CN111336151B - Control method of hydraulic speed regulation system with manual automatic switching function - Google Patents
Control method of hydraulic speed regulation system with manual automatic switching function Download PDFInfo
- Publication number
- CN111336151B CN111336151B CN202010250257.8A CN202010250257A CN111336151B CN 111336151 B CN111336151 B CN 111336151B CN 202010250257 A CN202010250257 A CN 202010250257A CN 111336151 B CN111336151 B CN 111336151B
- Authority
- CN
- China
- Prior art keywords
- valve
- hydraulic
- control
- switching
- port
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
-
- 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
- F15B20/008—Valve failure
-
- 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
- F15B2013/0409—Position sensing or feedback of the valve member
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
- F15B2211/8636—Circuit failure, e.g. valve or hose failure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/875—Control measures for coping with failures
- F15B2211/8757—Control measures for coping with failures using redundant components or assemblies
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/895—Manual override
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to the technical field of hydraulic systems, in particular to a control method of a hydraulic speed regulating system with manual automatic switching. By the control method, the problems of unreliable operation of the hydraulic speed regulating system and difficulty in fault finding and removing can be effectively solved.
Description
Technical Field
The invention relates to the technical field of hydraulic systems, in particular to a control method of a hydraulic speed regulating system with manual automatic switching.
Background
The hydraulic control technology is widely applied to various industries at present, and is also very commonly applied to the control field of the hydropower industry. As important adjusting, controlling and application occasions, the hydropower industry has very high requirements on the reliability of a speed regulation hydraulic system. At present, in many hydropower stations used as peak load regulation and frequency regulation tasks of large-scale power grids, in consideration of safe operation of units, electromagnetic valves (generally proportional valves) which play important hydraulic control signal outputs are required to adopt a redundant parallel design mode, and when a main electromagnetic valve fails, the main electromagnetic valve can be reliably switched to another standby valve.
In the existing design, a chinese invention patent document with publication number CN101487437 and publication date of 2009, 07 and 22 is proposed to solve the above-mentioned existing technical problems, and the technical scheme disclosed by the patent document is as follows: a main distributing valve is connected with a hydraulic control system through an oil way, the main distributing valve is connected with a microcomputer control system through a circuit, the hydraulic control system comprises a manual/automatic switching electromagnetic valve, a servo proportional valve, a proportional valve switching electromagnetic valve and a hydraulic control reversing valve, a flow feedback device is arranged on the main distributing valve, the flow feedback device comprises a flow feedback valve and a displacement sensor, and a manual operation electromagnetic valve is further arranged in the hydraulic control system.
In the actual use process, the following problems can occur in the technical scheme:
(1) although this patent can realize the switching of servo proportional valve, when switching the solenoid valve because of the case card hinders, switch not in place scheduling problem when switching the trouble, no feedback signal reports, and monitored control system can't in time discover to get rid of the trouble, and whole hydraulic control system can take huge potential safety hazard in the operation. Once the main servo proportional valve fails, the problem that the switching solenoid valve cannot be switched can be found when switching is needed, so that the hydraulic control system cannot complete the switching operation in time, and only the system is decompressed, thereby causing accident shutdown.
Although some switching electromagnetic valves have a valve core position detection function, the function mode has the following disadvantages:
a. the purchase cost is greatly increased, and the price of the switching electromagnetic valve with the valve core position feedback function is about 9 times that of the common switching electromagnetic valve;
b. because the electric signal detection is adopted, the reliability is not high, and various faults such as signal false alarm or failure in alarm can occur after the electromagnetic valve is switched for a long time and the valve core is frequently switched to act;
c. the switching electromagnetic valve with the valve core position feedback function has the advantages that the valve core is easy to block and blow-by, and serious faults such as control failure or misoperation of the whole hydraulic system can be caused; meanwhile, the oil leakage is large, so that huge energy loss is brought to the system, and the temperature of the oil is increased.
Therefore, it is not feasible to replace the ordinary switching electromagnetic valve with a valve core position feedback function, and the problem cannot be solved.
(2) The on-line maintenance of the faults of the switching electromagnetic valve can not be realized, once the switching electromagnetic valve breaks down, the whole pressure relief and shutdown of a hydraulic system are generally carried out, the machine set is stopped due to the accident that the maintenance time is too long, and the machine set can be stopped only by stopping.
(3) During the manual control, the servo proportional valve is not manually switched, but the operation of the opening control valve is directly and manually controlled, the servo proportional valve does not work any more, and the movement of the valve core of the main valve cannot be accurately controlled.
Disclosure of Invention
In order to solve the technical problems, the invention provides a control method of a hydraulic speed regulating system with manual and automatic switching, which can effectively solve the problems of unreliable operation of the hydraulic speed regulating system and difficulty in fault discovery and removal.
The invention is realized by adopting the following technical scheme:
a control method of a hydraulic speed regulating system with manual automatic switching is characterized in that: the hydraulic control switching valve comprises a speed regulator controller, a pressure oil source, a switching electromagnetic valve, an automatic switching hydraulic control reversing valve, a manual switching valve, a first hydraulic signal output proportional valve, a second hydraulic signal output proportional valve, a guide vane servomotor and a main pressure distribution valve; the main pressure distribution valve comprises an upper end control cavity, a main valve core and a lower end control cavity, a spring is arranged in the lower end control cavity, and an A, B opening switch cavity of the main pressure distribution valve is respectively connected with a switch cavity of the guide vane servomotor through an oil pipeline; after the automatic control mode or the manual control mode is switched, the output port of the hydraulic signal output proportional valve I or the hydraulic signal output proportional valve II at the main control position is connected with the upper end control cavity of the main pressure distribution valve and matched with a spring in a lower end control cavity of the main pressure distribution valve, the valve core of the main valve is controlled to move up and down, and the opening and closing of the guide vane servomotor are controlled;
the automatic control mode specifically refers to:
the switching electromagnetic valve controls the station of the automatic switching hydraulic control reversing valve through the control cavities at the two ends of the automatic switching hydraulic control reversing valve, and determines that the hydraulic signal output proportional valve I or the hydraulic signal output proportional valve II is in the master control position;
wherein the manual control mode specifically refers to:
the manual switching valve is provided with a first oil port, a second oil port and a third oil port, a handle of the manual switching valve is manually rotated, and the first hydraulic signal output proportional valve or the second hydraulic signal output proportional valve is determined to be located at a main control position by selecting a communication mode among the three oil ports.
The hydraulic control reversing valve is characterized by further comprising an emergency stop electromagnetic valve and an emergency stop hydraulic control reversing valve, wherein the output port of the first hydraulic signal output proportional valve or the second hydraulic signal output proportional valve at the main control position is connected with the upper end control cavity of the main pressure distribution valve through the emergency stop hydraulic control reversing valve, the output port B of the emergency stop electromagnetic valve is communicated with the right end control cavity X of the emergency stop hydraulic control reversing valve, and the output port A is communicated with the left end control cavity Y of the emergency stop hydraulic control reversing valve.
