A rotating diaphragm angle control system for a steam turbine and a control method thereof

Abstract

The application discloses a rotating partition corner control system of a steam turbine and a control method thereof. The position servo controller of the application accepts a position instruction signal of a control system and an actual position signal of a displacement sensor, and then carries out difference operation to be converted into a current signal for controlling the servo valve. Finally, the linear motion of the hydraulic piston rod of the rotating partition oil motor is converted into the corner motion of the rotating partition, so that the opening of the rotating partition is automatically controlled. When the electromagnetic valve and the servo valve on the rotating partition oil motor are faulty, the relevant cartridge stop valve, cartridge unloading valve and adjustable throttle hole can be manually closed to simultaneously achieve the purpose of isolating the electromagnetic valve, the servo valve and the rotating partition oil motor, and finally realize the online replacement of the electromagnetic valve and the servo valve under the condition that the corner position of the rotating partition is unchanged. Finally, the reliability of the rotating partition actuator and even the steam turbine is comprehensively improved.

Description

Technical Field

[0001] This invention belongs to the field of steam turbine technology, specifically relating to a steam turbine rotating diaphragm angle control system and its control method. Background Technology

[0002] The rotary diaphragm actuator of the extraction steam turbine can receive DEH commands to automatically adjust the rotation angle of the heating rotary diaphragm to control the opening degree to adapt to changes in external heating demand. The pressure sensor obtains the extraction steam pressure signal (electrical signal), which is calculated, verified and processed by DEH. The difference signal is then amplified and sent to the electro-hydraulic servo valve of the rotary diaphragm actuator. The electro-hydraulic servo valve controls the movement of the hydraulic piston, thereby controlling the opening degree of the rotary diaphragm.

[0003] The current turbine rotating diaphragm angle control system suffers from several drawbacks. High ambient temperatures at the equipment installation location can cause solenoid valves and servo valves on the rotating diaphragm hydraulic actuator to malfunction. When these valves fail, the turbine rotating diaphragm angle control system cannot function properly. Furthermore, it lacks the capability to replace solenoid valves and servo valves online while maintaining a constant rotating diaphragm angle.

[0004] Therefore, it is imperative to develop a turbine rotating diaphragm angle control system and its control method that is relatively simple in structure, safe and reliable in performance, and has the function of online replacement of solenoid valves and servo valves while keeping the rotating diaphragm angle unchanged. Summary of the Invention

[0005] The purpose of this invention is to provide a turbine rotating diaphragm angle control system and its control method that are relatively simple in structure, safe and reliable in performance, and have online servo valve replacement function. The system receives commands from the DEH and achieves continuous and accurate control of the rotating diaphragm's angle position through a dedicated position servo controller.

[0006] To achieve the above-mentioned objectives, the technical solution of the present invention is as follows: A turbine rotating diaphragm angle control system includes a hydraulic actuator, a rotating diaphragm, a position servo controller, and oil passages. The rotating diaphragm and the piston rod of the hydraulic actuator are hinged to form a rotating pair via a rotating joint mechanism. The oil passages include a pressure oil passage, a discharge oil passage, and a safety oil passage. The control system also includes three cartridge-type shut-off valves, a servo valve, two cartridge-type unloading valves, a solenoid valve, a pressure sequence valve, an adjustable throttle orifice, and two check valves. Each cartridge-type unloading valve includes one control port and two working ports. The pressure oil passage is divided into two paths. One path of the pressure oil passage is sequentially connected to the pressure ports of the cartridge-type shut-off valve and the servo valve. The two control ports of the servo valve are each connected to a cartridge-type shut-off valve. One cartridge-type shut-off valve is connected to the working port of the cartridge-type unloading valve and the rod chamber of the hydraulic actuator. The other cartridge-type shut-off valve is connected to the outlet port of the pressure sequence valve. The outlet port of the pressure sequence valve is connected to the other... One cartridge-type unloading valve's working port is connected to the rodless chamber of the hydraulic actuator. Another safety oil passage connects to the working port of the solenoid valve and another working port of the cartridge-type shut-off valve on the rod chamber side. The drain passage connects to the outlet port of a check valve. The inlet port of the check valve connects to the outlet port of the servo valve, the outlet port of the solenoid valve, the outlet port of the pressure sequence valve, and another working port of the cartridge-type unloading valve on the rodless chamber side. The safety oil passage connects to the outlet port of another check valve. The inlet port of the check valve in the safety oil passage connects to the control port of the solenoid valve, the control port of the pressure sequence valve, and the control ports of the two cartridge-type unloading valves. The two ends of the adjustable throttle orifice are connected to the pressure oil passage and the pressure port of the solenoid valve, respectively. A displacement sensor is installed on the piston rod of the hydraulic actuator. The displacement sensor, cartridge-type shut-off valve, servo valve, cartridge-type unloading valve, solenoid valve, and pressure sequence valve are electrically connected to the position servo controller.

[0007] The position servo controller receives the position command signal from the control system and the actual position signal from the displacement sensor, performs a difference calculation, and converts it into a current signal to control the operation of the servo valve. Finally, it controls the linear motion of the piston rod of the rotary diaphragm hydraulic motor through hydraulic pressure, which is then converted into the angular motion of the rotary diaphragm.

[0008] Furthermore, the rotary joint mechanism includes a rotating partition connecting rod and a horizontal connecting rod. One end of the rotating partition connecting rod is hinged to the rotating partition, and the other end is connected to one end of the horizontal connecting rod. The other end of the horizontal connecting rod is hinged to the piston rod of the hydraulic actuator. A rotating mechanism fixed to the outer cylinder of the turbine is provided in the middle of the horizontal connecting rod. The rotating partition connecting rod mechanism is connected to the piston rod of the rotating partition hydraulic actuator and the rotating partition through hinges to form a rotary joint. The hydraulic actuator is the driving member, and the rotating partition is the driven member, forming a rotary joint mechanism with one degree of freedom. The linear motion of the piston rod of the rotating partition hydraulic actuator is converted into the angular motion of the rotating partition by hydraulic pressure.

[0009] Furthermore, the cartridge-type gate valve includes a gate valve core, a locking nut, a gate valve sleeve, and a gate valve seat. The top of the gate valve sleeve has an external thread that mates with the locking nut. The gate valve sleeve has a cavity, through which the gate valve core passes and connects to the gate valve seat. The gate valve core is a stepped cylindrical structure that is thinner at the top and thicker at the bottom. Its upper end has an internal hexagonal structure, and its lower end has a conical head structure. The outer surface of the thinner end of the cylinder of the gate valve core has an external thread, and the stepped part of the gate valve core has a convex spherical surface. The upper part of the cavity of the gate valve sleeve has an internal thread that mates with the thread of the gate valve core. The stop valve sleeve cavity has a concave spherical surface that mates with the convex spherical surface of the stop valve core. The stop valve core and the stop valve seat are connected by threads. The stop valve seat is a hollow cylindrical structure. The upper part of the hollow stop valve seat is a cylindrical hole that fits with the coarse end of the stop valve core with a clearance, and the lower part is a conical hole that fits with the conical part of the stop valve core. The side wall of the stop valve seat has four evenly distributed radial holes. The cylindrical surface of the convex spherical surface of the stop valve core and the inner hole of the stop valve sleeve are sealed by a combination of a single-sided rectangular integral retaining ring and an O-ring. The lower outer cylindrical surface of the stop valve seat is provided with a combination of a double-sided rectangular integral retaining ring and an O-ring for sealing.

