Difunctional heavy hammer closing device

Abstract

The utility model relates to the technical field of water-turbine generator sets, in particular to a double-function heavy hammer closing device which comprises a speed regulator main distributing valve, a regulation and control unit, a heavy hammer, a guide vane servomotor and an overspeed protection device. The speed regulator main distributing valve is connected with the regulation and control unit; the regulation and control unit is respectively connected with the heavy hammer, the guide vane servomotor and the overspeed protection device; and the heavy hammer is matched with the guide vane servomotor. According to the dual-function heavy hammer closing device, the regulation and control unit is matched with the heavy hammer, the guide vane servomotor and the overspeed protection device, so that accident closing of the tubular hydroelectric generating set can be realized no matter whether the oil pressure of a system is normal or not or whether oil pressure exists or not, and the dual-function heavy hammer closing device is safe and reliable. The double-function heavy hammer closing device is simple in structure, easy to install and adjust, convenient to reduce installation space, capable of simplifying pipelines and capable of reducing cost.

Description

Technical Field

[0001] This utility model relates to the field of hydro-generator technology, and in particular to a dual-function counterweight shut-off device. Background Technology

[0002] Currently, there are two common types of overspeed protection devices for axial-flow turbine generator sets: The first type is an emergency pressure regulating valve. When the system oil pressure exceeds the minimum operating oil pressure, the emergency pressure regulating valve activates, allowing hydraulic oil to enter the guide vane servo and close it within a specified time. If the system oil pressure drops, the emergency pressure regulating valve cannot activate, and the guide vane servo cannot close. The second type is a counterweight closing device. Regardless of whether the system oil pressure is normal, abnormal, or underpressure, the counterweight closing device activates, opening the guide vane servo's switching chamber to the atmosphere. The guide vane servo closes under the weight of the counterweight. After prolonged operation, corrosion and large gaps may occur between moving parts, increasing the turbine's closing torque. In this case, the weight of the counterweight may not be sufficient to close the guide vane servo within the specified time, and in severe cases, the weight of the counterweight may prevent the guide vane servo from activating at all.

[0003] In existing technologies, some power plants are equipped with both emergency pressure regulating valves and counterweight shut-off devices. However, this increases installation space, makes pipeline configuration more complex, and significantly increases costs. Furthermore, the hydraulic control system and monitoring control process and logic are complex, making it inconvenient for later inspection and maintenance. Utility Model Content

[0004] Based on the above-mentioned technical problems, this utility model provides a dual-function counterweight closing device.

[0005] The technical solution of this utility model to solve the above-mentioned technical problems is as follows:

[0006] A dual-function counterweight shut-off device includes: a governor main pressure valve, a control unit, a counterweight, a guide vane relay, and an overspeed protection device.

[0007] The main pressure distribution valve of the speed controller is connected to the control unit; the control unit is connected to the counterweight, the guide vane relay and the overspeed protection device respectively; the counterweight cooperates with the guide vane relay.

[0008] Furthermore, the control unit includes: a first check valve, a second check valve, a counterweight closing main valve, a third check valve, an action signal contact, and a counterweight closing solenoid valve;

[0009] The C port of the first check valve is connected to the pressure oil, and the T3 port of the first check valve is connected to the return oil tank; the B1 port of the second check valve is connected to the pressure oil, and the B2 port of the second check valve is connected to the B chamber of the main valve for closing the counterweight.

[0010] The Z1 port of the main valve closed by the counterweight is connected to the pressure oil; the Z2 port of the main valve closed by the counterweight is connected to the closed chamber of the main pressure regulating valve of the speed governor; the Z3 port of the main valve closed by the counterweight is connected to the open chamber of the main pressure regulating valve of the speed governor; the Z4 port of the main valve closed by the counterweight is connected to the return oil tank; the Z5 port of the main valve closed by the counterweight is connected to the closed chamber of the guide vane servo; and the Z6 port of the main valve closed by the counterweight is connected to the open chamber of the guide vane servo.

[0011] The B3 port of the third check valve is connected to the Z6 port of the main valve closed by the counterweight, and the B4 port of the third check valve is connected to the B chamber of the main valve closed by the counterweight.

[0012] The P1 port of the counterweight closing solenoid valve is connected to the A port of the overspeed protection device or directly to the pressure oil; the A1 port of the counterweight closing solenoid valve is connected to the A2 chamber of the counterweight closing main valve; the T1 port of the counterweight closing solenoid valve is connected to the return oil tank; the action signal contact is connected to the A2 chamber of the counterweight closing main valve.