The emergency stop electromagnetic valve is a single-coil emergency stop electromagnetic valve.
The emergency shutdown electromagnetic valve is characterized by further comprising a first pressure relay, a pressure gauge and a second pressure relay, wherein an oil port of the first pressure relay is connected with an output port A of the switching electromagnetic valve, a pressure measuring port of the pressure gauge is connected with an output port B of the switching electromagnetic valve, and an oil port of the second pressure relay is communicated with an output port B of the emergency shutdown electromagnetic valve.
The hydraulic signal output proportional valve I is communicated with the hydraulic signal output proportional valve I through a port P, the hydraulic signal output proportional valve I is communicated with a pressure oil source through a port P, and the switching electromagnetic valve I is communicated with a pressure oil source through a port P.
The switching electromagnetic valve, the first pressure relay, the second pressure relay, the pressure gauge, the automatic switching hydraulic control reversing valve, the manual switching valve, the first hydraulic signal output proportional valve, the second hydraulic signal output proportional valve, the first maintenance ball valve, the second maintenance ball valve, the third maintenance ball valve, the emergency shutdown electromagnetic valve and the emergency shutdown hydraulic control reversing valve are installed on an integrated valve block, and all oil paths are connected through inner ducts of the valve block.
The switching electromagnetic valve is a two-position four-way valve and adopts a double electromagnet structure with position locking.
The switching electromagnetic valve, the pressure relay I, the pressure relay II, the pressure gauge, the automatic switching hydraulic control reversing valve, the manual switching valve, the hydraulic signal output proportional valve I, the hydraulic signal output proportional valve II, the maintenance ball valve I, the maintenance ball valve II, the maintenance ball valve III, the emergency shutdown electromagnetic valve and the emergency shutdown hydraulic control reversing valve all adopt standard hydraulic elements.
The automatic switching hydraulic control reversing valve is of a two-position four-way sliding valve structure, and pressure oil sources or return oil are communicated with two ends of a control piston of the automatic switching hydraulic control reversing valve.
And the manual operation angles among the first oil port, the second oil port and the third oil port of the manual switching valve are all 90 degrees.
Compared with the prior art, the invention has the beneficial effects that:
1. in the control method of the hydraulic speed regulation control system, a manual switching function is designed besides automatic switching control. By controlling the electromagnets at the two ends of the switching electromagnetic valve, the automatic switching control can be realized on the main and standby working states of the first hydraulic signal output proportional valve and the second hydraulic signal output proportional valve on line. When the automatic switching fails or needs to be overhauled, the main and standby switching of the first hydraulic signal output proportional valve and the second hydraulic signal output proportional valve can be realized through the manual switching valve. After automatic or manual switching, the output port of the hydraulic signal output proportional valve I or the hydraulic signal output proportional valve II at the main control position is connected with the upper end control cavity of the main pressure distributing valve, the hydraulic signal output proportional valve I or the hydraulic signal output proportional valve II can receive the electric control signal of the monitoring system, the displacement of the valve core of the main pressure distributing valve is controlled in proportion to the electric signal, the regulation of the flow and the pressure of the output hydraulic oil is realized, the pressure of the hydraulic oil of the control cavity at the upper end of the main pressure distributing valve is changed, the balance (main valve core static state) or unbalance (main valve core moving state) of force is realized with a spring in a control cavity at the lower end of the main pressure distribution valve, the upper and lower displacement of the main valve spool is controlled, so that the opening and closing of the guide vane servomotor are controlled and the speed is accurately adjusted, the whole speed regulating system can work normally, and the running of a unit is ensured.
The automatic switching hydraulic control reversing valve used as the automatic switching main oil way is characterized in that pressure oil or oil return is communicated with control cavities at two ends under the control of a pilot switching electromagnetic valve, the change of the valve core station of the automatic switching hydraulic control reversing valve is realized, the connection mode of an automatic switching oil way system is changed, and the change of the main and standby states of a hydraulic signal output proportional valve I and a hydraulic signal output proportional valve II is realized. The automatic switching hydraulic control reversing valve adopts a two-end hydraulic oil control mode, and the potential safety hazard that the spring is fatigue failure due to frequent action of the valve core or long-time compression of the valve core under the long-term use condition when the spring is used as a valve core return mechanism is avoided. Meanwhile, the hydraulic pressure operation is larger than the spring force, and the valve core can still be pushed to change direction by the hydraulic pressure under the condition that the clearance of the valve core of the automatic switching hydraulic control change-over valve is blocked by foreign matters. The reversing mode has high safety and reliability, low requirement on the fit clearance of the valve core and the valve sleeve, good manufacturability and convenient processing and assembly.
The lower end control cavity of the main distributing valve is provided with a spring, and the upper end control cavity is communicated with a hydraulic signal output control port from the hydraulic signal output proportional valve. When the downward hydraulic pressure generated by the hydraulic oil of the upper control cavity is balanced with the gravity of the main valve core and the spring force of the lower end, the main valve core is kept still, the opening A, B of the main valve switch cavity is sealed by the valve disc structure of the valve core, and the guide vane servomotor is kept still; when the spring force is greater than the hydraulic pressure and the gravity of the main valve spool, the main valve spool moves upwards, and the guide vane servomotor moves towards the closing direction; when the spring force is smaller than the hydraulic pressure and the gravity of the main valve spool, the main valve spool moves downwards, and the guide vane servomotor moves towards the opening direction. Whether the hydraulic control is automatic control or manual control, the flow and the pressure of hydraulic oil entering the upper end control cavity of the main pressure distributing valve are accurately controlled through the hydraulic signal output proportional valve, so that the movement direction of the valve core of the main valve is controlled, and further the opening and the closing of the guide vane servomotor of the water turbine are controlled or the guide vane servomotor of the water turbine is kept at a certain fixed position without moving. The mode of controlling the valve core of the main valve simplifies the mechanical structure of the main pressure distributing valve, and the accurate control of the valve core of the main valve can be realized only by controlling the relevant parameters of the hydraulic oil of the control cavity at the upper end of the main pressure distributing valve.
2. The emergency shutdown hydraulic circuit is composed of an emergency shutdown hydraulic control reversing valve and an emergency shutdown electromagnetic valve controlled by a pilot thereof. The design of the hydraulic control reversing valve can increase the reliability of the reversing valve in long-term use, and avoid the problems of valve core blockage and incomplete reversing caused by fatigue and aging of the spring when the spring is used for reversing. Meanwhile, hydraulic pressure is adopted for reversing, the driving force is large, and the problem of valve core blockage caused by small foreign matters can be avoided. The control mode realizes the function of emergency stop when abnormal power failure occurs in the automatic control state of the speed regulation control system.
3. The emergency stop electromagnetic valve can adopt a single coil design, when the power plant is abnormally power-off, the direction of the spring at the right end of the emergency stop electromagnetic valve is changed by the emergency stop electromagnetic valve, the X cavity of the emergency stop hydraulic control reversing valve is communicated with the oil return through the emergency stop electromagnetic valve, at the moment, the valve core of the emergency stop hydraulic control reversing valve is changed direction under the action of the pressure oil of the Y cavity at the left end of the emergency stop hydraulic control reversing valve, the pressure oil of the control cavity at the upper end of the main distributing valve is communicated with the oil return through the emergency stop hydraulic control reversing valve, the valve core of the main valve moves upwards under the action of the spring force in the control cavity at the lower end, and the guide vane servomotor realizes the emergency closing function.
