oil cylinders stop at the current positions to ensure safety;
the lodging process is as follows:
the electromagnetic directional valve (1) is switched to a right functional position by electrifying, a P port of the electromagnetic directional valve (1) is communicated with an A port, a T port is communicated with a B port, pressure oil is output to a pilot port of the balance valve (2) from the A port of the electromagnetic directional valve (1), pilot ports of N hydraulic control one-way valves and rod cavities of N oil cylinders, the N hydraulic control one-way valves and the balance valve (2) are reversely opened under the action of pilot pressure, a load port of the balance valve (2) generates balance pressure, N overflow valves are in a closed state without leakage, hydraulic oil in rodless cavities of the N oil cylinders reversely passes through the corresponding hydraulic control one-way valves and the balance valve (2) and then returns to the T port through the B port of the electromagnetic directional valve (1), in the lodging process, once the rodless cavity oil pipe (11) bursts, the balance pressure of the balance valve (2) is released, the pressure sensor (3) detects that the pressure is sharply reduced, the lodging action is closed, and the pressure at the pilot port of the hydraulic control one, the hydraulic control one-way valve is closed, hydraulic oil in a rodless cavity of the oil cylinder cannot leak, the oil cylinder stops at the current position to ensure safety, when the oil cylinder is in a lifting state and is lodged, if the oil cylinder stands for a long time and the environmental temperature rises, the volume of the hydraulic oil in the rodless cavity of the oil cylinder expands, due to the sealing effect of the hydraulic control one-way valve, pressure is formed in the rodless cavity of the oil cylinder, when the pressure is higher than the set value of the overflow valve, the overflow is started, the pressure of a load port of the hydraulic control one-way valve cannot exceed the limit value, the working pressure of a system can be ensured.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114458646A (en) * | 2022-01-27 | 2022-05-10 | 大连华锐重工集团股份有限公司 | Hydraulic system of car dumper and control method thereof |
| CN114576508A (en) * | 2022-01-27 | 2022-06-03 | 北京航天发射技术研究所 | Vehicle-mounted radar turnover hydraulic control system and control method |
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| CN114576508A (en) * | 2022-01-27 | 2022-06-03 | 北京航天发射技术研究所 | Vehicle-mounted radar turnover hydraulic control system and control method |
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| CN112855637B (en) | 2023-03-21 |
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