Dual-redundancy servo valve hydraulic servo-motor for steam turbine
By designing a dual redundant servo valve oil motor, using a dual redundant servo valve group and switching solenoid valve, the problem of degradation of control capability caused by servo valve jamming is solved, the continuous operation and rapid response of the turbine are achieved, and the reliability and safety of the system are improved.
Patent Information
- Application Number
- CN202422404135.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-09-30
- Publication Date
- 2025-08-29
- Estimated Expiration
- 2034-09-30
AI Technical Summary
The existing turbine servo valves are prone to jamming during operation, resulting in a decrease in control capabilities, affecting unit performance and safety, especially in rapid response situations, increasing the risk of accidents, and repair or replacement leads to production interruptions and economic losses.
A dual redundant servo valve oil motor for steam turbines is designed, and a dual redundant servo valve group and a switching solenoid valve are used to ensure that the other servo valve can work normally when one servo valve fails. By switching the solenoid valve, the continuous operation of the system is achieved, and the control accuracy and response speed are improved through components such as servo cards, oil blocks and pressure measuring joints.
It improves the reliability and safety of the system, reduces downtime and maintenance costs, ensures continuous operation and rapid response of the system, and improves control performance and work efficiency.
Smart Images
Figure CN223282306U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of oil motors, and specifically provides a double-redundant servo valve oil motor for a steam turbine. Background Art
[0002] The steam turbine digital electro-hydraulic control system is an important component of the power plant's DCS system. Its main function is to automatically monitor, regulate, control, and protect the entire process of steam turbine startup, operation, and shutdown. It is both an electro-hydraulic conversion element and a power amplifier element. It can convert weak electrical input signals of low power into high-power hydraulic energy output. In the electro-hydraulic servo system, it connects the electrical part and the hydraulic part to achieve electro-hydraulic signal conversion and hydraulic amplification.
[0003] Once the servo valve in the existing technology gets stuck during the operation of the unit, its control ability is affected, resulting in a decrease in turbine performance, reduced output power or efficiency, and untimely or inaccurate system response, thereby increasing the risk of accidents. Especially in situations where a quick response is required, such as emergency shutdown or load adjustment, in serious cases, it will endanger the operation safety of the unit; when the servo valve is stuck, it is necessary to shut down for maintenance or replacement, resulting in production interruption and loss of production capacity, affecting the economic benefits of the enterprise.
[0004] Accordingly, the art requires a new dual-redundant servo valve oil motor for a steam turbine to solve the above technical problems. Utility Model Content
[0005] The utility model aims to solve the above technical problem, that is, to solve the problem that the existing unit must suspend work and interrupt production when a problem occurs in the servo valve.
[0006] The utility model provides a dual-redundant servo valve oil motor for a steam turbine, the oil motor comprising an oil cylinder, two servo valve groups, a switching solenoid valve and a measuring component, wherein:
[0007] The cylinder body of the oil cylinder has a rod cavity and a rodless cavity;
[0008] The measuring component is used to detect the movement information of the piston rod of the oil cylinder;
[0009] Each of the servo valve groups includes a servo valve and a hydraulic isolation valve; in each of the servo valve groups, the servo valve has a first oil port, a second oil port, a third oil port and a fourth oil port, and the hydraulic isolation valve has a fifth oil port, a sixth oil port, a seventh oil port, an eighth oil port and a ninth oil port for communicating with the hydraulic cavity of the hydraulic isolation valve, wherein the first oil port is connected to a high-pressure oil source, the second oil port is connected to an oil return line, the third oil port is connected to the fifth oil port, and the fourth oil port is connected to the sixth oil port; when the servo valve is in a first state, the first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; when the servo valve is in a first state, the first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; In the second state, the first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port; when the servo valve is in the third state, the first oil port, the second oil port, the third oil port and the fourth oil port are isolated from each other; the seventh oil port of the hydraulic isolation valve is connected to the rodless chamber of the cylinder, and the eighth oil port of the hydraulic isolation valve is connected to the rod chamber of the cylinder; when the hydraulic isolation valve is in the first state, the fifth oil port is connected to the eighth oil port, and the sixth oil port is connected to the seventh oil port; when the hydraulic isolation valve is in the second state, the fifth oil port, the sixth oil port, the seventh oil port and the eighth oil port are isolated from each other;
[0010] A switching solenoid valve, the switching solenoid valve having a tenth oil port, an eleventh oil port, a twelfth oil port and a thirteenth oil port, wherein the tenth oil port is connected to the ninth oil port of the hydraulic isolation valve in one of the servo valve groups, and the eleventh oil port is connected to the ninth oil port of the hydraulic isolation valve in another of the servo valve groups; the twelfth oil port is connected to a high-pressure oil source, and the thirteenth oil port is connected to an oil return line; when the switching solenoid valve is in a first state, the tenth oil port is connected to the twelfth oil port, and the eleventh oil port is connected to the thirteenth oil port; when the switching solenoid valve is in a second state, the tenth oil port is connected to the thirteenth oil port, and the eleventh oil port is connected to the twelfth oil port.