4. The pressure meter also comprises a pressure relay I, a pressure meter and a pressure relay II. The first pressure relay is used for monitoring the change of the hydraulic pressure of the Y cavity of the automatic switching hydraulic control reversing valve and reporting a switching value signal to a monitoring system. The pressure gauge is used for monitoring the change of the hydraulic pressure of the X cavity of the hydraulic control reversing valve, and is convenient for in-situ observation and overhaul. And the second pressure relay is used for monitoring whether the emergency stop electromagnetic valve is in a normal or emergency stop state. When the unit normally operates, the pressure relay is communicated with pressure oil, when an emergency stop accident occurs, the electromagnet of the emergency stop electromagnetic valve loses power, the output port B of the emergency stop electromagnetic valve is communicated with return oil, the pressure relay is also communicated with the return oil, and the switch correspondingly acts and reports an emergency stop state signal of the speed regulating system to the monitoring system.
5. Still including overhauing ball valve one, overhauing ball valve two and overhauing ball valve three, through each maintenance ball valve of manual shut-down, cut off the pressure oil source and correspond the being connected of valve, alright realize the online maintenance and the change to this valve, and need not make entire system pressure release, cause the phenomenon of unit shut down to take place.
6. The switching electromagnetic valve, the pressure relay I, the pressure relay II, the pressure gauge, the automatic switching hydraulic control reversing valve, the manual switching valve, the hydraulic signal output proportional valve I, the hydraulic signal output proportional valve II, the maintenance ball valve I, the maintenance ball valve II, the maintenance ball valve III, the emergency stop electromagnetic valve and the emergency stop hydraulic control reversing valve are installed on an integrated valve block and serve as a complete functional module, and the switching electromagnetic valve is suitable for various hydraulic control systems which require the functions of hydraulic signal valve switching, state signal detection and display, and emergency stop and electromagnetic valve online maintenance. The integrated volume is small, the installation is convenient, after a whole functional module is made, no middle pipeline is connected, leakage points are reduced, the appearance is neat, compact and attractive, and the oil leakage condition caused by large occupied space of each element in the dispersed arrangement and large quantity of pipelines and joints in the open pipe connection can be effectively avoided.
7. The switching electromagnetic valve is a two-position four-way valve, and a structure with position locking double electromagnets is adopted, so that the electromagnets can be prevented from long-term live operation.
8. The switching electromagnetic valve, the pressure relay I, the pressure relay II, the pressure gauge, the automatic switching hydraulic control reversing valve, the manual switching valve, the hydraulic signal output proportional valve I, the hydraulic signal output proportional valve II, the maintenance ball valve I, the maintenance ball valve II, the maintenance ball valve III, the emergency shutdown electromagnetic valve and the emergency shutdown hydraulic control reversing valve all adopt standardized hydraulic elements, are good in interchange and universality, and are convenient to apply to various hydraulic control systems.
9. The two ends of the control piston of the automatic switching hydraulic control reversing valve are communicated with a pressure oil source or return oil without adopting differential pressure type or spring type control, the piston is reliably reversed by the mode, the blocking or oil channeling of the automatic switching hydraulic control reversing valve core is reduced, and in addition, the action areas of the control cavities at the two ends are the same, so that the reversing piston and the shell are good in processing manufacturability, and the assembly is also facilitated.
10. The manual operation angles among the first oil port, the second oil port and the third oil port of the manual switching valve are all 90 degrees, the position relation is convenient to operate, and meanwhile, a position switch arranged on a handle of the manual switching valve can send a switching state signal of the manual switching valve to a monitor and ensure that the switching is in place.
Drawings
The invention will be described in further detail with reference to the following description taken in conjunction with the accompanying drawings and detailed description, in which:
FIG. 1 is a schematic diagram of a hydraulic speed governing control method of the present invention;
FIG. 2 is a side view of the shaft of the hydraulic governor system of the present invention;
FIG. 3 is a side view of the hydraulic governor system of the present invention;
FIG. 4 is a top view of the hydraulic governor system of the present invention;
the labels in the figure are:
1. the hydraulic control system comprises a pressure oil source, 2, a switching electromagnetic valve, 3, first pressure relays, 4, a pressure gauge, 5, an automatic switching hydraulic control reversing valve, 6, a manual switching valve, 7, first hydraulic signal output proportional valves, 8, second hydraulic signal output proportional valves, 9, a guide vane servomotor, 10, a main pressure distribution valve, 11, an emergency stop electromagnetic valve, 12, an emergency stop hydraulic control reversing valve, 13, second pressure relays, 14, first maintenance ball valves, 15, second maintenance ball valves, 16 and a third maintenance ball valve.
Detailed Description
Example 1
As a basic implementation mode of the invention, the invention comprises a control method of a hydraulic speed regulation system with manual and automatic switching, which comprises a main control hydraulic system, a pressure oil source 1, a two-position four-way switching electromagnetic valve 2, a pressure relay I3 for monitoring the switching state, a pressure gauge 4, an automatic switching hydraulic control reversing valve 5, a manual switching valve 6, a hydraulic signal output proportional valve I7 and a hydraulic signal output proportional valve II 8. The manual switching valve 6 is provided with an oil port I, an oil port II and an oil port III.
The switching electromagnetic valve 2 adopts a structure of locking the position of a double electromagnet belt, so that the electromagnet can be prevented from long-term electrified operation. The P port of the switching electromagnetic valve 2 is connected with a pressure oil source 1, the T port is connected with return oil, the output port A is connected with the Y control cavity of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with a pressure relay I3, and the output port B is connected with the X control cavity of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with a pressure gauge 4. An output port B of the hydraulic signal output proportional valve I7 is connected with an output port A of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with an oil port III of the manual switching valve 6; and an output port B of the second hydraulic signal output proportional valve 8 is connected with an output port B of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with an oil port I of the manual switching valve 6. And the oil port II of the manual switching valve 6 and the K port of the automatic switching hydraulic control reversing valve 5 are respectively connected with a master control hydraulic system for output. The automatic switching hydraulic control reversing valve 5 is of a two-position four-way sliding valve structure, and a valve core is driven by hydraulic driving force generated by pressure oil or return oil passing through hydraulic control cavities at two ends to realize reversing, so that the state of an oil way of the system is changed.
The P ports of the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 are connected with a pressure oil source 1, the T ports are communicated with return oil, hydraulic control signals output by the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 enter a main control hydraulic system after being selected by the automatic switching hydraulic control reversing valve 5, and the main control hydraulic system can be specifically a main pressure distribution valve 10. The first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 are used as important hydraulic flow and pressure control output valves, a redundant design is adopted, the two valves are connected in parallel through an electric control system, and when one output valve fails, the other valve can be automatically switched to the other standby valve.