[0010] The lower end of the gate valve core has a conical head structure that achieves a hard seal with the inner wall of the gate valve seat. The coarse cylindrical end of the gate valve core achieves a shaft diameter fit with the inner hole of the gate valve seat for sealing. The locking nut on the cartridge-type gate valve is normally held tightly against the upper surface of the gate valve sleeve under a certain preload. When it is necessary to close or open the cartridge-type gate valve, first loosen the locking nut, and then use an Allen wrench to turn the gate valve core. When the gate valve core is tightened until the convex spherical surface at the transition between its fine and coarse cylindrical ends contacts the concave spherical surface on the gate valve sleeve, the cartridge-type gate valve is fully open. When the gate valve core is tightened until its lower conical head contacts the inner hole of the gate valve seat, the cartridge-type gate valve is fully closed. After the cartridge-type gate valve is in the open / closed position, the locking nut should be tightened promptly.

[0011] Furthermore, the cartridge-type unloading valve includes an adjusting screw, a locking nut, a sealing joint, an unloading valve cover plate, a spring, an unloading valve seat, and an unloading valve core. The unloading valve cover plate is a hollow cylindrical structure. The upper part of the hollow interior of the unloading valve cover plate is a cylindrical structure, and the bottom is a funnel structure. The center of the funnel is a mounting hole. The top of the hollow interior of the unloading valve cover plate is provided with an internal thread. The side wall of the unloading valve cover plate is provided with a control oil port communicating with the hollow interior of the unloading valve cover plate. The unloading valve seat is a hollow cylindrical structure. The bottom of the unloading valve cover plate is sealed to the top of the unloading valve seat. The unloading valve core is disposed inside the hollow interior of the unloading valve seat. The outer cylindrical surface of the unloading valve core and the inner cylindrical surface of the unloading valve seat are sealed through a shaft diameter fit. Multiple annular grooves are evenly distributed on the outer cylindrical surface of the unloading valve seat. A working oil port is provided at the bottom and side of the unloading valve seat. The top of the adjusting screw is a regular hexagonal structure with an external thread below it. The sealing joint and the locking nut are connected to the adjusting screw through the external thread of the adjusting screw. The upper part of the sealing joint is a hollow hexagonal structure, and the lower part is a hollow cylindrical structure. The cylindrical structure of the sealing joint is connected to the unloading valve cover plate by threads. The adjusting screw extends through the mounting hole into the unloading valve core. The spring is set inside the hollow part of the unloading valve seat. The lower end face of the spring contacts the bottom of the unloading valve core, and the upper end face contacts the top surface of the mounting hole of the unloading valve cover plate. It is circumferentially positioned by the inner wall of the unloading valve core.

[0012] The hydraulic action area at the bottom of the unloading valve core is smaller than that at the top. Assuming the liquid pressure at the upper and lower action areas of the unloading valve core is the same, due to the difference in the upper and lower action areas, the hydraulic pressure on the upper part of the unloading valve core is much greater than that on the lower part. This allows the cartridge unloading valve to achieve a seal through contact between the conical surface and the step of the unloading valve seat when closed. When the cartridge-type unloading valve is connected to the safety oil through the control port, the safety oil enters the unloading valve core through the safety oil passage in the unloading valve cover plate. Under the action of the safety oil pressure, the unloading valve core and the unloading valve seat are in close contact, so that the two working oil ports of the unloading valve are completely isolated. When the safety oil pressure above the unloading valve core is released through the control port, the unloading valve core will be quickly compressed by the spring under the action of the oil pressure at the bottom working oil port, so that the two working oil ports of the unloading valve are connected. The adjusting screw passes through the center of the spring and is inserted into the inner hole of the unloading valve core. When the cartridge unloading valve needs to participate in normal operation, the adjusting screw is turned out to the top dead center position. When the cartridge unloading valve needs to be manually closed, first loosen the lock nut, then screw in the adjusting screw so that the bottom end of the adjusting screw presses against the bottom surface of the unloading valve core, and then tighten the lock nut to complete the operation of manually closing the cartridge unloading valve.

[0013] A control method for a turbine rotating diaphragm angle control system includes, The following steps will allow you to open the rotating partition to a specific angle. 1) The cartridge stop valve is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve itself; 2) When the solenoid valve is de-energized, the pressure port and working port of the solenoid valve are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice and then enters the pressure port of the solenoid valve. Then, through the working port of the solenoid valve, it enters the control ports of the two cartridge unloading valves and the control port of the pressure sequence valve respectively. 3) When the adjusting screw of the cartridge unloading valve is turned out to the top dead center position, the control oil port of the cartridge unloading valve introduces safety oil into the upper cavity of the unloading valve core. Under the action of the safety oil pressure, the unloading valve core is in the closed state, so that the two working oil ports of the cartridge unloading valve are completely isolated. 4) The pressure sequence valve position quickly moves under the action of the safety oil pressure at the control port, overcoming the spring force, and connects its inlet and outlet ports; 5) The position servo controller receives position command signals from the control system and actual position signals from the displacement sensor; 6) The position servo controller performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal, which is sent to the servo valve coil to control the deflection of the servo valve position. This causes the pressure oil to pass through the cartridge shut-off valve installed on the pressure oil passage in front of the servo valve, and then enter the pressure oil port of the servo valve. It then flows out through the control oil port on the rodless side of the servo valve, and then passes through the cartridge shut-off valve and the pressure sequence valve on the rodless side in sequence, and finally enters the rodless chamber of the rotary diaphragm hydraulic motor. At the same time, the oil in the rod chamber of the rotary diaphragm hydraulic motor passes through the cartridge shut-off valve on the rod side, and then enters the control oil port on the rod side of the servo valve, and then flows out through the drain port of the servo valve. 8) Under the pressure of the rodless chamber of the rotating diaphragm hydraulic motor, the rotating pair mechanism overcomes the resistance of the rotating diaphragm, causing the rotating diaphragm to open wider; 9) The displacement sensor feeds back the position signal of the rotating diaphragm hydraulic motor to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the servo valve coil is zero, the servo valve is at the zero position, isolating the pressure oil passage, return oil passage and the passage between the rod chamber and rodless chamber of the rotating diaphragm hydraulic motor. At this time, the rotating diaphragm is opened to the specified rotation angle position. To reduce the size of the rotating partition to a specific angle, follow these steps: 1) The cartridge stop valve is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve itself; 2) When the solenoid valve is de-energized, the pressure port and working port of the solenoid valve are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice and then enters the pressure port of the solenoid valve. Then, through the working port of the solenoid valve, it enters the control ports of the two cartridge unloading valves and the control port of the pressure sequence valve respectively. 3) When the adjusting screw of the cartridge unloading valve is turned out to the top dead center position, the control oil port of the cartridge unloading valve introduces safety oil into the upper cavity of the unloading valve core. Under the action of the safety oil pressure, the unloading valve core is in the closed state, so that the two working oil ports of the cartridge unloading valve are completely isolated. 4) The pressure sequence valve position quickly moves under the action of the safety oil pressure at the control port, overcoming the spring force, and connects its inlet and outlet ports; 5) The position servo controller receives position command signals from the control system and actual position signals from the displacement sensor; 6) The position servo controller performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal, which is sent to the servo valve coil to control the deflection of the servo valve position. This causes the pressure oil to pass through the cartridge shut-off valve installed on the pressure oil passage in front of the servo valve, enter the pressure oil port of the servo valve, and then flow out through the control oil port on the rod side of the servo valve. After passing through the cartridge shut-off valve on the rod side, it finally enters the rod side of the rotary diaphragm hydraulic motor. At the same time, the oil in the rodless side of the rotary diaphragm hydraulic motor passes through the pressure sequence valve and the cartridge shut-off valve on the rodless side in sequence, and then enters the control oil port on the rodless side of the servo valve. Finally, it flows out through the drain port of the servo valve. 8) Under the pressure of the rod chamber of the rotary diaphragm hydraulic motor, the rotating pair mechanism overcomes the resistance of the rotary diaphragm and closes the rotary diaphragm. 9) The displacement sensor feeds back the position signal of the rotating diaphragm hydraulic motor to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the servo valve coil is zero, the servo valve is at the zero position, isolating the pressure oil passage, return oil passage and the passage between the rod chamber and rodless chamber of the rotating diaphragm hydraulic motor. At this time, the rotating diaphragm is closed to the specified rotation angle position.

[0014] Furthermore, the control method also includes, when the turbine trips under critical operating conditions, performing an emergency shutdown through the following steps; 1) Releasing the oil pressure in the downstream safety oil passage of the check valve will also release the oil pressure in the upstream safety oil passage of the check valve. 2) At this time, the safety oil pressure in the control chambers of the two cartridge unloading valves and the pressure sequence valve disappears. The cartridge unloading valve opens rapidly under the action of the oil pressure in the pressure oil passage and the oil pressure in the rodless chamber of the rotary diaphragm hydraulic motor, so that the pressure oil passage is connected to the rod chamber of the rotary diaphragm hydraulic motor and the return oil passage is connected to the rodless chamber of the rotary diaphragm hydraulic motor. 3) At the same time, under the action of its return spring, the pressure sequence valve isolates the passage between the rodless chamber of the rotating diaphragm hydraulic motor and the servo valve. The rotating diaphragm and other valves of the turbine close quickly, cutting off the new steam from entering the rotor to achieve the purpose of emergency shutdown.

[0015] Furthermore, the control method also includes that when the turbine regulating system is in a reset state and the solenoid valve is de-energized, the pressurized oil is converted into safety oil after passing through the adjustable throttle orifice and then acts on the control oil port of the cartridge unloading valve and the control chamber of the pressure sequence valve; under the action of the safety oil pressure, the cartridge unloading valve is in a closed state and the pressure sequence valve is in a conducting state, so as to keep the rotating diaphragm control system in working condition.

[0016] Furthermore, the control method also includes the following: when the turbine is operating normally for heating and the heat load is lost, and the turbine is in a reset state: simply energizing the solenoid valve can quickly release the oil pressure in the safety oil passage inside the check valve, while the oil pressure in the external safety oil passage remains unchanged. At this time, the safety oil pressure at the X port of the two cartridge unloading valves and the control chamber of the pressure sequence valve disappears. Under the action of the oil pressure in the pressure oil passage, the cartridge unloading valve opens rapidly under the action of the oil pressure in the rodless chamber of the rotary diaphragm hydraulic actuator, connecting the pressure oil passage with the rod chamber of the rotary diaphragm hydraulic actuator and the internal return oil passage with the rodless chamber of the rotary diaphragm hydraulic actuator, and quickly draining to the external return oil passage through the check valve; at the same time, under the action of its reset spring, the pressure sequence valve isolates the passage between the rodless chamber of the rotary diaphragm hydraulic actuator and the servo valve. Finally, with other valves of the turbine remaining normal, the rotary diaphragm hydraulic actuator quickly drives the rotary diaphragm to close rapidly to the minimum rotation angle position.

[0017] Furthermore, when the servo valve on the rotary diaphragm hydraulic motor malfunctions, the manually controlled cartridge shut-off valve is equipped with a manual switch to close it, thereby isolating the servo valve and the rotary diaphragm hydraulic motor. Ultimately, this allows for online replacement of the servo valve while maintaining the rotary diaphragm's rotational angle position.

[0018] Furthermore, when the solenoid valve on the rotary partition hydraulic actuator malfunctions, or when both the solenoid valve and the servo valve malfunction and need to be replaced while maintaining the rotary partition angle unchanged, the three cartridge-type shut-off valves, the adjustable throttle orifice, and the two cartridge-type unloading valves installed on the servo valve pressure oil passage and control oil passage are manually closed respectively; this simultaneously isolates the solenoid valve, the servo valve, and the rotary partition hydraulic actuator, ultimately enabling online replacement of the solenoid valve and the servo valve while maintaining the rotary partition angle position unchanged.

[0019] By adopting the above technical solution, the beneficial technical effects of the present invention are: 1. In this invention, the position servo controller receives the position command signal from the control system and the actual position signal from the displacement sensor, performs a difference calculation, and converts it into a current signal to control the operation of the servo valve. Finally, the linear motion of the piston rod of the rotary diaphragm hydraulic motor is controlled by hydraulic pressure to convert it into the angular motion of the rotary diaphragm, thereby realizing the automatic control of the opening degree of the rotary diaphragm.

[0020] 2. In this invention, an adjustable throttle orifice is configured between the pressure oil passage of the rotating diaphragm hydraulic actuator and the solenoid valve. When the turbine regulating system is in the reset state and the solenoid valve is de-energized, the pressure oil is converted into safety oil after passing through the adjustable throttle orifice and then acts on the X port of the cartridge unloading valve and the control chamber of the pressure sequence valve. Under the action of the safety oil pressure, the cartridge unloading valve is in the closed state and the pressure sequence valve is in the open state, maintaining the operating conditions of the rotating diaphragm control system.

[0021] 3. In this invention, the lower end of the cartridge-type gate valve core has a conical head structure that achieves a hard seal with the inner wall of the gate valve seat. The coarse cylindrical end of the gate valve core achieves a shaft diameter fit with the inner hole of the gate valve seat to achieve a seal. The locking nut on the cartridge-type gate valve is normally tightly pressed against the upper surface of the gate valve sleeve under a certain preload. When it is necessary to close or open the cartridge-type gate valve, first loosen the locking nut, and then use an Allen wrench to rotate the gate valve core. When the gate valve core is tightened until the transition between its fine and coarse cylindrical ends is designed with a convex spherical surface that contacts the concave spherical surface of the gate valve sleeve, the cartridge-type gate valve is fully opened. When the gate valve core is tightened until its lower conical head contacts the inner hole of the gate valve seat, the cartridge-type gate valve is fully closed. After the cartridge-type gate valve is in the open / closed position, the locking nut should be tightened promptly.

[0022] 4. In this invention, the hydraulic action area at the bottom of the unloading valve core is smaller than that at the top. Assuming the liquid pressure at the upper and lower action areas of the unloading valve core is the same, due to the difference in the upper and lower action areas of the unloading valve core, the hydraulic pressure on the upper part of the unloading valve core is much greater than that on the lower part. This allows the cartridge unloading valve to achieve a contact seal through the cone surface and the step of the unloading valve seat when closed. When the cartridge unloading valve is connected to the safety oil through the control port, the safety oil enters the upper part of the unloading valve core through the safety oil passage in the unloading valve cover plate. Under the action of the safety oil pressure, the unloading valve core and the unloading valve seat are in close contact, ensuring that the two working oils of the unloading valve... The ports are completely isolated. When the safety oil pressure above the unloading valve core is released through the control port, the unloading valve core will quickly compress the spring under the action of the oil pressure at the bottom working port, opening the two working ports of the unloading valve. The adjusting screw passes through the center of the spring and is inserted into the inner hole of the unloading valve core. When the cartridge unloading valve needs to participate in normal operation, the adjusting screw is turned out to the top dead center position. When the cartridge unloading valve needs to be manually closed, first loosen the lock nut, then screw in the adjusting screw so that the bottom end of the adjusting screw presses against the bottom surface of the unloading valve core, and then tighten the lock nut to complete the operation of manually closing the cartridge unloading valve. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the turbine rotating diaphragm angle control system of the present invention.

[0024] Figure 2 This is a schematic diagram of the cartridge-type shut-off valve of the present invention.

[0025] Figure 3 This is a schematic diagram of the cartridge-type unloading valve of the present invention.

[0026] The components include: 1. Hydraulic actuator; 2. Rotating partition; 3. Position servo controller; 5. Rotary joint mechanism; 6. Safety oil passage; 7. Pressure oil passage; 8. Discharge oil passage; 9. Displacement sensor; 10. Cartridge-type stop valve; 11. Servo valve; 12. Cartridge-type unloading valve; 13. Solenoid valve; 14. Pressure sequence valve; 15. Check valve; 16. Adjustable throttle orifice; 10-1. Stop valve core; 10-2. Locking nut; 10-3. Stop valve sleeve; 10-4. Stop valve seat; 12-1. Adjusting screw; 12-2. Locking nut; 12-3. Sealing joint; 12-4. Unloading valve cover plate; 12-5. Spring; 12-6. Unloading valve seat; 12-7. Unloading valve core. Detailed Implementation

[0027] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0028] It should be noted that the structures, proportions, sizes, etc. shown in this specification are only used to complement the content disclosed in the specification for those skilled in the art to understand and read, and are not intended to limit the conditions under which the present invention can be implemented. Any modifications to the structure, changes in the proportions, or adjustments to the size, without affecting the effects and objectives that the present invention can produce, should fall within the scope of the technical content disclosed in the present invention.

[0029] Furthermore, the terms such as "upper," "lower," "left," "right," "middle," and "one" used in this specification are merely for clarity of description and are not intended to limit the scope of the invention. Any changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of the invention.

[0030] Example 1 like Figure 1As shown, this embodiment provides a turbine rotating diaphragm 2 angle control system, including a hydraulic actuator 1, a rotating diaphragm 2, a position servo controller 3, and oil passages. The rotating diaphragm 2 and the piston rod of the hydraulic actuator 1 are hinged to form a rotating pair via a rotating pair mechanism 5. The oil passages include a pressure oil passage 7, a drain oil passage 8, and a safety oil passage 6. The control system also includes three cartridge-type shut-off valves 10, a servo valve 11, two cartridge-type unloading valves 12, a solenoid valve 13, a pressure sequence valve 14, an adjustable throttle orifice 16, and two check valves 15. 12 includes one control port and two working ports. The pressure oil passage 7 is divided into two paths. One path of the pressure oil passage 7 is sequentially connected to the pressure ports of a cartridge-type shut-off valve 10 and a servo valve 11. The two control ports of the servo valve 11 are respectively connected to a cartridge-type shut-off valve 10. One cartridge-type shut-off valve 10 is connected to the working port of a cartridge-type unloading valve 12 and the rod chamber of the hydraulic actuator 1. The other cartridge-type shut-off valve 10 is connected to the outlet port of a pressure sequence valve 14. The outlet port of the pressure sequence valve 14 is connected to another cartridge-type unloading valve. The working port of valve 12 is connected to the rodless chamber of the hydraulic actuator 1. Another safety oil passage 6 is connected to the working port of solenoid valve 13 and another working port of the cartridge-type shut-off valve 10 on the rod chamber side. The drain passage 8 is connected to the outlet of a check valve 15. The inlet of the check valve 15 is connected to the outlet of servo valve 11, the outlet of solenoid valve 13, the outlet of pressure sequence valve 14, and another working port of the cartridge-type unloading valve 12 on the rodless chamber side. The safety oil passage 6 is connected to the outlet of another check valve 15. The one-way... The oil inlet of valve 15 is connected to the control oil port of solenoid valve 13, the control oil port of pressure sequence valve 14, and the control oil ports of two cartridge unloading valves 12. A displacement sensor 9 is installed on the piston rod of the hydraulic actuator 1. The displacement sensor 9, cartridge shut-off valve 10, servo valve 11, cartridge unloading valve 12, solenoid valve 13, and pressure sequence valve 14 are electrically connected to the position servo controller 3. The control system is also provided with an adjustable throttle orifice 16. The two ends of the adjustable throttle orifice 16 are connected to the pressure oil passage 7 and the pressure oil port of solenoid valve 13, respectively. The position servo controller 3 receives the position command signal from the control system and the actual position signal from the displacement sensor, performs a difference calculation, and converts it into a current signal to control the operation of the servo valve 11. Finally, it controls the linear motion of the piston rod of the hydraulic motor 1 of the rotating baffle 2 through hydraulic pressure, which is then converted into the angular motion of the rotating baffle 2. The rotating pair mechanism 5 includes a rotating partition 2 connecting rod and a horizontal connecting rod. One end of the rotating partition 2 connecting rod is hinged to the rotating partition 2, and the other end is connected to one end of the horizontal connecting rod. The other end of the horizontal connecting rod is hinged to the piston rod of the hydraulic actuator 1. A rotating mechanism fixed to the outer cylinder of the turbine is provided in the middle of the horizontal connecting rod. The rotating partition 2 connecting rod mechanism is connected to the piston rod of the hydraulic actuator 1 and the rotating partition 2 respectively through hinges to form a rotating pair. The hydraulic actuator 1 is the driving member, and the rotating partition 2 is the driven member, forming a rotating pair mechanism 5 with one degree of freedom. The linear motion of the piston rod of the hydraulic actuator 1 is converted into the angular motion of the rotating partition 2 by hydraulic pressure control.

[0031] In this embodiment, when it is necessary to increase the steam extraction rate and open the rotating baffle 2 to a certain angle value, the following steps are taken to open the rotating baffle 2 to a certain angle value. 1) The cartridge stop valve 10 is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve 10 itself; 2) When the solenoid valve 13 is de-energized, the pressure oil port and the working oil port of the solenoid valve 13 are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice 16 and then enters the pressure oil port of the solenoid valve 13. Then, through the working oil port of the solenoid valve 13, it enters the control oil ports of the two cartridge unloading valves 12 and the control oil port of the pressure sequence valve 14 respectively. 3) When the adjusting screw of the cartridge unloading valve 12 is turned out to the top dead center position, the control oil port of the cartridge unloading valve 12 introduces safety oil into the upper cavity of the unloading valve core. Under the action of the safety oil pressure, the unloading valve core is in the closed state, so that the two working oil ports of the cartridge unloading valve 12 are completely isolated. 4) Pressure sequence valve 14 moves rapidly under the action of safe oil pressure at the control port, overcoming the spring force, and connects its inlet and outlet ports. 5) The position servo controller 3 receives the position command signal from the control system and the actual position signal from the displacement sensor; 6) The position servo controller 3 performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal, which is sent to the coil of servo valve 11 to control the deflection of servo valve 11. This causes the pressure oil to enter the pressure port of servo valve 11 after passing through the cartridge shut-off valve 10 installed on the pressure oil passage 7 in front of servo valve 11. Then, it flows out through the control port on the rodless side of servo valve 11, and then passes through the cartridge shut-off valve 10 and the pressure sequence valve 14 on the rodless side in sequence, finally entering the rodless chamber of rotary baffle 2 hydraulic motor 1. At the same time, the oil in the rod chamber of rotary baffle 2 hydraulic motor 1 passes through the cartridge shut-off valve 10 on the rod side, and then enters the control port on the rod side of servo valve 11, and then flows out through the drain port of servo valve 11. 8) Under the pressure of the rodless chamber of the hydraulic motor 1, the rotating pair mechanism 5 overcomes the resistance of the rotating partition 2 and opens the rotating partition 2. 9) The displacement sensor 9 feeds back the position signal of the rotating baffle 2 hydraulic motor 1 to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the coil of the servo valve 11 is zero, the servo valve 11 is in the zero position, and the passage between the pressure oil passage 7, the return oil passage and the rod chamber and rodless chamber of the rotating baffle 2 hydraulic motor 1 are isolated. At this time, the rotating baffle 2 is opened to the specified rotation angle position.

[0032] In this embodiment, when it is necessary to reduce the steam extraction rate and close the rotating baffle 2 to a certain angle value, the following steps are taken to close the rotating baffle 2 to a certain angle value. 1) The cartridge stop valve 10 is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve 10 itself; 2) When the solenoid valve 13 is de-energized, the pressure oil port and the working oil port of the solenoid valve 13 are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice 16 and then enters the pressure oil port of the solenoid valve 13. Then, through the working oil port of the solenoid valve 13, it enters the control oil ports of the two cartridge unloading valves 12 and the control oil port of the pressure sequence valve 14 respectively. 3) When the adjusting screw of the cartridge unloading valve 12 is turned out to the top dead center position, the control oil port of the cartridge unloading valve 12 introduces safety oil into the upper cavity of the unloading valve core. Under the action of the safety oil pressure, the unloading valve core is in the closed state, so that the two working oil ports of the cartridge unloading valve 12 are completely isolated. 4) Pressure sequence valve 14 moves rapidly under the action of safe oil pressure at the control port, overcoming the spring force, and connects its inlet and outlet ports. 5) The position servo controller 3 receives the position command signal from the control system and the actual position signal from the displacement sensor; 6) The position servo controller 3 performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal, which is sent to the coil of servo valve 11 to control the deflection of servo valve 11. This causes the pressure oil to pass through the cartridge shut-off valve 10 installed on the pressure oil passage 7 in front of servo valve 11, and then enter the pressure oil port of servo valve 11. It then flows out through the control oil port on the rod side of servo valve 11, and then through the cartridge shut-off valve 10 on the rod side, and finally enters the rod side of the rotary baffle 2 hydraulic motor 1. At the same time, the oil in the rodless side of the rotary baffle 2 hydraulic motor 1 passes through the pressure sequence valve 14 and the cartridge shut-off valve 10 on the rodless side in sequence, and then enters the control oil port on the rodless side of servo valve 11, and then flows out through the drain port of servo valve 11. 8) Under the pressure of the rod chamber of the hydraulic motor 1 on the rotating partition 2, the rotating pair mechanism 5 overcomes the resistance of the rotating partition 2 and closes the rotating partition 2. 9) The displacement sensor 9 feeds back the position signal of the rotating baffle 2 hydraulic motor 1 to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the coil of the servo valve 11 is zero, the servo valve 11 is in the zero position, and the passage between the pressure oil passage 7, the return oil passage and the rod chamber and rodless chamber of the rotating baffle 2 hydraulic motor 1 are isolated. At this time, the rotating baffle 2 is closed to the specified rotation angle position.

[0033] In this embodiment, when the steam turbine is operating normally for heating and the heat load is lost, and the steam turbine is in the reset state: simply energizing the solenoid valve 13 can quickly release the oil pressure in the safety oil passage 6 inside the one-way valve 15, while the oil pressure in the external safety oil passage 6 remains unchanged. At this time, the safety oil pressure at the X port of the two cartridge unloading valves 12 and the control chamber of the pressure sequence valve 14 disappears. Under the action of the oil pressure in the pressure oil passage 7, the oil pressure in the rodless chamber of the rotary baffle 2 hydraulic actuator 1 of the cartridge unloading valve 12 is reduced. Under the action of force, it opens rapidly, connecting the pressure oil passage 7 with the rod chamber of the rotating baffle 2 hydraulic actuator 1, and the internal return oil passage with the rodless chamber of the rotating baffle 2 hydraulic actuator 1, and is quickly discharged to the external return oil passage through the one-way valve 15; at the same time, the pressure sequence valve 14, under the action of its return spring, isolates the passage between the rodless chamber of the rotating baffle 2 hydraulic actuator 1 and the servo valve 11. Finally, with other valves of the steam turbine in normal condition, the rotating baffle 2 hydraulic actuator 1 quickly drives the rotating baffle 2 to close rapidly to the minimum rotation angle position.

[0034] In this embodiment, when the turbine regulating system is in the reset state and the solenoid valve 13 is de-energized: the pressure oil is converted into safety oil after passing through the adjustable throttle orifice 16 and then acts on the control oil port of the cartridge unloading valve 12 and the control chamber of the pressure sequence valve 14; under the action of the safety oil pressure, the cartridge unloading valve 12 is in the closed state and the pressure sequence valve 14 is in the open state, keeping the rotating partition 2 control system in working condition.

[0035] In this embodiment, when the steam turbine trips under critical operating conditions, such as high speed, low lubricating oil pressure, low control oil pressure, large differential expansion, or large shaft vibration, causing the steam turbine to trip and shut down, the following steps are taken for emergency shutdown: 1) When the oil pressure in the downstream safety oil passage 6 of the check valve 15 is released, the oil pressure in the upstream safety oil passage 6 of the check valve 15 will also be released. 2) At this time, the safety oil pressure in the control chambers of the two cartridge unloading valves 12 and the pressure sequence valve 14 disappears. The cartridge unloading valve 12 opens rapidly under the action of the oil pressure in the pressure oil passage 7 and the oil pressure in the rodless chamber of the rotating baffle 2 hydraulic motor 1, so that the pressure oil passage 7 is connected to the rod chamber of the rotating baffle 2 hydraulic motor 1, and the return oil passage is connected to the rodless chamber of the rotating baffle 2 hydraulic motor 1. 3) At the same time, under the action of its return spring, the pressure sequence valve 14 isolates the passage between the rodless chamber of the rotating baffle 2 hydraulic motor 1 and the servo valve 11. The rotating baffle 2 and other valves of the turbine close quickly, cutting off the new steam from entering the rotor to achieve the purpose of emergency shutdown.

[0036] Example 2 The difference between this embodiment and Embodiment 1 is that, in this embodiment, as... Figure 2 As shown, the cartridge-type gate valve 10 includes a gate valve core 10-1, a locking nut 10-2, a gate valve sleeve 10-3, and a gate valve seat 10-4. The top of the gate valve sleeve 10-3 is provided with an external thread that mates with the locking nut 10-2. The gate valve sleeve 10-3 has a cavity inside, through which the gate valve core 10-1 passes and connects to the gate valve seat 10-4. The gate valve core 10-1 has a stepped cylindrical structure that is thinner at the top and thicker at the bottom. Its upper end is provided with an internal hexagonal structure, and its lower end is a conical head structure. The outer surface of the thinner end of the cylinder of the gate valve core 10-1 is provided with an external thread, and the stepped part of the gate valve core 10-1 is provided with a convex spherical surface. The upper part of the cavity of the gate valve sleeve 10-3 is provided with an internal thread that mates with the thread of the gate valve core 10-1. The cavity of the shut-off valve sleeve 10-3 is provided with a concave spherical surface that mates with the convex spherical surface of the shut-off valve core 10-1. The shut-off valve core 10-1 and the shut-off valve seat 10-4 are connected by threads. The shut-off valve seat 10-4 is a hollow cylindrical structure. The upper part of the hollow part of the shut-off valve seat 10-4 is a cylindrical hole that mates with the coarse end of the shut-off valve core 10-1 with clearance, and the lower part is a conical hole that mates with the cone of the shut-off valve core 10-1. The side wall of the shut-off valve seat 10-4 is provided with four evenly distributed radial holes. The cylindrical surface of the convex spherical surface of the shut-off valve core 10-1 and the inner hole of the shut-off valve sleeve 10-3 are sealed by a combination of a single-sided rectangular integral retaining ring and an O-ring. The lower outer cylindrical surface of the shut-off valve seat 10-4 is provided with a combination of a double-sided rectangular integral retaining ring and an O-ring for sealing. like Figure 3As shown, the cartridge-type unloading valve 12 includes an adjusting screw 12-1, a locking nut 12-2, a sealing joint 12-3, an unloading valve cover plate 12-4, a spring 12-5, an unloading valve seat 12-6, and an unloading valve core 12-7. The unloading valve cover plate 12-4 has a hollow cylindrical structure. The upper part of the hollow interior of the unloading valve cover plate 12-4 is a cylindrical structure, and the bottom is a funnel structure. The center of the funnel is a mounting hole. The top of the hollow interior of the unloading valve cover plate 12-4 is provided with an inner... The unloading valve cover plate 12-4 has a control oil port on its side wall, which connects to the hollow interior of the unloading valve cover plate 12-4. The unloading valve seat 12-6 is a hollow cylindrical structure. The bottom of the unloading valve cover plate 12-4 is sealed to the top of the unloading valve seat 12-6. The unloading valve core 12-7 is disposed inside the hollow interior of the unloading valve seat 12-6. The outer cylindrical surface of the unloading valve core 12-7 and the inner cylindrical surface of the unloading valve seat 12-6 are sealed by a shaft diameter fit. Multiple annular grooves are evenly distributed on the cylindrical surface. The unloading valve seat 12-6 has a working oil port on its bottom and side. The top of the adjusting screw 12-1 is a regular hexagonal structure, with an external thread below it. The sealing joint 12-3 and the locking nut 12-2 are connected to the adjusting screw 12-1 via the external thread. The upper part of the sealing joint 12-3 is a hollow hexagonal structure, and the lower part is a hollow cylindrical structure. The cylindrical structure of the head 12-3 is connected to the unloading valve cover plate 12-4 by threads. The adjusting screw 12-1 extends through the mounting hole into the unloading valve core 12-7. The spring 12-5 is set in the hollow interior of the unloading valve seat 12-6. The lower end face of the spring 12-5 contacts the bottom of the unloading valve core 12-7, and the upper end face contacts the top surface of the mounting hole of the unloading valve cover plate 12-4. It is circumferentially positioned by the inner wall of the unloading valve core 12-7. The rest of the structure is the same as in Embodiment 1.

[0037] In this embodiment, the lower end of the stop valve core 10-1 is a conical head structure that achieves a hard seal with the inner wall of the stop valve seat 10-4. The thick end of the stop valve core 10-1 is cylindrical and achieves a shaft diameter fit with the inner hole of the stop valve seat 10-4 to achieve a seal. The locking nut on the cartridge stop valve 10 is normally tightly attached to the locking nut of the stop valve sleeve 10-2 under a certain preload. When it is necessary to close or open the cartridge stop valve 10, the locking nut is first loosened, and then the stop valve core 10-1 is rotated with an Allen wrench. When the valve core 10-1 is screwed until the convex spherical surface at the transition between its thin and thick cylindrical ends contacts the locking nut 10-2 at the valve sleeve 10-3, the cartridge valve 10 is fully opened. When the valve core 10-1 is screwed until the conical head at its lower end contacts the inner hole of the valve seat 10-4, the cartridge valve 10 is fully closed. After the cartridge valve 10 is in the open / closed position, the locking nut should be tightened promptly. The hydraulic action area at the bottom of the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7 is smaller than that at the top. Assuming the liquid pressure at the upper and lower action areas of the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7 is the same, due to the difference in the upper and lower action areas of the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7, the hydraulic pressure above the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7 is much greater. The hydraulic pressure below causes the cartridge unloading valve 12 to close, achieving a seal through the conical surface and the step of the unloading valve seat. When the cartridge unloading valve 12 is connected to safety oil via the control port, the safety oil enters the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7 above the safety oil passage 6 in the unloading valve cover plate 12-4. Under the pressure of the safety oil, the unloading valve core 12-5 (spring), 12-6 (unloading valve seat), and 12-7 come into close contact with the unloading valve seat. This completely isolates the two working ports of the unloading valve. When the safety oil pressure above the unloading valve core 12-5 spring, 12-6 unloading valve seat, and 12-7 is released through the control port, the unloading valve core 12-5 spring, 12-6 unloading valve seat, and 12-7 will rapidly compress the spring under the action of the oil pressure at the bottom working port, opening the valve and connecting the two working ports. The adjusting screw 12-1 passes through the center of the spring and inserts into the unloading valve core 12-5 spring and 12-6 unloading valve. In the inner hole of valve seat 12-7, when the cartridge unloading valve 12 needs to participate in normal operation, the adjusting screw 12-1 is turned out to the upper stop position. When it is necessary to manually close the cartridge unloading valve 12, first loosen the lock nut, and then screw in the adjusting screw 12-1 to press the bottom end of the adjusting screw 12-1 against the unloading valve core 12-5 spring; 12-6 unloading valve seat; 12-7 upper bottom surface, and then tighten the lock nut to complete the operation of manually closing the cartridge unloading valve 12.

[0038] In this embodiment, when the servo valve 11 fails due to poor hydraulic oil cleanliness causing the valve core to jam and malfunction, or when the servo valve 11 seal is damaged and leaks oil, the manual control cartridge shut-off valve 10 is equipped with a manual switch to close it. This achieves the purpose of isolating the servo valve 11 and the rotary baffle 2 hydraulic motor 1, ultimately enabling online replacement of the servo valve 11 while maintaining the rotation angle position of the rotary baffle 2 unchanged.

[0039] In this embodiment, when the solenoid valve 13 on the rotating baffle 2 hydraulic motor 1 fails, or when both the solenoid valve 13 and the servo valve 11 fail and need to be replaced while keeping the rotation angle of the rotating baffle 2 unchanged, the three cartridge-type shut-off valves 10, the adjustable throttle orifice 16, and the two cartridge-type unloading valves 12 installed on the pressure oil passage 7 and the control oil passage of the servo valve 11 are manually closed respectively; at the same time, the solenoid valve 13, the servo valve 11, and the rotating baffle 2 hydraulic motor 1 are isolated, and finally the solenoid valve 13 and the servo valve 11 are replaced online while keeping the rotation angle position of the rotating baffle 2 unchanged.

[0040] It is understood that the present invention has been described through some embodiments, and those skilled in the art will recognize that various changes or equivalent substitutions can be made to these features and embodiments without departing from the spirit and scope of the invention. Furthermore, under the teachings of the present invention, these features and embodiments can be modified to adapt to specific situations and materials without departing from the spirit and scope of the invention. Therefore, the present invention is not limited to the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the protection scope of the present invention.

Claims

1. A turbine rotating diaphragm angle control system, comprising a hydraulic actuator (1), a rotating diaphragm (2), a position servo controller (3), and an oil passage, characterized in that: The rotating partition (2) and the piston rod of the hydraulic actuator (1) are hinged to form a rotating pair through a rotating pair mechanism (5). The oil passage includes a pressure oil passage (7), an oil discharge passage (8), and a safety oil passage (6). The control system also includes three cartridge-type shut-off valves (10), a servo valve (11), two cartridge-type unloading valves (12), a solenoid valve (13), a pressure sequence valve (14), an adjustable throttle orifice (16), and two check valves (15). The cartridge-type unloading valve (12) includes a control port. The pressure oil passage (7) is divided into two paths, with two working ports. One path of the pressure oil passage (7) is connected in sequence to the pressure ports of a cartridge shut-off valve (10) and a servo valve (11). The two control ports of the servo valve (11) are respectively connected to a cartridge shut-off valve (10). One of the cartridge shut-off valves (10) is connected to the working port of the cartridge unloading valve (12) and the rod chamber of the hydraulic actuator (1). The other cartridge shut-off valve (10) is connected to the outlet of the pressure sequence valve (14). The oil outlet of the pressure sequence valve (14) is connected to the working port of another cartridge unloading valve (12) and the rodless chamber of the hydraulic actuator (1). Another safety oil passage (6) is connected to the working port of the solenoid valve (13) and the other working port of the rod-side cartridge shut-off valve (10). The oil drain passage (8) is connected to the oil outlet of a check valve (15). The oil inlet of the check valve (15) is connected to the oil outlet of the servo valve (11), the oil outlet of the solenoid valve (13), and the pressure sequence valve (14). 14) The drain port and the other working port of the cartridge unloading valve (12) on the rodless chamber side are connected. The safety oil passage (6) is connected to the outlet of another check valve (15). The inlet of the check valve (15) of the safety oil passage (6) is connected to the control port of the solenoid valve (13), the control port of the pressure sequence valve (14) and the control ports of the two cartridge unloading valves (12). The two ends of the adjustable throttle orifice (16) are connected to the pressure oil passage (7) and the pressure port of the solenoid valve (13) respectively. The piston rod of the hydraulic actuator (1) is equipped with a displacement sensor (9), and the displacement sensor (9), cartridge shut-off valve (10), servo valve (11), cartridge unloading valve (12), solenoid valve (13) and pressure sequence valve (14) are electrically connected to the position servo controller (3).

2. The control system according to claim 1, characterized in that: The rotating pair mechanism (5) includes a rotating partition (2) connecting rod and a horizontal connecting rod. One end of the rotating partition (2) connecting rod is hinged to the rotating partition (2), and the other end is connected to one end of the horizontal connecting rod. The other end of the horizontal connecting rod is hinged to the piston rod of the oil motor (1). A rotating mechanism fixed to the outer cylinder of the turbine is provided in the middle of the horizontal connecting rod. The rotating partition (2) connecting rod mechanism is connected to the piston rod of the oil motor (1) and the rotating partition (2) respectively by hinges to form a rotating pair. The oil motor (1) is the driving member, and the rotating partition (2) is the driven member, forming a rotating pair mechanism (5) with one degree of freedom. The linear motion of the piston rod of the oil motor (1) of the rotating partition (2) is converted into the angular motion of the rotating partition (2) by hydraulic pressure control.

3. The control system according to claim 1, characterized in that: The cartridge-type shut-off valve (10) includes a shut-off valve core (10-1), a locking nut (10-2), a shut-off valve sleeve (10-3), and a shut-off valve seat (10-4). The top of the shut-off valve sleeve (10-3) is provided with an external thread that mates with the locking nut (10-2). The shut-off valve sleeve (10-3) has a cavity inside. The shut-off valve core (10-1) passes through the cavity and connects to the shut-off valve seat (10-4). The shut-off valve core (10-1) is a stepped cylindrical structure that is thinner at the top and thicker at the bottom. Its upper end is provided with an internal hexagonal structure, and its lower end is a conical head structure. The outer surface of the thin end of the cylinder of the shut-off valve core (10-1) is provided with an external thread, and the stepped part of the shut-off valve core (10-1) is provided with a convex spherical surface. The upper part of the cavity of the shut-off valve sleeve (10-3) is provided with an internal thread that mates with the thread of the shut-off valve core (10-1). The valve sleeve (10-3) has a concave spherical surface inside its cavity that mates with the convex spherical surface of the valve core (10-1). The valve core (10-1) and the valve seat (10-4) are connected by threads. The valve seat (10-4) is a hollow cylindrical structure. The upper part of the hollow valve seat (10-4) is a cylindrical hole that mates with the coarse end of the valve core (10-1) with clearance, and the lower part is a conical hole that mates with the cone of the valve core (10-1). The side wall of the valve seat (10-4) has four evenly distributed radial holes. The cylindrical surface of the convex spherical surface of the valve core (10-1) and the inner hole of the valve sleeve (10-3) are sealed by a combination of a single-sided rectangular integral retaining ring and an O-ring. The lower outer cylindrical surface of the valve seat (10-4) is sealed by a combination of a double-sided rectangular integral retaining ring and an O-ring.

4. The control system according to claim 1, characterized in that: The cartridge-type unloading valve (12) includes an adjusting screw (12-1), a locking nut (12-2), a sealing joint (12-3), an unloading valve cover plate (12-4), a spring (12-5), an unloading valve seat (12-6), and an unloading valve core (12-7). The unloading valve cover plate (12-4) has a hollow cylindrical structure. The upper part of the hollow interior of the unloading valve cover plate (12-4) is a cylindrical structure, and the bottom is a funnel structure. The center of the funnel is the mounting hole. The top of the hollow interior of the unloading valve cover plate (12-4) is... The unloading valve cover plate (12-4) has an internal thread. Its side wall has a control oil port communicating with the hollow interior of the unloading valve cover plate (12-4). The unloading valve seat (12-6) is a hollow cylindrical structure. The bottom of the unloading valve cover plate (12-4) is sealed to the top of the unloading valve seat (12-6). The unloading valve core (12-7) is located inside the hollow interior of the unloading valve seat (12-6). The outer cylindrical surface of the unloading valve core (12-7) and the inner cylindrical surface of the unloading valve seat (12-6) are sealed through a shaft diameter fit. Furthermore, the unloading valve core (12-7)... Multiple annular grooves are evenly distributed on the outer cylindrical surface of the valve seat (12-7). The unloading valve seat (12-6) has a working oil port on its bottom and side. The top of the adjusting screw (12-1) is a regular hexagonal structure, with an external thread below the hexagonal structure. The sealing joint (12-3) and the locking nut (12-2) are connected to the adjusting screw (12-1) via the external thread of the adjusting screw (12-1). The upper part of the sealing joint (12-3) is a hollow hexagonal structure, and the lower part of the sealing joint (12-3) is a hollow cylinder. The structure of the sealing joint (12-3) is a cylindrical structure connected to the unloading valve cover plate (12-4) by threads. The adjusting screw (12-1) extends through the mounting hole into the unloading valve core (12-7). The spring (12-5) is set in the hollow interior of the unloading valve seat (12-6). The lower end face of the spring (12-5) contacts the bottom of the unloading valve core (12-7), and the upper end face contacts the top surface of the mounting hole of the unloading valve cover plate (12-4). It is circumferentially positioned by the inner wall of the unloading valve core (12-7).

5. A control method for a turbine rotating diaphragm angle control system as described in any one of claims 1-4, characterized in that: The following steps are used to open the rotating partition (2) to a certain angle value. 1) The cartridge stop valve (10) is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve (10) itself; 2) When the solenoid valve (13) is de-energized, the pressure port and working port of the solenoid valve (13) are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice (16) and then enters the pressure port of the solenoid valve (13) and then enters the control ports of the two cartridge unloading valves (12) and the control port of the pressure sequence valve (14) through the working port of the solenoid valve (13); 3) The adjusting screw (12-1) of the cartridge unloading valve (12) is turned out to the upper dead point position. The control oil port of the cartridge unloading valve (12) introduces safety oil into the upper cavity of the unloading valve core. The unloading valve core is closed under the action of safety oil pressure, so that the two working oil ports of the cartridge unloading valve (12) are completely isolated. 4) The pressure sequence valve (14) moves quickly under the action of the safe oil pressure at the control oil port to overcome the spring force and connect its oil inlet and outlet. 5) The position servo controller (3) receives the position command signal from the control system and the actual position signal from the displacement sensor; 6) The position servo controller (3) performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal and sent to the coil of the servo valve (11) to control the deflection of the servo valve (11). The pressure oil then enters the pressure port of the servo valve (11) through the cartridge shut-off valve (10) installed on the pressure oil passage (7) in front of the servo valve (11), and then flows out through the control port on the rodless side of the servo valve (11). It then passes through the cartridge shut-off valve (10) and the pressure sequence valve (14) on the rodless side in sequence, and finally enters the rodless chamber of the rotary baffle (2) hydraulic motor (1). At the same time, the oil in the rod chamber of the rotary baffle (2) hydraulic motor (1) passes through the cartridge shut-off valve (10) on the rod side, and then enters the control port on the rod side of the servo valve (11), and then flows out through the drain port of the servo valve (11). 8) Under the pressure of the rodless chamber of the rotating partition (2) and the hydraulic motor (1), the rotating pair mechanism (5) overcomes the resistance of the rotating partition (2) and makes the rotating partition (2) open wider; 9) The displacement sensor (9) feeds back the position signal of the rotating baffle (2) hydraulic motor (1) to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the coil of the servo valve (11) is zero, the servo valve (11) is at zero position, isolating the pressure oil passage (7), the return oil passage and the passage between the rod chamber of the rotating baffle (2) hydraulic motor (1) and the rodless chamber of the rotating baffle (2) hydraulic motor (1). At this time, the rotating baffle (2) is opened to the specified rotation angle position. The following steps are used to reduce the size of the rotating partition (2) to a certain angle value. 1) The cartridge stop valve (10) is in the fully open state, connecting the upstream and downstream oil passages of the cartridge stop valve (10) itself; 2) When the solenoid valve (13) is de-energized, the pressure port and working port of the solenoid valve (13) are connected. At this time, the pressure oil is converted into safety oil through the adjustable throttle orifice (16) and then enters the pressure port of the solenoid valve (13) and then enters the control ports of the two cartridge unloading valves (12) and the control port of the pressure sequence valve (14) through the working port of the solenoid valve (13); 3) The adjusting screw (12-1) of the cartridge unloading valve (12) is turned out to the upper dead point position. The control oil port of the cartridge unloading valve (12) introduces safety oil into the upper cavity of the unloading valve core. The unloading valve core is closed under the action of safety oil pressure, so that the two working oil ports of the cartridge unloading valve (12) are completely isolated. 4) The pressure sequence valve (14) moves quickly under the action of the safe oil pressure at the control oil port to overcome the spring force and connect its oil inlet and outlet. 5) The position servo controller (3) receives the position command signal from the control system and the actual position signal from the displacement sensor; 6) The position servo controller (3) performs a difference calculation based on the position deviation between the position command signal and the actual position signal; 7) After calculation, the signal is amplified and converted into a current signal and sent to the coil of the servo valve (11) to control the deflection of the servo valve (11). The pressure oil then enters the pressure port of the servo valve (11) through the cartridge shut-off valve (10) installed on the pressure oil passage (7) in front of the servo valve (11), and then flows out through the control port on the rod side of the servo valve (11). It then passes through the cartridge shut-off valve (10) on the rod side and finally enters the rod side of the rotating baffle (2) hydraulic motor (1). At the same time, the oil in the rodless side of the rotating baffle (2) hydraulic motor (1) passes through the pressure sequence valve (14) and the cartridge shut-off valve (10) on the rodless side in sequence, and then enters the control port on the rodless side of the servo valve (11). Finally, it flows out through the drain port of the servo valve (11). 8) Under the pressure of the rod chamber of the rotating partition (2) and the hydraulic motor (1), the rotating pair mechanism (5) overcomes the resistance of the rotating partition (2) and closes the rotating partition (2); 9) The displacement sensor (9) feeds back the position signal of the rotating partition (2) hydraulic motor (1) to the servo controller in real time and compares it with the position command signal until the deviation is zero. When the current signal received by the coil of the servo valve (11) is zero, the servo valve (11) is at zero position, isolating the pressure oil passage (7), the return oil passage and the passage between the rod chamber of the rotating partition (2) hydraulic motor (1) and the rodless chamber of the rotating partition (2) hydraulic motor (1). At this time, the rotating partition (2) is closed to the specified rotation angle position.

6. The control method according to claim 5, characterized in that: The control method also includes, when the turbine trips under critical operating conditions, performing an emergency shutdown through the following steps; 1) If the oil pressure in the downstream safety oil passage (6) of the check valve (15) is released, the oil pressure in the upstream safety oil passage (6) of the check valve (15) will also be released. 2) At this time, the safety oil pressure in the control chambers of the two cartridge unloading valves (12) and the pressure sequence valve (14) disappears. The cartridge unloading valve (12) opens rapidly under the action of the oil pressure in the pressure oil passage (7) and the oil pressure in the rodless chamber of the rotating baffle (2) oil motor (1), so that the pressure oil passage (7) is connected to the rod chamber of the rotating baffle (2) oil motor (1), and the return oil passage is connected to the rodless chamber of the rotating baffle (2) oil motor (1). 3) At the same time, the pressure sequence valve (14) isolates the passage between the rotating baffle (2), the rodless chamber of the oil motor (1), and the servo valve (11) under the action of its return spring. The rotating baffle (2) and other valves of the turbine are quickly closed, cutting off the new steam from entering the rotor to achieve the purpose of emergency shutdown.

7. The control method according to claim 5, characterized in that: The control method further includes that when the turbine regulating system is in the reset state and the solenoid valve (13) is de-energized, the pressure oil is converted into safety oil after passing through the adjustable throttle orifice (16) and then acts on the control oil port of the cartridge unloading valve (12) and the control chamber of the pressure sequence valve (14); under the action of the safety oil pressure, the cartridge unloading valve (12) is in the closed state and the pressure sequence valve (14) is in the open state, so that the rotating partition (2) control system has working conditions.

8. The control method according to claim 5, characterized in that: The control method further includes the following: when the turbine is operating normally for heating and the heat load is lost, and the turbine is in the reset state: simply energizing the solenoid valve (13) can quickly release the oil pressure in the safety oil passage (6) inside the check valve (15), while the oil pressure in the external safety oil passage (6) remains unchanged. At this time, the safety oil pressure in the X port of the two cartridge unloading valves (12) and the control chamber of the pressure sequence valve (14) disappears. Under the action of the oil pressure in the pressure oil passage (7) of the cartridge unloading valve (12), the oil pressure in the rodless chamber of the rotary baffle (2) hydraulic actuator (1) of the cartridge unloading valve (12) is released. Under the action of force, it opens quickly, so that the pressure oil passage (7) is connected to the rod chamber of the rotating diaphragm (2) oil motor (1), and the internal return oil passage is connected to the rodless chamber of the rotating diaphragm (2) oil motor (1), and is quickly discharged to the external return oil passage through the one-way valve (15); at the same time, the pressure sequence valve (14) isolates the passage between the rodless chamber of the rotating diaphragm (2) oil motor (1) and the servo valve (11) under the action of its return spring. Finally, under the normal state of other valves of the steam turbine, the rotating diaphragm (2) is quickly closed to the minimum rotation angle position by the rapid action of the rotating diaphragm (2) oil motor (1).

9. The control method according to claim 5, characterized in that: The control method also includes that when the servo valve (11) on the rotating partition (2) hydraulic motor (1) malfunctions, the manual control cartridge shut-off valve (10) is equipped with a manual switch to close it, thereby isolating the servo valve (11) and the rotating partition (2) hydraulic motor (1), and finally achieving the online replacement of the servo valve (11) while keeping the rotation angle position of the rotating partition (2) unchanged.

10. The control method according to claim 5, characterized in that: The control method further includes, when the solenoid valve (13) on the rotating partition (2) hydraulic motor (1) fails, or when both the solenoid valve (13) and the servo valve (11) fail and need to be replaced while keeping the rotation angle of the rotating partition (2) unchanged, the three cartridge-type shut-off valves (10), the adjustable throttle orifice (16), and the two cartridge-type unloading valves (12) installed on the pressure oil passage (7) and control oil passage of the servo valve (11) are manually closed respectively; at the same time, the purpose of isolating the solenoid valve (13), the servo valve (11), and the rotating partition (2) hydraulic motor (1) is achieved, and finally the solenoid valve (13) and the servo valve (11) are replaced online while keeping the rotation angle position of the rotating partition (2) unchanged.

Images