[0011] Based on the above structural setting, the reliability and safety of the system are significantly improved by adopting a dual redundant servo valve group. When one servo valve group fails, the other servo valve group can still work normally to ensure the continuous operation of the system; the design of the switching solenoid valve enables the system to automatically switch to the backup servo valve group when an abnormal situation is detected, ensuring that the system can respond in time, reducing downtime and maintenance costs; the oil circuit control design ensures the precise positioning and rapid response of the cylinder piston rod, improving the control performance and work efficiency of the system.
[0012] In the preferred technical solution of the above-mentioned hydraulic motor, each of the servo valve groups further includes a servo card, and the servo card is used to send a control signal to the servo valve.
[0013] Based on the above structural setting, the servo card provides precise control signals, enabling the servo valve to efficiently and accurately adjust the on-off state of the oil circuit, improving the control accuracy and response speed of the system; with the help of the servo card, while monitoring the system status in real time, the operation of the servo valve can be flexibly adjusted as needed, achieving a more flexible and efficient working mode.
[0014] In the preferred technical solution of the above-mentioned hydraulic motor, the servo valve group also includes a servo valve oil circuit block and a main oil circuit block. Oil circuits are formed inside the servo valve oil circuit block and the main oil circuit block. The oil circuit of the servo valve oil circuit block is used to install the oil circuit between the two servo valve groups and the switching solenoid valve, and the oil circuit of the main oil circuit block is used to install the oil circuit between the oil cylinder and the servo valve oil circuit block.
[0015] Based on the above structural setting, the separate design of the servo valve oil circuit block and the main oil circuit block makes the system more convenient during installation and maintenance, greatly reducing the difficulty and time of installation and maintenance; by integrating various channels through the oil circuit block, the oil circuit layout is simplified, the complexity of the pipeline and the potential risk of leakage are reduced, and the reliability and stability of the system are improved.
[0016] In the preferred technical solution of the above-mentioned hydraulic motor, the main oil circuit block is connected to an oil circuit pipe joint, and the oil cylinder is connected to a pressure measuring joint for respectively detecting the pressure of the rod chamber and the rodless chamber in the oil cylinder.
[0017] Based on the above-mentioned structural setting, the design of the oil circuit pipe joint and the pressure measuring joint enables real-time monitoring of the pressure in the rod chamber and the rodless chamber, providing rich operating data, facilitating timely detection of system anomalies and preventive maintenance; the data from the pressure measuring joint can be used in the feedback control system to further improve the motion control accuracy of the cylinder piston.
[0018] In the preferred technical solution of the above-mentioned hydraulic motor, a pressure differential switch for controlling the servo valve is further provided on the main oil circuit block.
[0019] Based on the above structural setting, the introduction of the pressure differential switch enables the system to monitor the operating status of the servo valve in real time, detect and handle faults in a timely manner, and avoid system shutdowns and safety accidents caused by servo valve failures; through pressure differential switch monitoring, emergency response measures can be quickly taken when an abnormality occurs, significantly improving the safety and reliability of the system.
[0020] In the preferred technical solution of the above-mentioned hydraulic motor, a manual isolation valve is provided between the first oil port of the servo valve and the high-pressure oil source.
[0021] Based on the above structural setting, the design of the manual isolation valve enables the high-pressure oil source to be quickly cut off in maintenance or emergency situations to protect the safety of the system and personnel; through the manual isolation valve, local repairs and component replacements can be carried out without affecting the operation of the entire system, thereby improving the maintenance efficiency of the system.
[0022] In the preferred technical solution of the above oil motor, a filter is provided on the manual isolation valve, and the filter is fixed to the main oil circuit block through a mounting block.