Example 2
As a preferred embodiment of the present invention, referring to fig. 1 of the specification, the present invention includes a control method of a hydraulic speed regulation system with manual and automatic switching, including a pressure oil source 1, a two-position four-way switching solenoid valve 2, a pressure relay 1 for monitoring switching status, a pressure gauge 4, an automatic switching hydraulic control directional control valve 5, a manual switching valve 6, a hydraulic signal output proportional valve 7, a hydraulic signal output proportional valve II 8, a guide vane servomotor 9, a main pressure distributing valve 10, an emergency stop solenoid valve 11, an emergency stop hydraulic control directional control valve 12, a pressure relay II 13 for monitoring stop, a maintenance ball valve I14 for maintaining the hydraulic signal output proportional valve I7, a maintenance ball valve II 15 for maintaining the hydraulic signal output proportional valve II 8, and a maintenance ball valve III 16 for maintaining the switching solenoid valve 2.
An inlet and an outlet of the first overhaul ball valve 14 are respectively communicated with the P port of the first hydraulic signal output proportional valve 7 and the pressure oil source 1, an inlet and an outlet of the second overhaul ball valve 15 are respectively communicated with the P port of the second hydraulic signal output proportional valve 8 and the pressure oil source 1, and an inlet and an outlet of the third overhaul ball valve 16 are respectively communicated with the P port of the switching electromagnetic valve 2 and the pressure oil source 1.
The main pressure distributing valve 10 comprises an upper end control cavity, a main valve core and a lower end control cavity, a spring is arranged in the lower end control cavity, the guide vane servomotor 9 is provided with two oil ports of a switch cavity, and the guide vane servomotor 9 is connected with pressure oil or return oil through an A, B port of the main pressure distributing valve 10 to realize the extending and retracting movement of a piston rod of the guide vane servomotor 9.
The manual switching valve 6 is provided with a first oil port, a second oil port and a third oil port, and manual operation included angles between the first oil port and the second oil port and between the second oil port and the third oil port are all 90 degrees. And the second oil port is used as a hydraulic signal output oil port for manual switching control and is connected with the upper end control cavity of the main distributing valve 10 through the emergency stop hydraulic control reversing valve 12.
The P port of the switching electromagnetic valve 2 is connected with a pressure oil source 1, the T port is connected with return oil, the output port A is connected with a Y control cavity of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with a pressure relay I3 to be used for providing state signals for monitoring, and the output port B is connected with an X control cavity of the hydraulic control reversing valve and is simultaneously connected with a pressure gauge 4 to be used for displaying the in-situ switching state. An output port A of the automatic switching hydraulic control reversing valve 5 is connected with an output port B of the hydraulic signal output proportional valve I7 and is simultaneously connected with an oil port III of the manual switching valve 6; and an output port B of the automatic switching hydraulic control reversing valve 5 is connected with an output port B of the second hydraulic signal output proportional valve 8 and is simultaneously connected with an oil port I of the manual switching valve 6.
When the manual switching valve 6 is at the 0-degree position, the first oil port of the manual switching valve 6 is communicated with the second oil port, at the moment, the output port B of the second hydraulic signal output proportional valve 8 is communicated with the upper end control cavity of the main pressure distributing valve 10, and the second hydraulic signal output proportional valve 8 is in a main state; when the manual switching valve 6 is at the 180-degree position, the oil port two of the manual switching valve 6 is communicated with the oil port three oil way, at the moment, the output port B of the hydraulic signal output proportional valve I7 is communicated with the upper end control cavity of the main pressure distributing valve 10, and the hydraulic signal output proportional valve I7 is in a main state. When the manual switching valve 6 is at the 90-degree position, oil paths of the first oil port, the second oil port and the third oil port are not communicated with each other, the manual switching valve 6 does not output a hydraulic control signal, and the manual switching does not work at the moment.
The P ports of the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 are connected with a pressure oil source 1, the T port is communicated with return oil, and the two ends of a control piston of the automatic switching hydraulic control reversing valve 5 are communicated with the pressure oil source 1 or the return oil. The pressure oil enters the port P of the switching electromagnetic valve 2, the port A or the port B is output by the pressure oil under the control of the switching electromagnetic valve 2, and the port T is communicated with the return oil. When the port A of the switching electromagnetic valve 2 is communicated with pressure and the port B is communicated with oil, the automatic switching hydraulic control reversing valve 5 is positioned at the left station, the control hydraulic oil output by the corresponding hydraulic signal output proportional valve I7 enters the upper end control cavity of the main pressure distribution valve 10 after passing through the automatic switching hydraulic control reversing valve 5 and the emergency stop hydraulic control reversing valve 12, and the hydraulic signal output proportional valve I7 is in the main state of automatic switching control. At the moment, the first pressure relay 3 leads pressure oil, a pressure action signal is reported, the pressure gauge 4 leads oil, and the pressure is displayed as 0. When the port B of the switching electromagnetic valve 2 is communicated with pressure oil and the port A is communicated with return oil, the automatic switching hydraulic control directional control valve 5 is positioned at the right station, and the corresponding hydraulic signal output proportional valve II 8 is in the main state of automatic switching control, namely, control hydraulic oil output by the hydraulic signal output proportional valve II 8 is output to the upper end control cavity of the main pressure distribution valve 10 after passing through the automatic switching hydraulic control directional control valve 5 and the emergency shutdown hydraulic control directional control valve 12. At the moment, the first pressure relay 3 leads to return oil, a non-pressure action signal is reported to the monitor, the pressure gauge 4 leads to pressure oil, and the system pressure is displayed.
The port P of the emergency stop electromagnetic valve 11 is connected with a pressure oil source 1, the port T is communicated with return oil, the port B is a working oil port and is communicated with a right end control cavity X of the emergency stop hydraulic control reversing valve 12, and the port A is a working oil port and is communicated with a left end control cavity Y of the emergency stop hydraulic control reversing valve 12. And a port P of the emergency stop hydraulic control reversing valve 12 is communicated with a port K of the automatic switching hydraulic control reversing valve 5 and a port II of the manual switching valve 6, a port T is communicated with return oil, and a port A is used as a unique hydraulic signal output port of the switching control device and is communicated with an upper end control cavity of the main pressure distribution valve 10. The emergency stop electromagnetic valve 11 adopts a single coil design, when the electromagnetic coil of the emergency stop electromagnetic valve 11 loses power or the whole service power disappears, the valve core is reversed under the action of a spring at the right end of the valve, an X control cavity of the emergency stop hydraulic control reversing valve 12 is communicated with return oil, pressure oil is correspondingly introduced into a Y control cavity at the left end of the emergency stop hydraulic control reversing valve 12, the valve core is reversed under the action of the pressure oil at the left end, so that the control cavity at the upper end of the main pressure distribution valve 10 is communicated with the return oil, the hydraulic pressure at the upper end disappears, the valve core of the main valve moves upwards under the action of the spring force at the lower end, at the moment, the pressure oil enters a closing cavity of the guide vane servomotor 9 through a port B of the main pressure distribution valve 10, oil in an opening cavity of the guide vane servomotor 9 is communicated with the return oil.