[0013] The first check valve is a swing check valve, and the second check valve is a hydraulically controlled check valve.

[0014] Furthermore, the first check valve, the second check valve, and the third check valve are any one of pipe check valves, flange check valves, and plate check valves.

[0015] Furthermore, the solenoid valve for closing the counterweight is any one of a solenoid directional valve, a solenoid ball valve, a proportional valve, a proportional servo valve, and a servo valve.

[0016] Furthermore: when the solenoid valve for closing the counterweight is a solenoid directional valve, it is specifically a two-position solenoid directional valve.

[0017] The dual-function counterweight closing device provided by this utility model has at least the following beneficial effects or advantages:

[0018] This utility model provides a dual-function counterweight shut-off device, in which the main pressure distribution valve of the speed governor is connected to the control unit; the control unit is connected to the counterweight, the guide vane servo, and the overspeed protection device respectively; the counterweight and the guide vane servo cooperate. This dual-function counterweight shut-off device, with the control unit cooperating with the counterweight, guide vane servo, and overspeed protection device, can achieve emergency shut-off of the axial-flow turbine generator unit regardless of whether the system oil pressure is normal or not, or whether there is oil pressure at all, ensuring safety and reliability. Furthermore, this dual-function counterweight shut-off device has a simple structure, is easy to install and adjust, and facilitates reducing installation space, simplifying piping, and lowering costs. Attached Figure Description

[0019] Figure 1 A schematic diagram of the dual-function counterweight closing device provided in an embodiment of this utility model.

[0020] The attached diagram lists the components represented by each number as follows:

[0021] 1-First check valve, 2-Second check valve, 3-Flat hammer shut-off main valve, 4-Third check valve, 5-Action signal contact, 6-Flat hammer shut-off solenoid valve, 7-Overspeed protection device, 8-Flat hammer, 9-Guide vane relay. Detailed Implementation

[0022] This invention addresses the technical deficiencies of the emergency pressure regulating valve and counterweight shut-off device commonly used in axial-flow turbine generator sets, and provides a dual-function counterweight shut-off device.

[0023] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of the present utility model.

[0024] In the description of this utility model, it should be noted that the terms and nouns in the various embodiments, such as "upper", "lower", "front", "back", "left", and "right", which indicate the location, are only used to simplify the description of the positional relationship based on the accompanying drawings. They do not mean that the components and devices referred to must be operated in accordance with the specific location and limited operation and method or structure in the specification. Such directional terms do not constitute a limitation on this utility model.

[0025] This utility model discloses a dual-function counterweight closing device, such as... Figure 1 As shown, it includes: a governor main pressure distribution valve, a control unit, a counterweight 8, a guide vane servo connector 9, and an overspeed protection device 7. The governor main pressure distribution valve is connected to the control unit; the control unit is connected to the counterweight 8, the guide vane servo connector 9, and the overspeed protection device 7 respectively. The overspeed protection device 7 can be a purely mechanical overspeed protection device; the counterweight 8 works in conjunction with the guide vane servo connector 9.

[0026] Specifically: such as Figure 1 As shown, the control unit includes: a first check valve 1, a second check valve 2, a counterweight closing main valve 3, a third check valve 4, an action signal contact 5, and a counterweight closing solenoid valve 6. The C port of the first check valve 1 is connected to the pressure oil, and the T3 port of the first check valve 1 is connected to the return oil tank; the B1 port of the second check valve 2 is connected to the pressure oil, and the B2 port of the second check valve 2 is connected to the B chamber of the counterweight closing main valve 3.

[0027] The Z1 port of the main valve 3 with its counterweight closed is connected to the pressure oil; the Z2 port of the main valve 3 with its counterweight closed is connected to the closed chamber of the governor's main pressure regulating valve; the Z3 port of the main valve 3 with its counterweight closed is connected to the open chamber of the governor's main pressure regulating valve; the Z4 port of the main valve 3 with its counterweight closed is connected to the return oil tank; the Z5 port of the main valve 3 with its counterweight closed is connected to the closed chamber of the guide vane servo connector 9; and the Z6 port of the main valve 3 with its counterweight closed is connected to the open chamber of the guide vane servo connector 9. The B3 port of the third check valve 4 is connected to the Z6 port of the main valve 3 with its counterweight closed; and the B4 port of the third check valve 4 is connected to the B chamber of the main valve 3 with its counterweight closed.

[0028] The P1 port of the counterweight closing solenoid valve 6 is connected to the A port of the overspeed protection device 7 or directly to the pressure oil. The A1 port of the counterweight closing solenoid valve 6 is connected to the A2 chamber of the counterweight closing main valve 3. The T1 port of the counterweight closing solenoid valve 6 is connected to the return oil tank. The action signal contact 5 is connected to the A2 chamber of the counterweight closing main valve 3.

[0029] In this system, the first check valve 1 is a swing check valve, and the second check valve 2 is a hydraulically controlled check valve. The first check valve 1, the second check valve 2, and the third check valve 4 can be any one of a pipe-type check valve, a flange-type check valve, or a plate-type check valve. The counterweight-closing solenoid valve 6 can be any one of a solenoid directional valve, a solenoid ball valve, a proportional valve, a proportional servo valve, or a servo valve. When the counterweight-closing solenoid valve 6 is a solenoid directional valve, it is specifically a two-position solenoid directional valve.

[0030] like Figure 1 As shown, the working process of the dual-function counterweight closing device disclosed in this embodiment of the present invention is as follows:

[0031] Under normal conditions, pressurized oil passes through ports P and A of the speed protection device 7 to ports P1 and A1 of the counterweight closing solenoid valve 6, and then connects to chamber A2 of the counterweight closing main valve 3. Pressurized oil also passes through ports B1 and B2 of the hydraulic check valve to chamber B of the counterweight closing main valve 3. Since the pressure of the pressurized oil entering chambers A2 and B of the counterweight closing main valve 3 is the same, and the area of ​​chamber A2 is larger than that of chamber B, the thrust of the pressurized oil acting on chamber A2 is greater than the thrust acting on chamber B. Therefore, the counterweight closing main valve 3... Figure 1 The workstation shown is the right workstation.

[0032] When the system does not lose pressure (oil pressure does not disappear) and an emergency shutdown is required: the counterweight closing solenoid valve 6 receives the microcomputer emergency shutdown signal and activates. The hydraulic oil in the A2 chamber of the counterweight closing main valve 3 flows to the return oil tank through the A1 and T1 ports of the counterweight closing solenoid valve 6. The thrust in the A2 chamber of the counterweight closing main valve 3 disappears. Under the thrust of the pressure oil in its B chamber, the counterweight closing main valve 3 moves to the left working position. At this time, the Z1 and Z5 ports and the Z6 and Z4 ports of the counterweight closing main valve 3 are connected. The pressure oil flows to the closed chamber of the guide vane servo 9 through the Z1 and Z5 ports of the counterweight closing main valve 3. The open chamber hydraulic oil of the guide vane servo 9 flows to the return oil tank through the Z6 and Z4 ports of the counterweight closing main valve 3, thus realizing a pressurized emergency shutdown.

[0033] When the system is not depressurized (oil pressure is not lost) and the counterweight closing solenoid valve 6 does not operate due to a fault, and the turbine generator speed reaches the set value: the pure mechanical overspeed protection device 7 operates, the hydraulic oil in the A2 chamber of the counterweight closing main valve 3 flows through the A1 and P1 ports of the counterweight closing solenoid valve 6 to the A and T ports of the pure mechanical overspeed protection device 7 and then to the return oil tank. The thrust of the A2 chamber of the counterweight closing main valve 3 disappears, and the counterweight closing main valve 3 moves to the left working position under the thrust of the pressure oil in its B chamber. At this time, the Z1 port and Z5 port of the counterweight closing main valve 3 are connected, and the Z6 port and Z4 port are connected. The pressure oil flows through the Z1 and Z5 ports of the counterweight closing main valve 3 to the closed chamber of the guide vane servo 9. The open chamber hydraulic oil of the guide vane servo 9 flows through the Z6 and Z4 ports of the counterweight closing main valve 3 to the return oil tank, realizing pressurized overspeed shutdown.

[0034] When the system loses pressure due to a burst pipe or other malfunction: At this time, the system has no oil pressure supply to the governor's main pressure distribution valve to control the guide vane servo 9, and there is no oil pressure to control the main valve 3 to close. The hydraulic oil in chamber A2 of the main valve 3 closes either flows through ports A1 and T1 of the solenoid valve 6 to the return oil tank, or through ports A1 and P1 of the solenoid valve 6 to ports A and T of the pure mechanical overspeed protection device 7 before returning to the return oil tank, or through ports A1 and P1 of the solenoid valve 6 to ports A and P of the pure mechanical overspeed protection device 7 before being released to the atmosphere. The thrust in chamber A2 of the main valve 3 closes disappears. At this time, the closed chamber of the guide vane servo 9 generates negative pressure under the gravity of the hammer 8, and the open chamber generates back pressure under the gravity of the hammer 8, i.e., oil is released at port Z6 of the main valve 3 closes. The pressurized oil flows through port Z6 of the main valve 3 (with the counterweight shutting valve) to ports B3 and B4 of the check valve, and then to chamber B of the main valve 3. Under the thrust of the pressurized oil in chamber B, the main valve 3 moves to the left working position. At this time, ports Z1 and Z5, and ports Z6 and Z4 of the main valve 3 are connected. Because the closed chamber of the guide vane servo actuator 9 is under negative pressure, the closed chamber of the guide vane servo actuator 9 draws in atmospheric air or hydraulic oil from the return tank via ports C and T3 of the swing check valve. The open chamber hydraulic oil of the guide vane servo actuator 9 flows through ports Z6 and Z4 of the main valve 3 to the return tank, achieving pressure loss shutdown. The action signal contact 5 has a signal output function.

[0035] The dual-function counterweight closing device provided in this embodiment of the utility model has at least the following beneficial effects or advantages:

[0036] The dual-function counterweight shut-off device provided in this embodiment connects the main pressure distribution valve of the speed governor to the control unit. The control unit is connected to the counterweight, the guide vane servo, and the overspeed protection device. The counterweight and the guide vane servo cooperate. This dual-function counterweight shut-off device, with the control unit cooperating with the counterweight, guide vane servo, and overspeed protection device, can achieve emergency shut-off of the axial-flow turbine generator unit regardless of whether the system oil pressure is normal or not, or whether there is oil pressure at all, ensuring safety and reliability. Furthermore, this dual-function counterweight shut-off device has a simple structure, is easy to install and adjust, and facilitates reducing installation space, simplifying piping, and lowering costs.

[0037] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to fixed connections or detachable connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model in light of the specific circumstances.

[0038] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A dual function dead latch closure device characterized by: The utility model relates to a governor main pressure distributing valve, a regulation and control unit, a heavy hammer, a guide vane booster and an overspeed protection device. The governor main pressure distributing valve is connected with the regulation and control unit; the regulation and control unit is connected with the heavy hammer, the guide vane booster and the overspeed protection device respectively; the heavy hammer cooperates with the guide vane booster. The regulation and control unit comprises a first check valve, a second check valve, a heavy hammer closing main valve, a third check valve, an action signal contact and a heavy hammer closing electromagnetic valve.

2. The dual function dead latch closure of claim 1 wherein: The C port of the first check valve is connected with pressure oil, and the T3 port of the first check valve is connected with an oil return tank; the B1 port of the second check valve is connected with pressure oil, and the B2 port of the second check valve is connected with the B cavity of the heavy hammer closing main valve. The Z1 port of the heavy hammer closing main valve is connected with pressure oil, the Z2 port of the heavy hammer closing main valve is connected with the closing cavity of the governor main pressure distributing valve, the Z3 port of the heavy hammer closing main valve is connected with the opening cavity of the governor main pressure distributing valve, the Z4 port of the heavy hammer closing main valve is connected with an oil return tank, the Z5 port of the heavy hammer closing main valve is connected with the closing cavity of the guide vane booster, and the Z6 port of the heavy hammer closing main valve is connected with the opening cavity of the guide vane booster. The B3 port of the third check valve is connected with the Z6 port of the heavy hammer closing main valve, and the B4 port of the third check valve is connected with the B cavity of the heavy hammer closing main valve. The P1 port of the heavy hammer closing electromagnetic valve is connected with the A port of the overspeed protection device or directly connected with pressure oil, the A1 port of the heavy hammer closing electromagnetic valve is connected with the A2 cavity of the heavy hammer closing main valve, and the T1 port of the heavy hammer closing electromagnetic valve is connected with an oil return tank; the action signal contact is connected with the A2 cavity of the heavy hammer closing main valve. The first check valve is a swing check valve, and the second check valve is a hydraulic check valve. The first check valve, the second check valve and the third check valve are any one of a pipe check valve, a flange check valve and a plate check valve.

3. The dual function dead latch closure of claim 2 wherein: The heavy hammer closing electromagnetic valve is any one of an electromagnetic directional control valve, an electromagnetic ball valve, a proportional valve, a proportional servo valve and a servo valve.

4. The dual function dead latch closure of claim 2 wherein: When the heavy hammer closing electromagnetic valve is an electromagnetic directional control valve, the electromagnetic directional control valve is specifically a two-position electromagnetic directional control valve.

5. The dual function dead latch closure of claim 4 wherein: ​

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