[0023] Based on the above structural setting, the setting of the filter can effectively prevent impurities from entering the high-pressure oil circuit, protect the servo valve and other precision components, and improve the durability and working reliability of the system; the filter is installed on the main oil circuit block, which is convenient for regular inspection and replacement of the filter to ensure that the system is always in the best working condition.
[0024] In the preferred technical solution of the above-mentioned hydraulic motor, the servo valve oil circuit block, the manual isolation valve, the hydraulic isolation valve, the servo valve, and the switching solenoid valve are all fixed by hexagonal cylindrical head screws.
[0025] Based on the above structural setting, the use of hexagonal cylindrical head screws ensures a firm connection between key components, avoids loosening and leakage, and ensures the long-term stable operation of the system; the unified fixing method makes the system layout more neat, simplifies the installation process, and helps to achieve standardized production and maintenance.
[0026] In the preferred technical solution of the above-mentioned hydraulic motor, the measuring component includes a displacement sensor, a mounting base plate, a stroke scale and a connecting component. The first end of the displacement sensor is fixed to one side of the cylinder through the mounting base plate, and the second end of the displacement sensor is fixedly connected to the oil port of the cylinder through the connecting component for testing the displacement information of the oil port of the cylinder; the first end of the stroke scale is also fixedly connected to the side of the connecting component away from the displacement sensor, and the second end of the stroke scale is fixedly connected to the cylinder for marking the stroke information of the oil port of the cylinder.
[0027] Based on the above structural setting, the combined design of the displacement sensor and the stroke scale can accurately measure the displacement information of the cylinder piston, provide accurate feedback data for the control system, and improve control accuracy; the application of the stroke scale allows the operator to intuitively see the movement stroke of the piston, which is convenient for operation monitoring and troubleshooting.
[0028] In the preferred technical solution of the above-mentioned hydraulic motor, two displacement sensors are arranged in parallel.
[0029] Based on the above structural setting, the two parallel displacement sensors can back up each other. When one sensor fails, the other sensor can still be used, further improving the reliability and fault tolerance of the system; the dual sensors can calibrate each other to provide more accurate and reliable position information, optimizing the control performance of the system. BRIEF DESCRIPTION OF THE DRAWINGS
[0030] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:
[0031] Figure 1 Shows a schematic diagram of the overall structure of the utility model;
[0032] Figure 2 Shows the right side view of the overall structure of the utility model;
[0033] Figure 3 Shows a front view of the overall structure of the utility model;
[0034] Figure 4 Shows a left view of the overall structure of the utility model;
[0035] Figure 5 Shows a rear view of the overall structure of the utility model;
[0036] Figure 6 Shows the oil circuit principle diagram of the utility model;
[0037] Reference numerals:
[0038] 1. Cylinder; 2. Main oil circuit block; 3. Servo valve oil circuit block; 4. Servo valve; 5. Switching solenoid valve; 6. Differential pressure switch; 7. Mounting block; 8. Filter; 9. Check valve; 10. Manual isolation valve; 11. Hydraulic isolation valve; 12. Hexagonal plug; 13. Oil pipe joint; 14. Mounting base plate; 15. Displacement sensor; 16. Travel scale; 17. Pressure measuring joint. DETAILED DESCRIPTION
[0039] The following describes preferred embodiments of the present invention with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely intended to illustrate the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. Those skilled in the art may adjust these embodiments as needed to suit specific applications.
[0040] It should be noted that in the description of this utility model, terms such as "center," "upper," "lower," "left," "right," "inner," and "outer" indicating directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings. This is merely for ease of description and does not indicate or imply that the structure described must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, it should not be understood as limiting the utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be understood to indicate or imply relative importance.
[0041] Furthermore, it should be noted that, in the description of this utility model, unless otherwise expressly specified or limited, the terms "connected," "connected," and "connection" should be understood in a broad sense. For example, they can refer to fixed connections or detachable connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.
[0042] See below Figures 1 to 6 ,like Figures 1 to 6 As shown, the utility model provides a dual redundant servo valve 4 oil motor for a steam turbine, the oil motor includes an oil cylinder 1, two servo valve groups, a switching solenoid valve 5 and a measuring component, wherein:
[0043] The cylinder body of the oil cylinder 1 has a rod cavity and a rodless cavity; it should be noted that the present invention does not impose any restrictions on the specific structure of the oil cylinder 1, and those skilled in the art can set it according to their needs. For example, the oil cylinder 1 can be a single-piston standard oil cylinder 1, or for another example, the oil cylinder 1 can also be a multi-piston compound oil cylinder 1, as long as it is ensured that the oil cylinder 1 can meet the movement requirements of the oil motor.