And an oil port of the second pressure relay 13 is communicated with an output port B of the emergency stop electromagnetic valve 11 and is used for monitoring whether the valve is in a normal or emergency stop state. When the unit normally operates, the pressure relay II 13 is filled with pressure oil, when an emergency stop accident occurs, the electromagnet of the emergency stop electromagnetic valve 11 loses power, the port B is filled with return oil, the pressure relay II 13 is also filled with return oil, and the switch correspondingly acts and reports an emergency stop state signal of the speed regulating system to the monitoring system.
Example 3
As another preferred embodiment of the present invention, the present invention includes a control method of a hydraulic speed regulation system with manual and automatic switching, which includes a governor controller, a pressure oil source 1, a switching electromagnetic valve 2, an automatic switching hydraulic control directional control valve 5, a manual switching valve 6, a first hydraulic signal output proportional valve 7, a second hydraulic signal output proportional valve 8, a guide vane servomotor 9, a main pressure distributing valve 10, an emergency stop electromagnetic valve 11, and an emergency stop hydraulic control directional control valve 12.
The main pressure distributing valve 10 is a three-position five-way sliding valve structure and comprises an upper end control cavity, a main valve core and a lower end control cavity, a spring is arranged in the lower end control cavity, and a switch cavity of an A, B port of the main pressure distributing valve 10 is respectively connected with a switch cavity of the guide vane servomotor 9 through an oil pipeline. And a control cavity at the upper end of the main pressure distributing valve 10 is connected with an A port of the emergency stop hydraulic control reversing valve 12, and the A port is finally connected with output ports of the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8.
After the automatic control mode or the manual control mode is switched, the first hydraulic signal output proportional valve 7 or the second hydraulic signal output proportional valve 8 at the main control position receives an electric control signal of a speed regulator controller, the displacement of a valve core of the hydraulic signal output proportional valve 7 or the hydraulic signal output proportional valve 8 is controlled in proportion to the electric signal, the regulation of the flow and the pressure of output hydraulic oil is realized, the pressure of hydraulic oil in a control cavity at the upper end of a main pressure distribution valve 10 is changed, the balance (the static state of the valve core of the main valve) or the unbalance (the moving state of the valve core of the main valve) of the force is realized by a spring at the bottom of the main pressure distribution valve 10, the displacement amount of the valve core of the main valve up and down is controlled, and further the opening and closing control of the guide vane servomotor 9 and the accurate regulation of the speed are realized.
The automatic control mode specifically refers to:
in an automatic control state, the switching electromagnetic valve 2 controls a station where a valve core of the automatic switching hydraulic control reversing valve 5 is located through control cavities at two ends of the automatic switching hydraulic control reversing valve 5, and then determines that the first hydraulic signal output proportional valve 7 or the second hydraulic signal output proportional valve 8 is located at a main control position. The mode of automatically switching the hydraulic control reversing valve 5 is used for changing the oil way of the system, so that the potential safety hazard that the spring is fatigue and fails due to frequent action or long-time compression of the spring when the valve core is reversed by spring force under the condition of long-term use is avoided. Meanwhile, the automatic switching hydraulic control reversing valve 5 does not belong to differential pressure type control reversing, so the manufacturability and the reliability of the automatic switching hydraulic control reversing valve 5 are better than those of a differential pressure type hydraulic control reversing valve, and the occurrence of the situations of valve core blocking of the hydraulic control valve and oil leakage through a matching gap between the valve core and a valve sleeve is greatly reduced.
When the automatic switching function is in failure, for example, the valve core of the switching electromagnetic valve 2 is subjected to card issuing, the valve core of the automatic switching hydraulic control reversing valve 5 is not in place in action, and the like, the manual switching valve 6 can realize the manual switching of the redundant output valve.
The manual switching valve 6 is provided with a first oil port, a second oil port and a third oil port, a handle of the manual switching valve 6 is manually rotated, the first hydraulic signal output proportional valve 7 or the second hydraulic signal output proportional valve 8 is determined to be located at a main control position by selecting a communication mode among the three oil ports, and meanwhile, a position switch arranged on the handle of the manual switching valve 6 can send a switching state signal of the manual switching valve 6 to a monitor and ensure that the switching is in place. The method specifically comprises the following steps: when the handle of the manual switching valve 6 is located at the position of 0 degree, the first oil port of the manual switching valve 6 is communicated with the second oil port, a hydraulic signal output by the output port B of the second hydraulic signal output proportional valve 8 finally enters the upper end control cavity of the main distributing valve 10, and the second hydraulic signal output proportional valve 8 is in a manual switching main state; when the manual switching valve 6 is in a 180-degree position, an oil port II of the manual switching valve 6 is communicated with an oil port III, a hydraulic signal output by an output port B of the hydraulic signal output proportional valve I7 finally enters an upper end control cavity of the main distributing valve 10, and the hydraulic signal output proportional valve I7 is in a manual switching main state; when the manual switching valve 6 is in a 90-degree position, the first oil port, the second oil port and the third oil port are not communicated with each other, and the manual switching control does not work due to the fact that the manual switching valve 6 does not have control output of a hydraulic control signal.
Example 4
As the best implementation mode of the invention, referring to the attached figure 1 of the specification, the invention comprises a control method of a hydraulic speed regulation system with manual automatic switching, which comprises a pressure oil source 1, a two-position four-way switching electromagnetic valve 2, a pressure relay I3 for monitoring the switching state, a pressure gauge 4, an automatic switching hydraulic control reversing valve 5, a manual switching valve 6, a hydraulic signal output proportional valve I7, a hydraulic signal output proportional valve II 8, a guide vane servomotor 9, a main pressure distributing valve 10, an emergency stop electromagnetic valve 11, an emergency stop hydraulic control reversing valve 12, a pressure relay II 13 for monitoring the stop, a maintenance ball valve I14 for maintaining the hydraulic signal output proportional valve I7, a maintenance ball valve II 15 for maintaining the hydraulic signal output proportional valve II 8 and a maintenance ball valve III 16 for maintaining the switching electromagnetic valve 2.
The main pressure distributing valve 10 includes an upper end control chamber, a valve core, and a lower end control chamber.
The manual switching valve 6 is provided with a first oil port, a second oil port and a third oil port, and the manual operation angles among the first oil port, the second oil port and the third oil port of the manual switching valve 6 are all 90 degrees. And the second oil port is finally connected with the upper end control cavity of the main pressure distribution valve 10 through the emergency stop hydraulic control reversing valve 12.
The switching electromagnetic valve 2 is a two-position four-way valve and is provided with a positioning device and a double-electromagnet structure. A port P of the switching electromagnetic valve 2 is connected with a pressure oil source 1, a port T is connected with return oil, a port A is connected with a Y control cavity of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with a pressure relay I3, and a port B is connected with an X control cavity of the automatic switching hydraulic control reversing valve 5 and is simultaneously connected with a pressure gauge 4; the port A of the automatic switching hydraulic control reversing valve 5 is connected with the port B of the hydraulic signal output proportional valve I7 and is simultaneously connected with the port III of the manual switching valve 6; the port B of the automatic switching hydraulic control reversing valve 5 is connected with the port B of the hydraulic signal output proportional valve II 8 and is also connected with the port I of the manual switching valve 6; the P ports of the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 are connected with a pressure oil source 1, the T ports are communicated with return oil, and hydraulic control signals enter an upper end control cavity of the main pressure distribution valve 10 through an emergency stop hydraulic control reversing valve 12 after being selected by the automatic switching hydraulic control reversing valve 5.
The control pressure oil source 1 respectively enters a P port of the switching electromagnetic valve 2, a P port of the first hydraulic signal output proportional valve 7, a P port of the second hydraulic signal output proportional valve 8 and a P port of the emergency stop electromagnetic valve 11, so that the T ports of the switching electromagnetic valve 2, the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8 are directly communicated with oil. The port A of the switching electromagnetic valve 2 is connected with the left end control cavity Y of the automatic switching hydraulic control reversing valve 5, and one path of the. The port B of the switching electromagnetic valve 2 is connected with the other control cavity X of the automatic switching hydraulic control reversing valve 5, and one path is led out and connected with the pressure gauge 4 at the same time, so that the change of the pressure of the hydraulic oil output from the port B of the switching electromagnetic valve 2 can be monitored in situ. And the port A and the port B of the automatic switching hydraulic control reversing valve 5 are respectively connected with the output ports B of the first hydraulic signal output proportional valve 7 and the second hydraulic signal output proportional valve 8, and the control signal output by the hydraulic signal output valve enters the upper end control cavity of the main pressure distribution valve 10 through the emergency stop hydraulic control reversing valve 12 after being selected by the automatic switching hydraulic control reversing valve 5.
When the right coil of the switching electromagnetic valve 2 is electrified, the switching electromagnetic valve 2 is positioned at a right station, the pressure oil source 1 enters a left control cavity of the automatic switching hydraulic control reversing valve 5 through the switching electromagnetic valve 2, a valve core of the automatic switching hydraulic control reversing valve 5 moves to the right under the action of pressure oil of the left control cavity, the valve core is positioned at a left station, and at the moment, hydraulic control oil output from a port B of the hydraulic signal output proportional valve II 8I enters an upper control cavity of the main pressure distribution valve 10 after passing through the automatic switching hydraulic control reversing valve 5 and the emergency shutdown hydraulic control reversing valve 12. At the moment, a pressure signal is reported by the first pressure relay 3, and the pressure gauge 4 displays that the system pressure is 0. When the coil at the left end of the switching electromagnetic valve 2 is electrified, a pressure-free signal is reported by the first pressure relay 3, and the pressure gauge 4 displays the system pressure.
The manual switching valve 6 has the function that when the automatic switching hydraulic control oil circuit has faults or a certain valve has the problems of valve core hairpin, channeling, oil leakage and the like, the manual switching is utilized, the on-line maintenance and the maintenance work of the faults of the automatic control part of the device are facilitated, the normal working time of a hydraulic system is prolonged, and the reliability and the maintainability of the system are improved.
The handle of the manual switching valve 6 is at a 90-degree position, at the moment, 3 control oil ports of the manual switching valve 6 are not communicated, the second oil port of the manual switching valve 6 does not control the output of hydraulic oil, the device is in an automatic switching control state, and the manual switching operation does not work.
In the actual movement process of the unit, the automatic switching control function is in a main state, and when the automatic switching loop fails, the redundant manual switching control is switched to. When the manual switching valve 6 is in the oil port communication between the first oil port and the second oil port, the hydraulic control signal output from the port B of the second hydraulic signal output proportional valve 8 enters the upper end control cavity of the main distributing valve 10 through the manual switching valve 6 and the emergency stop hydraulic control reversing valve 12, and the second hydraulic signal output proportional valve 8 is in the main position of manual switching. And similarly, when the manual switching valve 6 is positioned at the oil port three and is communicated with the oil port two, the hydraulic control signal output by the port B of the hydraulic signal output proportional valve I7 enters the upper end control cavity of the main distributing valve 10 after passing through the manual switching valve 6 and the emergency stop hydraulic control reversing valve 12, and the hydraulic signal output proportional valve I7 is positioned at the main position of manual switching. After being selected by the manual switching valve, the first hydraulic signal output proportional valve 7 or the second hydraulic signal output proportional valve 8 in the main position enters the upper end control cavity of the main pressure distribution valve 10 through the emergency stop hydraulic control reversing valve 12.
A spring is arranged in a lower end control cavity of the main pressure distributing valve 10, when the downward hydraulic pressure generated by the hydraulic oil in an upper end control cavity and the resultant force of the gravity of the main valve core are balanced with the spring force of the lower end, the main valve core is kept still, the oil port of a main valve switch cavity is sealed by a valve disc on the main valve core at the moment, and the guide vane servomotor 9 is kept still; when the spring force is greater than the hydraulic pressure and the gravity of the main valve spool, the main valve spool moves upwards, and the guide vane servomotor 9 is in a closed state; when the spring force is smaller than the hydraulic pressure and the gravity of the main valve spool, the main valve spool moves downwards, and the guide vane servomotor 9 is in an open state. The flow and the pressure of hydraulic oil entering the upper end control cavity of the main pressure distributing valve 10 are controlled by the hydraulic signal control output valve, so that the movement direction of the valve core of the main valve is controlled, and further the opening and the closing of the guide vane servomotor 9 of the water turbine are controlled or the guide vane servomotor 9 is kept at a certain fixed position without moving.
An inlet and an outlet of the first overhaul ball valve 14 are respectively communicated with the P port of the first hydraulic signal output proportional valve 7 and the pressure oil source 1, an inlet and an outlet of the second overhaul ball valve 15 are respectively communicated with the P port of the second hydraulic signal output proportional valve 8 and the pressure oil source 1, and an inlet and an outlet of the third overhaul ball valve 16 are respectively communicated with the P port of the switching electromagnetic valve 2 and the pressure oil source 1. When the maintenance is needed, the maintenance valves on the pressure oil paths of the valves are only needed to be closed. If the first hydraulic signal output proportional valve 7 needs to be overhauled or replaced, the first overhauling ball valve 14 is closed; when the second hydraulic signal output proportional valve 8 needs to be overhauled or replaced, the second overhauling ball valve 15 is closed; and when the switching electromagnetic valve 2 needs to be overhauled or replaced, the overhauling ball valve III 16 is closed. The maintenance and the replacement can be carried out on line, and the normal operation of the unit is not influenced. When the switching solenoid valve 2 is overhauled, the switching function needs to be switched to a manual switching control state.