[0044] The measuring component is used to detect the movement information of the piston rod of the oil cylinder 1;
[0045] Each servo valve group includes a servo valve 4 and a hydraulic isolation valve 11; in each servo valve group, the servo valve 4 has a first oil port, a second oil port, a third oil port and a fourth oil port, and the hydraulic isolation valve 11 has a fifth oil port, a sixth oil port, a seventh oil port, an eighth oil port and a ninth oil port for communicating with the hydraulic cavity of the hydraulic isolation valve 11, wherein the first oil port is connected to the high-pressure oil source, the second oil port is connected to the return oil line, the third oil port is connected to the fifth oil port, and the fourth oil port is connected to the sixth oil port; when the servo valve 4 is in the first state, its first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; when the servo valve 4 is in the second state, its first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port; when the servo valve 4 is in the third state, the first oil port, the second oil port, the seventh oil port, the eighth oil port and the ninth oil port are connected The third oil port and the fourth oil port are isolated from each other; the seventh oil port of the hydraulic isolation valve 11 is connected to the rodless chamber of the cylinder 1, and the eighth oil port of the hydraulic isolation valve 11 is connected to the rod chamber of the cylinder 1; when the hydraulic isolation valve 11 is in the first state, the fifth oil port is connected to the eighth oil port, and the sixth oil port is connected to the seventh oil port; when the hydraulic isolation valve 11 is in the second state, the fifth oil port, the sixth oil port, the seventh oil port and the eighth oil port are isolated from each other; of course, it should be noted that the present invention does not impose any restrictions on the specific type of the servo valve 4, and those skilled in the art can set it according to their needs. For example, the servo valve 4 can be an electric valve, or for example, the servo valve 4 can also be a pneumatic valve, as long as the servo valve 4 can meet the use of the oil motor, in this preferred embodiment, the servo valve 4 is a three-position four-way electro-hydraulic servo valve 4.
[0046] The switching solenoid valve 5 has a tenth oil port, an eleventh oil port, a twelfth oil port, and a thirteenth oil port. The tenth oil port is connected to the ninth oil port of the hydraulic isolation valve 11 in one servo valve group, and the eleventh oil port is connected to the ninth oil port of the hydraulic isolation valve 11 in another servo valve group; the twelfth oil port is connected to the high-pressure oil source, and the thirteenth oil port is connected to the return oil line; when the switching solenoid valve 5 is in the first state, the tenth oil port is connected to the twelfth oil port, and the eleventh oil port is connected to the thirteenth oil port; when the switching solenoid valve 5 is in the second state, the tenth oil port is connected to the thirteenth oil port, and the eleventh oil port is connected to the twelfth oil port. It should be noted that the present invention does not impose any restrictions on the specific type of the switching solenoid valve 5. Those skilled in the art can set it according to their needs. For example, the solenoid switching valve can be an air switching valve, or for example, the solenoid switching valve can also be a waste nitrogen switching valve, as long as the solenoid switching valve can switch the servo valve 4 as required. In this preferred embodiment, the solenoid switching valve is a two-position four-way valve.
[0047] The use of dual redundant servo valve groups significantly improves the reliability and safety of the system. When one servo valve group fails, the other servo valve group can still work normally, ensuring the continuous operation of the system. The design of switching solenoid valve 5 enables the system to automatically switch to the backup servo valve group when an abnormal situation is detected, ensuring that the system can respond in time, reducing downtime and maintenance costs. The oil circuit control design ensures the precise positioning and rapid response of the piston rod of cylinder 1, improving the control performance and working efficiency of the system.
[0048] When the servo valve 4 is in the first state, the first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port. The hydraulic oil flows from the high-pressure oil source into the first oil port and flows to the fifth oil port of the hydraulic isolation valve 11 through the third oil port; the return oil flows from the fourth oil port to the return oil pipeline and passes through the second oil port.
[0049] When the servo valve 4 is in the second state, the first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port. The hydraulic oil flows from the high-pressure oil source into the first oil port and flows to the sixth oil port of the hydraulic isolation valve 11 through the fourth oil port; the return oil flows from the third oil port to the return oil pipeline and passes through the second oil port.
[0050] When the servo valve 4 is in the third state, all oil ports are isolated from each other. In this state, hydraulic oil neither flows into nor flows out of the servo valve 4, and the oil circuit is completely isolated.
[0051] When the hydraulic isolation valve 11 is in the first state, the fifth oil port is connected to the eighth oil port, and the sixth oil port is connected to the seventh oil port. If the servo valve 4 is in the first state, the hydraulic oil will flow from the fifth oil port into the rod chamber of the cylinder, and at the same time, the oil will return from the rodless chamber through the sixth oil port to the seventh oil port; if the servo valve 4 is in the second state, the hydraulic oil will flow from the sixth oil port into the rodless chamber of the cylinder, and at the same time, the oil will return from the rod chamber through the fifth oil port to the eighth oil port.
[0052] When the hydraulic isolation valve 11 is in the second state, all oil ports are isolated from each other. In this state, hydraulic oil cannot flow from the hydraulic isolation valve 11 to the oil cylinder, and the oil circuit is completely isolated.
[0053] When the switching solenoid valve 5 is in the first state, the tenth oil port is connected to the twelfth oil port, and the eleventh oil port is connected to the thirteenth oil port, which allows the hydraulic isolation valve 11 of one servo valve group to be connected to the high-pressure oil source and the other to be connected to the return oil line, thereby selectively activating one servo valve group. This connection enables the hydraulic isolation valve 11 of one servo valve group to receive the high-pressure oil source, while the other receives the return oil, allowing one group to operate with full function while the other group is at rest.
[0054] When the switching solenoid valve 5 is in the second state, the tenth oil port is connected to the thirteenth oil port, and the eleventh oil port is connected to the twelfth oil port. The connection in this state is opposite to that in the first state, changing the flow direction of the hydraulic oil, thereby switching to another servo valve group, so that the other servo valve group receives the high-pressure oil source, while the previous group receives the return oil.
[0055] Furthermore, each servo valve assembly includes a servo card, which is used to send control signals to the servo valve 4. It should be noted that the present invention does not impose any restrictions on the specific type of servo card, and those skilled in the art can customize it according to their needs, as long as the servo card can control the normal operation of the corresponding servo valve 4. The servo card provides precise control signals, allowing the servo valve 4 to efficiently and accurately adjust the on-off state of the oil circuit, improving the control accuracy and response speed of the system. With the servo card, the operation of the servo valve 4 can be flexibly adjusted as needed while monitoring the system status in real time, achieving a more flexible and efficient operating mode.
[0056] Furthermore, the servo valve group also includes a servo valve oil circuit block 3 and a main oil circuit block 2. Oil passages are formed inside the servo valve oil circuit block 3 and the main oil circuit block 2. The oil passage of the servo valve oil circuit block 3 is used to install the oil circuit between the two servo valve groups and the switching solenoid valve 5, and the oil passage of the main oil circuit block 2 is used to install the oil circuit between the oil cylinder 1 and the servo valve oil circuit block 3. It should be noted that the present invention does not impose any restrictions on the specific structure of the servo valve oil circuit block 3 and the main oil circuit block 2. Those skilled in the art can set them according to their needs. For example, the servo valve oil circuit block 3 and the main oil circuit block 2 can be square structures. For another example, the servo valve oil circuit block 3 and the main oil circuit block 2 can be irregular polygonal structures, as long as the servo valve oil circuit block 3 and the main oil circuit block 2 can accommodate the various oil port connection pipelines of the hydraulic motor. The separate design of the servo valve oil circuit block 3 and the main oil circuit block 2 makes the system more convenient during installation and maintenance, greatly reducing the difficulty and time of installation and maintenance; the integration of various channels through the oil circuit block simplifies the oil circuit layout, reduces the complexity of the pipeline and the potential risk of leakage, and improves the reliability and stability of the system.
[0057] Furthermore, an oil circuit pipe joint 13 is connected to the main oil circuit block 2, and a pressure measuring joint 17 is connected to the oil cylinder 1, which are used to detect the pressure of the rod cavity and the rodless cavity in the oil cylinder 1 respectively. It should be noted that the present invention does not impose any restrictions on the specific connection method of the oil circuit pipe joint 13 and the pressure measuring joint 17. Those skilled in the art can set it according to their needs. For example, the oil circuit pipe joint 13 and the pressure measuring joint 17 can be fixedly connected by screwing. For another example, the oil circuit pipe joint 13 and the pressure measuring joint 17 can also be fixedly connected by plugging. As long as the sealing between the pipe connections is good, it can be used for a long time. The design of the oil circuit pipe joint 13 and the pressure measuring joint 17 makes it possible to monitor the pressure of the rod cavity and the rodless cavity in real time, providing rich operating data, facilitating timely detection of system abnormalities and preventive maintenance; the data of the pressure measuring joint 17 can be used in the feedback control system to further improve the motion control accuracy of the piston of the oil cylinder 1.
[0058] Furthermore, the main oil circuit block 2 is also provided with a pressure differential switch 6 for controlling the servo valve 4. The introduction of the pressure differential switch 6 enables the system to monitor the operating status of the servo valve 4 in real time, promptly detecting and addressing faults, thereby avoiding system downtime and safety accidents caused by servo valve 4 failures. Monitoring by the pressure differential switch 6 allows for rapid emergency response measures in the event of an anomaly, significantly improving the safety and reliability of the system.
[0059] Furthermore, a manual isolation valve 10 is provided between the first oil port of the servo valve 4 and the high-pressure oil source. It should be noted that the present invention does not impose any restrictions on the specific type of manual isolation valve 10, and those skilled in the art can set it according to their needs. For example, the manual isolation valve 10 can be a throttle valve, or a check valve, as long as the manual isolation valve 10 can be opened and closed according to user needs. The design of the manual isolation valve 10 allows the high-pressure oil source to be quickly cut off during maintenance or emergency situations, protecting the safety of the system and personnel. The manual isolation valve 10 allows for local repairs and component replacement without affecting the operation of the entire system, thereby improving the maintenance efficiency of the system.
[0060] Furthermore, a filter 8 is provided on the manual isolation valve 10, and the filter 8 is fixed to the main oil circuit block 2 through the mounting block 7. It should be noted that the present invention does not impose any restrictions on the specific type of the filter 8, and those skilled in the art can set it according to their needs. For example, the filter 8 can be a glass fiber filter element oil filter, or a stainless steel filter element oil filter, as long as it is ensured that the filter 8 can filter the oil well. The setting of the filter 8 can effectively prevent impurities from entering the high-pressure oil circuit, protect the servo valve 4 and other precision components, and improve the durability and working reliability of the system; the filter 8 is installed on the main oil circuit block 2, which is convenient for regular inspection and replacement of the filter 8 to ensure that the system is always in the best working condition.
[0061] As a preferred embodiment, the servo valve oil circuit block 3, the manual isolation valve 10, the hydraulic isolation valve 11, the servo valve 4, and the switching solenoid valve 5 are all fixed by hexagonal cylindrical head screws 12. The use of the hexagonal cylindrical head screws 12 ensures that the key components are firmly connected, avoids loosening and leakage, and ensures the long-term stable operation of the system; the unified fixing method makes the system layout more neat, simplifies the installation process, and helps to achieve standardized production and maintenance. Of course, the present invention does not impose any restrictions on the fixing method between the servo valve oil circuit block 3, the manual isolation valve 10, the hydraulic isolation valve 11, the servo valve 4, and the switching solenoid valve 5. Those skilled in the art can set it according to their needs, as long as it can ensure that the servo valve oil circuit block 3, the manual isolation valve 10, the hydraulic isolation valve 11, the servo valve 4, and the switching solenoid valve 5 can be stably installed.
[0062] Furthermore, the measurement assembly includes a displacement sensor 15, a mounting base 14, a stroke scale 16, and a connecting assembly. The first end of the displacement sensor 15 is fixed to one side of the cylinder 1 via the mounting base 14. The second end of the displacement sensor 15 is fixedly connected to the oil port of the cylinder 1 via the connecting assembly, used to measure the displacement information of the oil port of the cylinder 1. The first end of the stroke scale 16 is also fixedly connected to the side of the connecting assembly away from the displacement sensor 15. The second end of the stroke scale 16 is fixedly connected to the cylinder 1 and used to indicate the stroke information of the oil port of the cylinder 1. The combination of the displacement sensor 15 and the stroke scale 16 can accurately measure the displacement information of the piston in the cylinder 1, providing accurate feedback data to the control system and improving control accuracy. The use of the stroke scale 16 allows the operator to intuitively see the movement stroke of the piston, facilitating operation monitoring and troubleshooting. It should be noted that the present invention does not impose any restrictions on the specific structure of the stroke scale 16. Those skilled in the art can customize it according to their needs, as long as the stroke scale 16 is sufficient to measure the piston stroke of the hydraulic motor. Two displacement sensors 15 are arranged in parallel. The two parallel displacement sensors 15 can back up each other. When one sensor fails, the other sensor can still be used, further improving the reliability and fault tolerance of the system. The dual sensors can calibrate each other to provide more accurate and reliable position information and optimize the control performance of the system.
[0063] Working principle:
[0064] Hydraulic oil is distributed from an oil source through a main oil supply pipeline to two independent servo valve groups, and the two servo valve groups are configured as a first servo valve group and a second servo valve group.
[0065] The switching solenoid valve 5 is a two-position four-way solenoid valve having a first state and a second state. When the first servo valve group needs to work, the switching solenoid valve 5 is in the first state, the solenoid valve is actuated, the hydraulic isolation valve 11 of the first servo valve group is opened, and the hydraulic isolation valve 11 of the second servo valve group is closed;
[0066] The hydraulic oil source enters the manual isolation valve 10 of the first servo valve group through the main oil supply pipeline, which is used to control the flow of hydraulic oil into the channel of the first servo valve group;
[0067] The manual isolation valve 10 of the first servo valve group is connected to the filter 8 of the first servo valve group, and the hydraulic oil flows into the filter 8, and impurities in the hydraulic oil are removed by the filter 8;
[0068] The filter 8 of the first servo valve group is connected to the servo valve 4 of the first servo valve group. The hydraulic oil flows from the filter 8 into the servo valve 4. The servo valve 4 adjusts the flow and pressure of the hydraulic oil according to the electrical signal of the servo card.
[0069] The servo valve 4 of the first servo valve group is connected to the hydraulic isolation valve 11 of the first servo valve group. The hydraulic oil flows from the servo valve 4 into the hydraulic isolation valve 11. The hydraulic isolation valve 11 controls the flow of hydraulic oil to the oil motor.
[0070] The hydraulic isolation valve 11 of the first servo valve group is connected to the oil motor to drive the operation of the oil motor.
[0071] When the second servo valve group needs to work, the solenoid valve 5 is switched to the second state, the solenoid valve is actuated, the hydraulic isolation valve 11 of the second servo valve group is opened, and the hydraulic isolation valve 11 of the first servo valve group is closed;
[0072] The hydraulic oil source enters the manual isolation valve 10 of the second servo valve group through the main oil supply pipeline, which is used to control the flow of hydraulic oil into the channel of the second servo valve group;
[0073] The manual isolation valve 10 of the second servo valve group is connected to the filter 8 of the second servo valve group, and the hydraulic oil flows into the filter 8, and impurities in the hydraulic oil are removed by the filter 8;
[0074] The filter 8 of the second servo valve group is connected to the servo valve 4 of the second servo valve group. The hydraulic oil flows from the filter 8 into the servo valve 4. The servo valve 4 adjusts the flow and pressure of the hydraulic oil according to the electrical signal of the servo card.
[0075] The servo valve 4 of the second servo valve group is connected to the hydraulic isolation valve 11 of the second servo valve group. The hydraulic oil flows from the servo valve 4 into the hydraulic isolation valve 11. The hydraulic isolation valve 11 controls the flow of hydraulic oil to the oil motor.
[0076] The hydraulic isolation valve 11 of the second servo valve group is connected to the oil motor to drive the operation of the oil motor.
[0077] Thus far, the technical solutions of the present invention have been described in conjunction with the optional embodiments shown in the accompanying drawings. However, it is readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art may make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will fall within the scope of protection of the present invention.
Claims
1. A dual redundant servo valve oil motor for a steam turbine, characterized in that: The hydraulic motor includes a cylinder, two servo valve groups, a switching solenoid valve and a measuring component, wherein: The cylinder body of the oil cylinder has a rod cavity and a rodless cavity; The measuring component is used to detect the movement information of the piston rod of the oil cylinder; Each of the servo valve groups includes a servo valve and a hydraulic isolation valve; in each of the servo valve groups, the servo valve has a first oil port, a second oil port, a third oil port and a fourth oil port, and the hydraulic isolation valve has a fifth oil port, a sixth oil port, a seventh oil port, an eighth oil port and a ninth oil port for communicating with the hydraulic cavity of the hydraulic isolation valve, wherein the first oil port is connected to a high-pressure oil source, the second oil port is connected to an oil return line, the third oil port is connected to the fifth oil port, and the fourth oil port is connected to the sixth oil port; when the servo valve is in a first state, the first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; when the servo valve is in a first state, the first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; In the second state, the first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port; when the servo valve is in the third state, the first oil port, the second oil port, the third oil port and the fourth oil port are isolated from each other; the seventh oil port of the hydraulic isolation valve is connected to the rodless chamber of the cylinder, and the eighth oil port of the hydraulic isolation valve is connected to the rod chamber of the cylinder; when the hydraulic isolation valve is in the first state, the fifth oil port is connected to the eighth oil port, and the sixth oil port is connected to the seventh oil port; when the hydraulic isolation valve is in the second state, the fifth oil port, the sixth oil port, the seventh oil port and the eighth oil port are isolated from each other; A switching solenoid valve, the switching solenoid valve having a tenth oil port, an eleventh oil port, a twelfth oil port and a thirteenth oil port, wherein the tenth oil port is connected to the ninth oil port of the hydraulic isolation valve in one of the servo valve groups, and the eleventh oil port is connected to the ninth oil port of the hydraulic isolation valve in another of the servo valve groups; the twelfth oil port is connected to a high-pressure oil source, and the thirteenth oil port is connected to an oil return line; when the switching solenoid valve is in a first state, the tenth oil port is connected to the twelfth oil port, and the eleventh oil port is connected to the thirteenth oil port; when the switching solenoid valve is in a second state, the tenth oil port is connected to the thirteenth oil port, and the eleventh oil port is connected to the twelfth oil port.
2. The dual redundant servo valve oil motor for steam turbine according to claim 1, characterized in that: Each of the servo valve groups further includes a servo card, which is used to send a control signal to the servo valve.
3. The dual redundant servo valve oil motor for steam turbine according to claim 1, characterized in that: The servo valve group also includes a servo valve oil circuit block and a main oil circuit block. Oil circuits are formed inside the servo valve oil circuit block and the main oil circuit block. The oil circuit of the servo valve oil circuit block is used to install the oil circuit between the two servo valve groups and the switching solenoid valve, and the oil circuit of the main oil circuit block is used to install the oil circuit between the oil cylinder and the servo valve oil circuit block.
4. The dual-redundant servo valve oil motor for a steam turbine according to claim 3, characterized in that: The main oil circuit block is connected to an oil circuit pipe joint, and the oil cylinder is connected to a pressure measuring joint for respectively detecting the pressure of the rod cavity and the rodless cavity in the oil cylinder.
5. The dual-redundant servo valve oil motor for a steam turbine according to claim 3, characterized in that: The main oil circuit block is also provided with a pressure difference switch for controlling the servo valve.
6. The dual-redundant servo valve oil motor for a steam turbine according to claim 3, characterized in that: A manual isolation valve is provided between the first oil port of the servo valve and the high-pressure oil source.
7. The dual-redundant servo valve oil motor for a steam turbine according to claim 6, characterized in that: The manual isolation valve is provided with a filter, and the filter is fixed to the main oil circuit block through a mounting block.
8. The dual-redundant servo valve oil motor for a steam turbine according to claim 6, characterized in that: The servo valve oil circuit block, the manual isolation valve, the hydraulic isolation valve, the servo valve, and the switching solenoid valve are all fixed by hexagonal cylindrical head screws.
9. The dual-redundant servo valve oil motor for a steam turbine according to claim 1, characterized in that: The measuring assembly includes a displacement sensor, a mounting base, a stroke scale and a connecting assembly. The first end of the displacement sensor is fixed to one side of the cylinder through the mounting base, and the second end of the displacement sensor is fixedly connected to the oil port of the cylinder through the connecting assembly for testing the displacement information of the oil port of the cylinder; the first end of the stroke scale is also fixedly connected to the side of the connecting assembly away from the displacement sensor, and the second end of the stroke scale is fixedly connected to the cylinder for marking the stroke information of the oil port of the cylinder.
10. The dual-redundant servo valve oil motor for a steam turbine according to claim 9, characterized in that: Two displacement sensors are arranged in parallel.