The port P of the emergency stop electromagnetic valve 11 is connected with a pressure oil source 1, the port T is communicated with return oil, the port B is a working oil port communicated with a right end control cavity X of the emergency stop hydraulic control reversing valve 12, and the port A is a working oil port communicated with a left end control cavity Y of the emergency stop hydraulic control reversing valve 12. And a port P of the emergency stop hydraulic control reversing valve 12 is communicated with a port K of the automatic switching hydraulic control reversing valve 5 and a port II of the manual switching valve 6, a port T is communicated with return oil, and a port A is used as a unique hydraulic signal output port of the switching control device and is communicated with an upper end control cavity of the main pressure distribution valve 10.
When the unit needs emergency stop control, the electromagnet of the emergency stop electromagnetic valve 11 loses power, the valve core is reversed under the action of hydraulic control cavities at two ends of an emergency stop hydraulic control reversing valve 12, the control cavity at the upper end of the main pressure distributing valve 10 returns oil through the automatic switching hydraulic control reversing valve 5, and the valve core of the main valve moves upwards under the action of bottom spring force after losing downward acting force, so that the guide vane servomotor 9 is closed quickly. And an oil port of the second pressure relay 13 is communicated with an output port B of the emergency stop electromagnetic valve 11 and is used for monitoring whether the valve is in a normal or emergency stop state. When the unit normally operates, pressure oil is introduced into the second pressure relay 13; when an emergency shutdown accident occurs, the electromagnet of the emergency shutdown electromagnetic valve 11 loses power, the port B is communicated with return oil, the second pressure relay 13 is also communicated with the return oil, and the switch correspondingly acts and reports an emergency shutdown state signal of the speed regulating system to the monitoring system.
Referring to the attached figure 2 of the specification and the attached figure 4 of the specification, the switching electromagnetic valve 2, the first pressure relay 3, the second pressure relay 13, the pressure gauge 4, the automatic switching hydraulic control reversing valve 5, the manual switching valve 6, the first hydraulic signal output proportional valve 7, the second hydraulic signal output proportional valve 8, the first maintenance ball valve 14, the second maintenance ball valve 15, the third maintenance ball valve 16, the emergency stop electromagnetic valve 11 and the emergency stop hydraulic control reversing valve 12 are installed on an integrated valve block, and all oil paths are connected through inner pore channels of the valve block and are standard hydraulic elements. As a complete hydraulic control function module, the hydraulic control signal valve is suitable for various hydraulic control systems which require the functions of online switching, state reporting and displaying of the hydraulic control signal valve. Meanwhile, the module also has the function of manually switching the redundant proportional valve when the fault is automatically switched, and each electromagnetic valve pressure oil port is provided with a corresponding maintenance ball valve so as to facilitate the online maintenance and replacement operation of the valve. The integrated device has small volume, is convenient to install, has complete state detection points, and is convenient for fault analysis and state detection. After the hydraulic functional module is manufactured, no middle pipeline is connected, leakage points are reduced, and the appearance is neat, compact and attractive. The valve bank device is integrated by adopting standardized hydraulic components, has good interchange and universality, and is convenient to popularize and use in various hydraulic systems as a whole functional device.
In summary, after reading the present disclosure, those skilled in the art should make various other modifications without creative efforts according to the technical solutions and concepts of the present disclosure, which are within the protection scope of the present disclosure.
Claims (10)
1. A control method of a hydraulic speed regulating system with manual automatic switching is characterized in that: the hydraulic control system comprises a speed regulator controller, a pressure oil source (1), a switching electromagnetic valve (2), an automatic switching hydraulic control reversing valve (5), a manual switching valve (6), a hydraulic signal output proportional valve I (7), a hydraulic signal output proportional valve II (8), a guide vane servomotor (9) and a main pressure distribution valve (10); the main pressure distribution valve (10) comprises an upper end control cavity, a main valve core and a lower end control cavity, a spring is arranged in the lower end control cavity, and a switch cavity of an A, B port of the main pressure distribution valve (10) is respectively connected with a switch cavity of the guide vane servomotor (9) through an oil pipeline; after the automatic control mode or the manual control mode is switched, the output port of a first hydraulic signal output proportional valve (7) or a second hydraulic signal output proportional valve (8) at the main control position is connected with the upper end control cavity of the main pressure distribution valve (10) and is matched with a spring in the lower end control cavity of the main pressure distribution valve (10) to control the valve core of the main valve to move up and down and control the opening and closing of the guide vane servomotor (9);
the automatic control mode specifically refers to:
the switching electromagnetic valve (2) controls the station of the automatic switching hydraulic control reversing valve (5) through the control cavities at the two ends of the automatic switching hydraulic control reversing valve (5) to determine that the hydraulic signal output proportional valve I (7) or the hydraulic signal output proportional valve II (8) is in the master control position;
wherein the manual control mode specifically refers to:
the manual switching valve (6) is provided with an oil port I, an oil port II and an oil port III, a handle of the manual switching valve (6) is manually rotated, and the hydraulic signal output proportional valve I (7) or the hydraulic signal output proportional valve II (8) is determined to be located at a master control position by selecting a communication mode among the three oil ports.
2. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 1, characterized in that: the hydraulic control directional control valve for the emergency shutdown is characterized by further comprising an emergency shutdown electromagnetic valve (11) and an emergency shutdown hydraulic control directional valve (12), wherein the output port of the first hydraulic signal output proportional valve (7) or the second hydraulic signal output proportional valve (8) in the main control position is connected with the upper end control cavity of the main pressure distribution valve (10) through the emergency shutdown hydraulic control directional valve (12), the output port B of the emergency shutdown electromagnetic valve (11) is communicated with the right end control cavity X of the emergency shutdown hydraulic control directional valve (12), and the output port A is communicated with the left end control cavity Y of the emergency shutdown hydraulic control directional valve (12).
3. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 2, characterized in that: the emergency stop electromagnetic valve (11) is a single-coil emergency stop electromagnetic valve.
4. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 3, characterized in that: still include pressure relay (3), manometer (4) and pressure relay two (13), the hydraulic fluid port of pressure relay (3) links to each other with the delivery outlet A of switching solenoid valve (2), the pressure measurement mouth of manometer (4) links to each other with the delivery outlet B of switching solenoid valve (2), the hydraulic fluid port of pressure relay two (13) communicates with each other with the delivery outlet B of emergency shutdown solenoid valve (11).
5. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 4, characterized in that: the hydraulic signal output proportional valve is characterized by further comprising a first overhaul ball valve (14), a second overhaul ball valve (15) and a third overhaul ball valve (16), an inlet and an outlet of the first overhaul ball valve (14) are communicated with a P port of a first hydraulic signal output proportional valve (7) and a pressure oil source (1) respectively, an inlet and an outlet of the second overhaul ball valve (15) are communicated with a P port of a second hydraulic signal output proportional valve (8) and the pressure oil source (1) respectively, and an inlet and an outlet of the third overhaul ball valve (16) are communicated with a P port of a switching electromagnetic valve (2) and the pressure oil source (1) respectively.
6. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 5, characterized in that: the hydraulic control switching valve is characterized in that the switching electromagnetic valve (2), the first pressure relay (3), the second pressure relay (13), the pressure gauge (4), the automatic switching hydraulic control reversing valve (5), the manual switching valve (6), the first hydraulic signal output proportional valve (7), the second hydraulic signal output proportional valve (8), the first maintenance ball valve (14), the second maintenance ball valve (15), the third maintenance ball valve (16), the emergency shutdown electromagnetic valve (11) and the emergency shutdown hydraulic control reversing valve (12) are installed on an integrated valve block, and all oil paths are connected through inner hole channels of the valve block.
7. The control method of the hydraulic speed regulating system with the manual automatic switching function according to claim 1 or 6, characterized in that: the switching electromagnetic valve (2) is a two-position four-way valve and adopts a structure with double electromagnets for locking positions.
8. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 6, characterized in that: the switching solenoid valve (2), the first pressure relay (3), the second pressure relay (13), the pressure gauge (4), the automatic switching hydraulic control reversing valve (5), the manual switching valve (6), the first hydraulic signal output proportional valve (7), the second hydraulic signal output proportional valve (8), the first maintenance ball valve (14), the second maintenance ball valve (15), the third maintenance ball valve (16), the emergency shutdown solenoid valve (11) and the emergency shutdown hydraulic control reversing valve (12) all adopt standardized hydraulic components.
9. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 7, characterized in that: the automatic switching hydraulic control reversing valve (5) is of a two-position four-way sliding valve structure, and two ends of a control piston of the automatic switching hydraulic control reversing valve (5) are respectively communicated with a pressure oil source (1) and return oil.
10. The control method of the hydraulic speed regulating system with the automatic manual switching function according to claim 9, characterized in that: the manual operation angles among the first oil port, the second oil port and the third oil port of the manual switching valve (6) are all 90 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010250257.8A CN111336151B (en) | 2020-04-01 | 2020-04-01 | Control method of hydraulic speed regulation system with manual automatic switching function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010250257.8A CN111336151B (en) | 2020-04-01 | 2020-04-01 | Control method of hydraulic speed regulation system with manual automatic switching function |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111336151A CN111336151A (en) | 2020-06-26 |
| CN111336151B true CN111336151B (en) | 2021-08-13 |
Family
ID=71178720
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010250257.8A Active CN111336151B (en) | 2020-04-01 | 2020-04-01 | Control method of hydraulic speed regulation system with manual automatic switching function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111336151B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114198355B (en) * | 2021-12-07 | 2023-11-17 | 重庆红江机械有限责任公司 | Hydraulic reversing device of electro-hydraulic speed regulator |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4039010A (en) * | 1975-11-03 | 1977-08-02 | J. I. Case Company | Hydraulic circuit for tree harvesting implement |
| EP0314164B1 (en) * | 1987-10-29 | 1992-03-25 | Nissan Motor Co., Ltd. | Actively controlled suspension system with control characteristics variable depending upon vehicular speed |
| JPH10115280A (en) * | 1996-10-09 | 1998-05-06 | Meidensha Corp | Speed governor |
| CN201025232Y (en) * | 2007-04-03 | 2008-02-20 | 武汉东顺机械制造有限公司 | Mechanical hydraulic pressure system with speed adjuster capable of automatic center recovery function |
| CN203548054U (en) * | 2013-09-22 | 2014-04-16 | 东方电机控制设备有限公司 | Hydraulic device for water turbine speed control and protection system |
| CN108119419A (en) * | 2016-11-29 | 2018-06-05 | 沈阳格泰水电设备有限公司 | A kind of electrohydraulic servo system of new type hydraulic turbine governor |
| CN110080934A (en) * | 2019-06-04 | 2019-08-02 | 东方电气自动控制工程有限公司 | Hydrogovernor with start and stop defencive function |
-
2020
- 2020-04-01 CN CN202010250257.8A patent/CN111336151B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4039010A (en) * | 1975-11-03 | 1977-08-02 | J. I. Case Company | Hydraulic circuit for tree harvesting implement |
| EP0314164B1 (en) * | 1987-10-29 | 1992-03-25 | Nissan Motor Co., Ltd. | Actively controlled suspension system with control characteristics variable depending upon vehicular speed |
| JPH10115280A (en) * | 1996-10-09 | 1998-05-06 | Meidensha Corp | Speed governor |
| CN201025232Y (en) * | 2007-04-03 | 2008-02-20 | 武汉东顺机械制造有限公司 | Mechanical hydraulic pressure system with speed adjuster capable of automatic center recovery function |
| CN203548054U (en) * | 2013-09-22 | 2014-04-16 | 东方电机控制设备有限公司 | Hydraulic device for water turbine speed control and protection system |
| CN108119419A (en) * | 2016-11-29 | 2018-06-05 | 沈阳格泰水电设备有限公司 | A kind of electrohydraulic servo system of new type hydraulic turbine governor |
| CN110080934A (en) * | 2019-06-04 | 2019-08-02 | 东方电气自动控制工程有限公司 | Hydrogovernor with start and stop defencive function |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111336151A (en) | 2020-06-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111350627B (en) | Hydraulic speed regulation control system with automatic hand switching function | |
| CN101696641B (en) | Electronically controllable and testable turbine trip system | |
| CA1122880A (en) | Hydraulic control valve unit | |
| US4637587A (en) | Facility for the monitoring of physical quantities on systems | |
| US4181017A (en) | Fault detecting apparatus for fluid pressure systems | |
| CN111336151B (en) | Control method of hydraulic speed regulation system with manual automatic switching function | |
| CN211874850U (en) | Hydraulic system with hand automatic switching function | |
| US5143119A (en) | Drive for a feed valve | |
| CN113345289A (en) | Training device and method for water turbine speed governor | |
| US4019390A (en) | System and method for complete on line testing of a mechanical overspeed trip channel associated with an electrohydraulic emergency trip system for a turbine power plant | |
| CN104235109B (en) | Axial flow compressor servo closed loop redundant electrohydraulic proportional control apparatus | |
| CN210660418U (en) | Hydraulic control system of hydraulic turbine speed regulator of hydraulic amplification mechanism | |
| CN109236803B (en) | Hydraulic system with redundancy protection function | |
| CN112727819B (en) | Servo redundant control system of steam turbine | |
| CN113503275A (en) | Intelligent servo hoist system for ship lock | |
| CN218062408U (en) | Two-out-one-speed closing valve control module capable of realizing online test of steam turbine | |
| CN212206572U (en) | Valve on-line partial stroke test and system switching device | |
| CN109458292B (en) | Self-holding self-closing method for speed regulator power failure | |
| CN109236553B (en) | Overspeed protection and flow control method for pumped storage power station | |
| RU176944U1 (en) | Electro-hydraulic column of a turbine speed controller | |
| CN109611396B (en) | Automatic oil supply switching hydraulic system and method for large-ladle sliding gate hydraulic cylinder | |
| CN203906450U (en) | Safety device for oil hydraulic circuit | |
| JPH0255840B2 (en) | ||
| KR102458799B1 (en) | Redundant system and method of hydraulic servo valve for safety control of turbine control actuator for power plants | |
| CN218000006U (en) | Digital barrel valve hydraulic control system capable of being closed independently |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |