JP7053418B2 - Combined intermediate valve gear and turbine power generation equipment - Google Patents

Description

Embodiments of the present invention relate to a combined intermediate valve device and a turbine power generation facility.

In a nuclear power plant, the steam after working in a high pressure turbine is dehumidified by a moisture separator and then introduced into a low pressure turbine via a cross-around pipe. The cross-around pipe is provided with an intermediate steam stop valve and an intercept valve, respectively, in order to prevent overspeed of the turbine due to steam inflow to the low pressure turbine during a turbine trip or load cutoff of the low pressure turbine. The intermediate steam stop valve and intercept valve are incorporated in series along the flow direction of steam flowing through the cross-around pipe and are configured as a combined intermediate valve device.

The combined intermediate valve device 100 according to the related technique will be described with reference to FIGS. 6 and 7. FIG. 6 is a schematic configuration diagram of a combined intermediate valve device according to a related technique, and FIG. 7 is a plan view of FIG. 6 as viewed from the PP direction. As shown in FIG. 6, the combined intermediate valve device 100 integrates a butterfly type intermediate steam stop valve 12a and a butterfly type intercept valve 12b in a tubular valve casing 11 having flanges at both ends. It is said that the configuration is as follows. Both ends of the valve casing 11 in the axial direction are connected via a flange between a cross-around pipe (not shown) and a low-pressure turbine inlet pipe.

As shown in FIGS. 6 and 7, the intermediate steam stop valve 12a is a valve body of the combined intermediate valve device 100, and its central position is attached to the valve rod 13a. The valve rod 13a is a rotation axis of the intermediate steam stop valve 12a, and is rotatably supported by the bearing portion 11a of the valve casing 11 in an arrangement orthogonal to the steam flow direction. One end of the valve rod 13a is connected to an intermediate steam stop valve drive device 20a, which will be described later.

The intermediate steam stop valve drive device 20a is a drive device for the hydraulic intermediate steam stop valve 12a, and is fixed to the outside of the valve casing 11 via a connector 18a. A drive rod 21a that can be displaced in the vertical direction protrudes from the center position on one end side of the intermediate steam stop valve drive device 20a, and a valve rod 13a is connected to the tip of the drive rod 21a via a link type drive lever 14a. There is. When hydraulic oil is supplied from the hydraulic pressure supply device (not shown) to the hydraulic cylinder 22a of the intermediate steam stop valve drive device 20a, the hydraulic pressure from the hydraulic oil acts on the drive rod 21a and the drive rod inside the hydraulic cylinder 22a. The drive rod 21a is pushed upward against the restoring force from the spring connected to the 21a. As a result, the drive rod 21a is displaced upward, and the displacement amount changes according to the amount of hydraulic oil supplied to the hydraulic cylinder 22a. The drive lever 14a converts the vertical motion of the drive rod 21a into a rotary motion and transmits the drive force to the valve rod 13a. As a result, the intermediate steam stop valve 12a attached to the valve rod 13a opens and closes and rotates together with the valve rod 13a. More specifically, when a predetermined amount of hydraulic oil is supplied to the hydraulic cylinder 22a of the intermediate steam stop valve drive device 20a, the intermediate steam stop valve 12a is fully opened and the hydraulic oil is completely discharged from the hydraulic cylinder 22a. If (the hydraulic oil in the hydraulic cylinder 22a is empty), the intermediate steam stop valve 12a is fully closed.

On the other hand, the intercept valve 12b is combined with the intermediate steam stop valve 12a to form the valve body of the intermediate valve device 100, and the center position thereof is attached to the valve rod 13b. The valve rod 13b is a rotation shaft of the intercept valve 12b, and is rotatably supported by a bearing portion 11b on the downstream side in the steam flow direction with respect to the intermediate steam stop valve 12a. Other configurations are the same as those of the intermediate steam stop valve 12a. That is, the intercept valve driving device 20b is fixed to the outside of the valve casing 11 via the connector 18b. The valve rod 13b is connected to the drive rod 21b of the intercept valve drive device 20b via the drive lever 14b.

In the event of a turbine trip, load shedding, etc., the intermediate steam stop valve drive device 20a and intercept valve drive device 20b are urgently activated to discharge hydraulic oil from the inside of the hydraulic cylinders that compose them, and the intermediate steam stop valve 12a and intercept are used. The valve 12b is closed suddenly.

Japanese Unexamined Patent Application Publication No. 2003-293705.

The intermediate steam stop valve 12a and the intercept valve 12b are required to be able to continue the operating state for a predetermined time even when a turbine trip, load cutoff, or the like occurs. When a turbine trip or load shedding occurs, the intermediate steam stop valve 12a and the intercept valve 12b are suddenly closed. To meet this requirement, the valve body is suddenly closed and then the valve body is suddenly opened again. It is necessary to confirm whether the opening can be controlled. However, in order to open the valve body, hydraulic oil that only resists the restoring force from the springs connected to the drive rods 21a and 21b inside the hydraulic cylinders of the intermediate steam stop valve drive device 20a and the intercept valve drive device 20b, respectively. Need to be resupplied. Therefore, it may take a longer time than when the valve body is suddenly closed in order to open the valve body and confirm whether the valve opening degree can be controlled by the above method.

Further, in a general nuclear power generation facility, a plurality of intermediate steam stop valves 12a and intercept valves 12b are provided, respectively, and the intermediate steam stop valve drive device 20a and the intercept valve drive device 20b corresponding to each of these valves are one. It is connected to a hydraulic supply device (not shown). Therefore, when a plurality of valve bodies are suddenly opened at the same time, the total flow rate of the hydraulic oil to be supplied to these drive devices may temporarily exceed the total flow rate of the hydraulic oil that can be supplied from the hydraulic pressure supply device. .. This can cause a sharp drop in pressure in the hydraulic system of all steam valves installed in nuclear power plants, which can lead to uncontrollable steam valves.

Therefore, an object to be solved by the present invention is to provide a combined intermediate valve device and a turbine power generation facility capable of performing sudden closing and subsequent rapid opening of a valve body only by discharging hydraulic oil.

In order to solve the above problems, according to the combined intermediate valve device of the embodiment, the valve rod to which the valve body is attached is driven to rotate by adjusting the amount of hydraulic oil in the hydraulic cylinder, and this valve is driven from the steam flow path. It is a combination intermediate valve device that controls the amount of steam that passes through the body and is supplied to the steam turbine. The hydraulic cylinder is provided, and the amount of hydraulic oil supplied to the hydraulic cylinder is adjusted via the valve rod. The first and second drive devices that transmit the driving force to the valve body are provided between the first drive device and the valve rod, and between the second drive device and the valve rod. The steam is provided with a clutch mechanism for connecting the valve rod and any one of the first and second drive devices, and a control device for outputting a control command for adjusting the connection by the clutch mechanism. During normal operation of the turbine, the valve rod is connected to the first drive device via the clutch mechanism, and the opening of the valve body is adjusted by the amount of hydraulic oil in the hydraulic cylinder of the first drive device. When the valve body is suddenly closed during abnormal operation of the steam turbine, the supply of the hydraulic oil to the hydraulic cylinder of the first drive device is cut off, and the hydraulic cylinder of the first drive device is used. When the hydraulic oil is discharged and the valve body is suddenly opened after the sudden closing, the clutch mechanism causes the first drive device and the valve rod to be connected based on a control command from the control device. The second drive device and the valve rod are connected to each other, and the supply of the hydraulic oil to the hydraulic cylinder of the second drive device is cut off, so that a predetermined amount of the hydraulic oil is filled. The hydraulic oil is discharged from the hydraulic cylinder of the second drive device.

According to the embodiment of the present invention, the valve body can be suddenly closed and then suddenly opened only by discharging the hydraulic oil.

It is a schematic diagram of the turbine power generation facility provided with the combined intermediate valve device which concerns on embodiment. It is a schematic diagram of the combination intermediate valve device which concerns on embodiment which concerns on embodiment. It is an enlarged view of the vicinity of the intercept valve of the combination intermediate valve device which concerns on embodiment, (a) is the case where a valve rod 13b and a drive lever 14b are connected, and (b) is a case where a valve rod 13b and a drive lever 15b are connected. The cases of concatenation are shown respectively. It is a flowchart which shows the opening and closing operation of the intercept valve which concerns on embodiment, (a) shows the time of sudden closing of an intercept valve, (b) shows the time of sudden opening after sudden closing, respectively. It is a figure which shows the structure of the combination intermediate valve device which concerns on the modification of embodiment. It is a schematic block diagram of the combination intermediate valve device which concerns on the related technology. FIG. 6 is a plan view of FIG. 6 as viewed from the PP direction.

In the present embodiment, two intercept valve driving devices for driving the intercept valve are provided, and one of these driving devices and the valve stem of the intercept valve are connected via a clutch mechanism. As a result, the intercept valve can be suddenly closed and then suddenly opened through the discharge of the hydraulic oil from each drive device. Hereinafter, the details will be described. The same parts as those of the combined intermediate valve device according to the above-mentioned related techniques will be described with the same reference numerals.

FIG. 1 is a diagram showing an example of a turbine power generation facility provided with a combined intermediate valve device according to an embodiment. This turbine power generation facility is, for example, a turbine power generation facility for nuclear power generation. In this embodiment, a turbine power generation facility for boiling water reactor power generation (BWR) will be illustrated and described.

As shown in FIG. 1, the turbine power generation facility 1 includes a reactor 2, a main steam stop valve 3a, a steam control valve 3b, a high-pressure steam turbine 4, a moisture separation heater 5, and a low-pressure steam turbine 6. , A generator 7, a condenser 8, a condenser pump 9, and a combined intermediate valve device 10.

The steam generated in the reactor 2 passes through the main steam pipe, sequentially passes through the main steam stop valve 3a and the steam control valve 3b that directly controls the inflow speed and load to the high-pressure steam turbine 4, and then flows into the high-pressure steam turbine 4. do. The steam flowing into the high-pressure steam turbine 4 expands inside the high-pressure steam turbine 4 to rotate and drive the high-pressure steam turbine 4. The steam after working in the high-pressure steam turbine 4 is discharged from the high-pressure steam turbine 4 as exhaust from the high-pressure steam turbine 4, and flows into the moisture separation heater 5 through an around pipe. The moisture separation heater 5 removes moisture in the exhaust gas and heats the exhaust gas to generate reheated steam. After being discharged from the moisture separation heater 5, the reheated steam flows into the low-pressure steam turbine 6 through the intermediate steam stop valve 12a and the intercept valve 12b constituting the combined intermediate valve device 10 in sequence. The reheated steam flowing into the low-pressure steam turbine 6 expands in the low-pressure steam turbine 6 to rotationally drive the low-pressure steam turbine 6. This reheated steam is discharged from the low-pressure steam turbine 6 as exhaust from the low-pressure steam turbine 6, and is condensed into condensate by the condenser 8. The condensate is supplied to the reactor 2 again from the condensate 8 via the condensate pump 9.

As described above, the flow path of steam or condensate flowing through the turbine power generation facility 1 constitutes a closed loop. The rotational energy generated by the rotational drive of the high-pressure steam turbine 4 and the low-pressure steam turbine 6 is converted into electric energy in the generator 7 and sent to the transmission system.

Although the turbine power generation facility 1 including one high-pressure steam turbine 4 and three low-pressure steam turbines 6 is illustrated here, the configuration of the turbine power generation facility 1 is not limited to this case. For example, a configuration including a high-pressure steam turbine, a medium-pressure steam turbine, and a low-pressure steam turbine, or a configuration in which a plurality of at least one of these steam turbines is installed may be used.

Next, the combined intermediate valve device 10 described with reference to FIG. 1 will be described. The same configuration as the combined intermediate valve device according to the related technology will be described with the same reference numerals.

The combined intermediate valve device 10 includes a valve casing 11, an intermediate steam stop valve 12a, an intercept valve 12b, valve rods 13a and 13b, drive levers 14a, 14b, and 15b, a clutch mechanism 16b, and an intermediate steam stop valve. It includes a drive device 20a, an intercept valve drive device 20b (first drive device) and 30b (second drive device), and a hydraulic circuit 40. That is, the combined intermediate valve device 10 includes two drive devices, the intercept valve drive device 20b (first drive device) and the intercept valve drive device 30b (second drive device), as the drive device for the intercept valve 12b.

The intermediate steam stop valve 12a is a valve body of the combined intermediate valve device 10, and its center position is attached to the valve rod 13a. The valve rod 13a is a rotation axis of the intermediate steam stop valve 12a, and is rotatably supported around an axis orthogonal to the valve casing 11 via a bearing portion 11a of the valve casing 11. That is, the intermediate steam stop valve 12a and the valve rod 13a are integrated and rotate around an axial center orthogonal to the valve casing 11. One end of the valve rod 13a is connected to the intermediate steam stop valve drive device 20a described later via a drive lever 14a described later.

The intercept valve 12b is combined with the intermediate steam stop valve 12a to form the valve body of the intermediate valve device 10, and the center position thereof is attached to the valve rod 13b. The valve rod 13b is a rotation axis of the intercept valve 12b, and is rotatably supported around an axis orthogonal to the valve casing 11 via a bearing portion 11b of the valve casing 11. That is, the intermediate steam stop valve 12b and the valve rod 13b are integrated and rotate around an axial center orthogonal to the valve casing 11. A drive lever 14b and an intercept valve drive device 20b are provided on one end side of the valve rod 13b, and a drive lever 15b and an intercept valve drive device 30b are provided on the other end side. A clutch mechanism 16b is provided between the valve rod 13b and the drive levers 14b and 15b, and as will be described later, one of these drive levers and the valve rod 13b are connected via the clutch mechanism 16b.

The intermediate steam stop valve drive device 20a includes a drive rod 21a, a hydraulic cylinder 22a, a dump valve chamber (not shown), and a disc dump valve (not shown). The intermediate steam stop valve drive device 20a is arranged outside the valve casing 11 and at a position unilaterally separated from the center of the valve casing 11 in a posture orthogonal to each other in a side view. At this time, the valve casing 11 and the intermediate steam stop valve drive device 20a are integrally fixed via the connector 18a. A drive rod 21a that can be displaced in the vertical direction protrudes from the center position on one end side of the intermediate steam stop valve drive device 20a, and the tip of the drive rod 21a and the valve rod 13a are connected via a link type drive lever 14a. Will be done. The intermediate steam stop valve drive device 20a displaces the drive rod 21a up and down by adjusting the amount of hydraulic oil supplied to the inside of the hydraulic cylinder 22a, and converts this displacement into rotary motion with the drive lever 14a to convert the valve rod 13a. Is rotated. As a result, the intermediate steam stop valve 12a opens and closes and rotates in the valve casing 11 together with the valve rod 13a. The configuration of the dump valve chamber and the disc dump valve (both not shown) and the operation method thereof are the same as those of the dump valve chamber 23b and the disc dump valve 24b of the intercept valve drive device 20b described later.

The intermediate steam stop valve 12a is set to be fully closed when the hydraulic cylinder 22a is not filled with hydraulic oil, and to be fully open when the hydraulic cylinder 22a is filled with a predetermined amount of hydraulic oil. Has been done.

Next, the intercept valve driving devices 20b and 30b will be described with reference to FIG. FIG. 2 is a schematic view of the combination butterfly valve device according to the embodiment. The intercept valve drive device 20b includes a drive rod 21b, a hydraulic cylinder 22b, a dump valve chamber 23b, and a disc dump valve 24b.

The intermediate steam stop valve drive device 20b is arranged outside the valve casing 11 and at a position unilaterally separated from the center of the valve casing 11 in a posture orthogonal to each other in a side view. At this time, the valve casing 11 and the intermediate steam stop valve drive device 20b are integrally fixed via the connector 18b. A drive rod 21b that can be displaced in the vertical direction protrudes from the center position on one end side of the intercept valve drive device 20b, and its tip is connected to a link type drive lever 14b. The drive rod 21b is integrally formed with the hydraulic cylinder 22b, supplies hydraulic oil to the inside of the hydraulic cylinder 22b, and is movable in the vertical direction by the hydraulic pressure from the hydraulic oil.

A dump valve chamber 23b is provided below the hydraulic cylinder 22b. The dump valve chamber 23b accommodates the disc dump valve 24b and the spring in a state of being connected to each other. Further, the dump valve chamber 23b is provided with a connection port for connecting to the first discharge flow path 45 of the hydraulic circuit 40, which will be described later. When the disc dump valve 24b is open, the connection port connected to the first discharge flow path 45 of the hydraulic circuit 40, which will be described later, is open. When the disk dump valve 24 is closed, the connection port connected to the first discharge flow path 45 of the hydraulic circuit 40, which will be described later, is closed. The details of the opening / closing operation of the disc dump valve 24b will be described later.

On the other hand, the intercept valve drive device 30b includes a drive rod 31b, a hydraulic cylinder 32b, a dump valve chamber 33b, and a disc dump valve 34b. The intermediate steam stop valve drive device 30b is arranged on the outside of the valve casing 11 and on the side facing the intercept valve drive device 20b at a position separated from the center of the valve casing 11 to one side and orthogonal to each other in a side view. .. At this time, the valve casing 11 and the intermediate steam stop valve drive device 30b are integrally fixed via the connector 19b. A drive rod 31b that can be displaced in the vertical direction protrudes from the center position on one end side of the intercept valve drive device 30b, and its tip is connected to a link type drive lever 15b. The configurations of the dump valve chamber 33b and the disk dump valve 34b are the same as those of the intercept valve drive device 20b.

Here, the connection relationship between the valve rod 13b and the drive levers 14b and 15b will be described in more detail with reference to FIG. FIG. 3 is an enlarged view of the vicinity of the intercept valve of the combined intermediate valve device according to the embodiment. FIG. 3A is a case where the valve rod 13b and the drive lever 14b are connected, and FIG. 3B is a drive with the valve rod 13b. The case where the lever 15b is connected is shown respectively. The arrow of the alternate long and short dash line extending from the control device 17b to the clutch mechanism 16b shown in FIG. 3 indicates a control command from the control device 17b to the clutch mechanism 16b. Further, in this figure, the control device 17b is arranged around the intercept valve 12b, which exemplifies that the control device 17b transmits a control command to the clutch mechanism 16b. It does not indicate that the installation position of the control device 17b is at this position.

As shown in FIGS. 3A and 3B, a clutch mechanism 16b is provided between the drive levers 14b and 15b and the valve rod 13b. The clutch mechanism 16b is, for example, a hydraulic clutch mechanism provided with a hydraulic cylinder, and the clutch mechanism hydraulic circuit (not shown) for supplying hydraulic oil to the hydraulic cylinder and the hydraulic circuit based on a control command from the control device 17b. It is equipped with an electromagnetic valve (not shown) that supplies or shuts off hydraulic oil. That is, hydraulic oil is supplied to the clutch mechanism 16b from the clutch mechanism hydraulic circuit (not shown) based on the control command from the control device 17b. When the clutch mechanism 16b is displaced by the hydraulic pressure from the hydraulic oil, the valve rod 13b and the drive lever 14b are connected (the state shown in FIG. 3A), or the valve rod 15b and the drive lever 15b are connected (the state shown in FIG. 3A). The state shown in FIG. 3 (b)). A detailed description of the connection between the valve rod 13b and the drive lever 14b or 15b will be described later.

Next, the hydraulic circuit 40 that supplies hydraulic oil to the intercept valve drive devices 20b and 30b will be described with reference to FIG. The hydraulic circuit 40 includes a first hydraulic oil supply flow path 41 (first supply flow path), shutoff valves 42 and 52, servo valves 43 and 53, a first emergency oil supply flow path 44, and a first. One discharge flow path 45, a first rapidly operating solenoid valve 46, a second hydraulic oil supply flow path 51 (second supply flow path), a second emergency oil supply flow path 54, and a second. The discharge flow path 55 of the above and the second rapid-acting solenoid valve 56 are provided. In addition to this, the hydraulic circuit 40 is a command unit (not shown) that outputs control commands to the servo valves 43 and 53, the first fast-acting solenoid valve 46, and the second quick-acting solenoid valve 56, respectively. ). Regarding the various configurations of the hydraulic circuit 40 shown in FIG. 2, those whose drawing numbers start with 4 (excluding the hydraulic circuit 40) are related to the intercept valve drive device 20b, and those whose drawing numbers start with 5 are intercept valves. It relates to the drive device 30b.

The first hydraulic oil supply flow path 41 is a hydraulic oil flow path supplied from the hydraulic pressure supply device (not shown) to the hydraulic cylinder 22b of the intercept valve drive device 20b, and the second hydraulic oil supply flow path 51 is hydraulic pressure. It is a flow path of hydraulic oil supplied from a supply device (not shown) to a hydraulic cylinder 32b of an intercept valve drive device 30b.

The isolation valve 42 is provided on the upstream side of the first hydraulic oil supply flow path 41. The shutoff valve 42 accommodates a piston inside, and a part of emergency oil flowing through the first emergency oil supply flow path 44, which will be described later, is supplied to the upper portion of the piston. When emergency oil is not supplied to the isolation valve 42, the flow path from the first hydraulic oil supply flow path 41 to the servo valve 43 is closed by this piston. When emergency oil is supplied to the isolation valve 42, the emergency oil pushes down the piston to open the flow path from the first hydraulic oil supply flow path 41 to the servo valve 43. The isolation valve 52 is provided on the upstream side of the second hydraulic oil supply flow path 51, and its configuration and operation are the same as those of the isolation valve 42.

The servo valve 43 has a flow of supplying hydraulic oil from the hydraulic pressure generator (not shown) to the hydraulic cylinder 22b via the first hydraulic oil supply flow path 41 and a flow inside the hydraulic cylinder 22b based on a control command from the command unit. It controls the flow of hydraulic oil discharged through the first discharge flow path 45 described later. The servo valve 53 has a flow of supplying hydraulic oil from the hydraulic pressure generator (not shown) to the hydraulic cylinder 32b via the second hydraulic oil supply flow path 51 and a flow inside the hydraulic cylinder 32b based on a control command from the command unit. It controls the flow of hydraulic oil discharged through the second discharge flow path 55, which will be described later.

The first emergency oil supply flow path 44 is an emergency oil flow path supplied from the hydraulic pressure supply device (not shown) to the dump valve chamber 23b of the intercept valve drive device 20b, and the second emergency oil supply flow path 54 is. It is a flow path of emergency oil supplied from the hydraulic pressure supply device (not shown) to the dump valve chamber 33b of the intercept valve drive device 30b. In the present embodiment, the hydraulic oil and the emergency oil are supplied from the same hydraulic pressure supply device (not shown), and among the oils from the hydraulic pressure supply device (not shown), the oil is supplied to the hydraulic cylinders 22b and 32b to drive the rod. The oil that applies hydraulic pressure to 21b and 31b is called hydraulic oil, and the oil that is supplied to the dump valve chambers 23b and 33b and applies hydraulic pressure to the disc dump valves 24b and 34b is called emergency oil.

The first discharge flow path 45 is a flow path for discharging the hydraulic oil inside the hydraulic cylinder 22b and the emergency oil inside the dump valve chamber 23b to the hydraulic supply device (not shown), and the second discharge flow path 55 is the hydraulic cylinder. This is a flow path for discharging the hydraulic oil inside the 32b and the emergency oil inside the dump valve chamber 33b to the hydraulic pressure supply device (not shown).

The first rapidly operating solenoid valve 46 is in a non-excited state during normal operation (normal operation), and connects the emergency oil supply flow path 44 and the dump valve chamber 23b. On the other hand, in the event of an abnormality (when a turbine trip or load cutoff occurs), the excitation state is set based on a control command from the command unit (not shown), and the first emergency oil supply flow path 44 and the dump valve chamber 23b are connected. At the same time as shutting off, the dump valve chamber 23b and the first discharge flow path 45 are connected, and the hydraulic oil inside the hydraulic cylinder 22b is quickly discharged. Similarly, for the second rapidly operating solenoid valve 56, the second emergency oil supply flow path 54 and the dump valve chamber 33b are normally connected, and in the event of an abnormality, the dump valve chamber 33b and the second discharge flow path 55 are connected. And are connected. These rapidly operating solenoid valves are driven by an intercept valve when supplying hydraulic oil to the hydraulic cylinder or during normal operation of the turbine power generation facility 1 (when adjusting the amount of hydraulic oil inside the hydraulic cylinder within a predetermined range). The device and the discharge flow path are cut off (non-excited state). A detailed description of the first and second fast-acting solenoid valves 46, 56 will be described later.

Next, the operation of the intercept valve 12b of the present embodiment will be described. For comparison, after explaining the operation of the intercept valve 12b in the normal time (normal operation) of the turbine power generation facility 1, the intercept valve 12b in the case of an abnormality in the turbine power generation facility 1 (when a turbine trip or load cutoff occurs) Explain the action.

(Normal time)
The operation of the intercept valve 12b in a normal state will be described with reference to FIG. Normally, the valve rod 13b and the drive lever 14b are connected via the clutch mechanism 16b. That is, the intercept valve 12b is rotated by the intercept valve drive device 20b. At this time, the intercept valve drive device 30b is filled with a predetermined amount of hydraulic oil. Further, based on a control command from a command unit (not shown), the servo valve 43 has the first hydraulic oil supply flow path 41 and the hydraulic cylinder 22b, and the servo valve 53 has the second hydraulic oil supply flow path 51 and the hydraulic pressure. The cylinders 32b are connected to each other.

When supplying hydraulic oil to the intercept valve drive device 20b (when opening the intercept valve 12b), the first emergency oil supply flow path 44, first from the hydraulic pressure supply device (not shown), before supplying the hydraulic oil. Emergency oil is supplied to the dump valve chamber 23b through one of the rapidly operating solenoid valves 46. When emergency oil is supplied to the dump valve chamber 23b, the disc dump valve 24b receives upward hydraulic pressure from the emergency oil. When this hydraulic pressure overcomes the restoring force of the spring connected to the disc dump valve 24b, the disc dump valve 24 is displaced upward and closes the connection port between the hydraulic cylinder 22b and the first discharge flow path 45. Further, a part of the emergency oil flowing through the first emergency oil supply flow path 44 is supplied to the isolation valve 42 and pushes down the piston constituting the isolation valve 42. As a result, the flow path from the first hydraulic oil supply flow path 41 to the servo valve 43 is opened.

In this state, when the servo valve 43 connects the first hydraulic oil supply flow path 41 and the hydraulic cylinder 22b based on the control command from the command unit (not shown), the hydraulic oil from the hydraulic oil supply device (not shown) Is supplied to the hydraulic cylinder 22b via the first hydraulic oil supply flow path 41, the shutoff valve 42, and the servo valve 43 in that order. When the hydraulic oil is supplied to the hydraulic cylinder 22b, the drive rod 21a is displaced upward by the hydraulic pressure from the hydraulic oil. The drive lever 14b converts the displacement of the drive rod 21a into a rotary motion to rotate the valve rod 13b and the intercept valve 12b. As a result, the intercept valve 12b opens.

The case of supplying hydraulic oil to the intercept valve drive device 30b is the same as that of the intercept valve drive device 20b. That is, before supplying the hydraulic oil, the emergency oil is supplied from the hydraulic pressure supply device (not shown) to the dump valve chamber 33b via the second emergency oil supply flow path 54 and the second rapidly operating solenoid valve 56, and the disk is used. The dump valve 34b is displaced upward to close the connection port between the hydraulic cylinder 32b and the second discharge flow path 55. Further, a part of the emergency oil flowing through the second emergency oil supply flow path 54 is supplied to the shutoff valve 52, and this emergency oil pushes down the piston and flows from the second hydraulic oil supply flow path 51 to the servo valve 53. Open the road. In this state, the servo valve 53 is controlled based on a control command from the command unit (not shown) to connect the second hydraulic oil supply flow path 51 and the hydraulic cylinder 32b. Then, the hydraulic oil is supplied from the hydraulic pressure supply device (not shown) to the hydraulic cylinder 32b via the second hydraulic oil supply flow path 51. Normally, hydraulic oil is supplied to the hydraulic cylinder 32b by the above procedure, and a predetermined amount of hydraulic oil is filled therein. Further, since the hydraulic cylinder 32b is filled with a predetermined amount of hydraulic oil, the drive rod 31b is displaced upward.

On the other hand, when the hydraulic oil is discharged from the intercept valve drive device 20b in order to adjust the opening of the intercept valve 12b, the servo valve 43 supplies the first hydraulic oil based on the control command from the command unit (not shown). The flow path 41 and the hydraulic cylinder 22b are shut off, and the hydraulic cylinder 22b and the first discharge flow path 45 are connected to each other. As a result, the hydraulic oil inside the hydraulic cylinder 22b is discharged to the hydraulic supply device (not shown) via the first discharge flow path 45, and the intercept valve 12b and the valve rod 13b rotate in the closing direction. When the intercept valve 12b reaches a predetermined opening, the servo valve 43 is adjusted to the neutral position based on the control command from the command unit (not shown), and the hydraulic cylinder 22b is the first hydraulic oil supply flow. It is assumed that it is not connected to the road 41 or the first discharge flow path 45.

As described above, in the normal state, the valve rod 13b and the drive lever 14b are connected via the clutch mechanism 16b, and the opening of the intercept valve 12b is adjusted by the driving force (hydraulic pressure) from the intercept valve drive device 20b. This opening is adjusted by adjusting the connection between the hydraulic cylinder 22b and the first hydraulic oil supply flow path 41 or the first discharge flow path 45 via the servo valve 43, and controlling the amount of hydraulic oil inside the hydraulic cylinder 22b. It is realized by doing.

(In case of abnormality)
Next, with reference to FIGS. 2 and 4, the operation when the intercept valve 12b is suddenly closed and suddenly opened (at the time of abnormality) from the normal time will be described. 4A and 4B are flowcharts showing an opening / closing operation of the intercept valve according to the embodiment, in which FIG. 4A shows a sudden closing time of the intercepting valve, and FIG. 4B shows a sudden opening time after the sudden closing. In this embodiment, a case where a turbine trip occurs as an abnormal time and a case where the load is cut off due to a system accident such as a lightning strike will be described as an example. Further, the sudden closing or sudden opening of the intercept valve 12b here means that the intercept valve 12b is rotated in a time earlier than a normal opening / closing operation, for example, a time of less than 1 second, and the intercept valve 12b is opened / closed in a hurry. To say.

Further, in the following description, the normal time will be described as the initial state. That is, in the initial state, the isolation valves 42 and 52 and the servo valves 43 and 53 are opened, and the hydraulic cylinders 22b and 32b pass through the first hydraulic oil supply flow path 41 or the second hydraulic oil supply flow path 51. Each of the above is filled with a predetermined amount of hydraulic oil. Further, the valve rod 13b is connected to the drive lever 14b via the clutch mechanism 16b, and the intercept valve 12b and the valve rod 13b rotate to the fully open position. Further, since the hydraulic cylinder 32b is filled with a predetermined amount of hydraulic oil, the drive rod 31b is located above.

(When closing suddenly)
As shown in FIG. 4A, when a turbine trip or load interruption occurs, the command unit (not shown) excites the first fast-acting solenoid valve 46 (first fast-acting solenoid according to FIG. 2). A control command (which displaces the valve body of the valve 46 downward) is output (S1). When the first fast-acting solenoid valve 46 is excited based on this control command, the dump valve chamber 23b is shut off from the first emergency oil supply flow path 44 and connected to the first discharge flow path 45 ( S2). When the emergency oil is discharged from the inside of the dump valve chamber 23b, the disc dump valve 24b is displaced downward due to the restoring force from the spring, and the connection port from the dump valve chamber 23b to the first discharge flow path 45 is opened ( S3). As a result, the hydraulic oil inside the hydraulic cylinder 22b is discharged from the connection port to the hydraulic supply device (not shown) via the first discharge flow path 45 (S4), and the drive rod 21b is displaced downward. When the drive rod 21b is displaced downward, the drive lever 14b converts this displacement into a rotary motion and rotates the valve rod 13b and the intercept valve 12b in the closing direction (S5). As a result, the intercept valve 12b is suddenly closed (quickly fully closed) (S6).

When the first fast-acting solenoid valve 46 is excited (that is, in the case of step S2), the flow path of the emergency oil to the isolation valve 42 is also the first discharge flow through the first quick-acting solenoid valve 46. It is connected to the road 45, and the emergency oil inside the shutoff valve 42 is discharged to the first discharge flow path 45 together with the emergency oil inside the dump valve chamber 23b. As a result, the flow path from the first hydraulic oil supply flow path 41 to the servo valve 43 is closed, and the supply of hydraulic oil to the hydraulic cylinder 22b is cut off.

(When opening suddenly after sudden closing)
As shown in FIG. 4B, when the intercept valve 12b is suddenly closed and then suddenly opened again (quickly fully opened) in order to continuously operate the low pressure steam turbine 6, the control device 17b is referred to the clutch mechanism 16b. Then, the connection between the valve rod 13b and the drive lever 14b is cut off, and a control command for connecting the valve rod 13b and the drive lever 15b is output (S7). The clutch mechanism 16b connects the valve rod 13b and the drive lever 15b based on this control command (S8). After this, the command unit (not shown) outputs a control command for exciting the second fast-acting solenoid valve 56 (displaces the valve body of the second fast-acting solenoid valve 56 shown in FIG. 2 downward). (S9). When the second rapidly operating solenoid valve 56 is excited based on this control command, the dump valve chamber 33b is shut off from the second emergency oil supply flow path 54 and connected to the second discharge flow path 55 ( S10). When the emergency oil is discharged from the inside of the dump valve chamber 33b, the disc dump valve 34b is displaced downward due to the restoring force from the spring, and the connection port from the dump valve chamber 33b to the second discharge flow path 55 is opened ( S11). As a result, the hydraulic oil inside the hydraulic cylinder 32b is discharged from the connection port to the hydraulic supply device (not shown) via the second discharge flow path 55 (S12), and the drive rod 31b is displaced downward. When the drive rod 21b is displaced downward, the drive lever 15b converts this displacement into a rotary motion, and the valve rod 13b and the intercept valve 12b are further rotated from the fully closed position in the same rotational direction as when the valve rod 13b is suddenly closed (S13). .. As a result, the intercept valve 12b is suddenly opened (quickly fully opened) (S14).

When the second fast-acting solenoid valve 56 is excited (that is, in the case of step S10), the flow path of the emergency oil to the isolation valve 52 is also the second discharge flow through the second fast-acting solenoid valve 56. It is connected to the road 55, and the emergency oil inside the shutoff valve 52 is discharged to the second discharge flow path 55 together with the emergency oil inside the dump valve chamber 33b. As a result, the flow path from the second hydraulic oil supply flow path 51 to the servo valve 53 is closed, and the supply of hydraulic oil to the hydraulic cylinder 32b is cut off.

That is, the valve rod 13b is connected to the intercept valve driving device 20b or 30b, which is the driving device of the intercept valve, via the clutch mechanism 16b according to the operations of the sudden closing and the subsequent sudden opening of the intercept valve 12b. To switch. Then, the intercept valve 12b can execute the sudden closing of the valve body and the subsequent sudden opening through the sequential discharge of the hydraulic oil from the drive device connected to the valve rod 13b.

According to the above-described embodiment, the intercept valve 12b is provided with two drive devices, the intercept valve drive devices 20b and 30b, and the clutch mechanism 16b is operated in response to the sudden closing and subsequent sudden opening of the intercept valve 12b. Then, the connection between the intercept valve driving device 20b or 30b and the valve rod 13b is adjusted. Then, hydraulic oil is supplied from the hydraulic cylinder 22b of the intercept valve drive device 20b when the intercept valve 12b is suddenly closed, and from the hydraulic cylinder 32b of the intercept valve drive device 30b when the intercept valve 12b is suddenly closed and then suddenly opened. By discharging, the intercept valve 12b can be suddenly closed and then suddenly opened only by discharging the hydraulic oil. Therefore, when the intercept valve 12b is suddenly closed and then suddenly opened again, it is not necessary to supply the hydraulic oil again to the hydraulic cylinder from which the hydraulic oil has been discharged once, and the intercept valve 12b can be suddenly opened in a shorter time than before. Further, since the intercept valve can be suddenly opened without supplying the hydraulic oil to the hydraulic cylinder, it is not necessary to supply a large amount of the hydraulic oil even when a plurality of intercept valves are suddenly opened at one time.

Further, in the present embodiment, for example, during the sudden opening after the sudden closing, the hydraulic oil is supplied again to the hydraulic cylinder 22b of the intercept valve drive device 20b, and a predetermined amount of the hydraulic oil is filled inside the hydraulic cylinder 22b. be able to. That is, in parallel with the opening / closing operation of the intercept valve 12b, the hydraulic oil can be supplied to the drive device on the side not connected to the valve rod 13b. Therefore, since it is possible to prepare for the other operation in parallel while executing one of the sudden closing or the sudden opening operation, even if the sudden closing or the sudden opening operation is required again, the switching by the clutch mechanism 16b is performed. If you perform an operation, you can immediately execute a sudden closing or sudden opening operation.

In the present embodiment, the case where the two drive devices are provided only on the intercept valve 12b has been described as an example, but the intermediate steam stop valve 12a may also be provided with the two drive devices, or the intermediate steam stop valve 12a may also be provided with the two drive devices. Two drive devices may be provided only on the valve 12a, and one drive device may be provided on the intercept valve 12b as in the conventional case. However, when two drive devices are provided, these drive devices and the valve stem are connected via a clutch mechanism.

Further, as a modification of the present embodiment, for example, as shown in FIG. 5, the hydraulic circuit 40 newly provides a third discharge flow path 57 and a third fast-acting solenoid valve 58, and the hydraulic cylinder 32b is vertically operated. A connection port connected to the third discharge flow path 57 may be provided at an intermediate position of the above. In the case of this configuration, it is preferable to adjust the conversion ability of the drive lever 15b to the rotary motion, for example, to have twice the conversion ability of the drive lever 14b. That is, it is preferable to design the drive lever 15b to rotate the valve rod 13b and the intercept valve 12b by a rotation angle twice that of the drive lever 14b when the drive rod is displaced by the same displacement amount. With such a configuration, the intercept valve 12b can be rotated half a circle through the discharge of the hydraulic oil from the intercept valve drive device 30b of the modified example.

That is, at the time of sudden opening after sudden closing, the third rapidly operating solenoid valve 58 is excited without discharging the hydraulic oil of the dump valve chamber 23b based on the control command from the command unit (not shown), and the hydraulic cylinder 32b. Half of the predetermined amount of hydraulic oil filled inside is discharged to the hydraulic pressure supply device (not shown) in sequence through the third rapidly operating solenoid valve 58, the third discharge flow path 57, and the second discharge flow path 55. Let me. At this time, since the conversion capacity of the drive lever 15b is twice that of the drive lever 14b, the intercept valve 12b can be suddenly opened only by discharging a predetermined half amount of hydraulic oil. When a predetermined half amount of hydraulic oil is discharged or the valve opening of the intercept valve 12b is detected by a sensor (not shown) or the like and it is confirmed that the intercept valve 12b is suddenly opened, the command unit (not shown). The third rapidly operating solenoid valve 58 is returned to non-excitation by a control command from. With such a configuration, for example, even if a turbine trip or load cutoff occurs again after sudden opening, the remaining hydraulic oil inside the hydraulic cylinder 32b is discharged by the same method as in the first embodiment to intercept the valve. 12b can be closed again.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1. 1. Turbine power generation equipment, 2. Reactor, 3a. Main steam stop valve, 3b. Steam control valve, 4. High pressure steam turbine, 5. Moisture separation heater, 6. Low pressure steam turbine, 7. Generator, 8. Condenser, 9. Condensation pump, 10. Combination intermediate valve device, 11. Valve casings, 11a, 11b. Bearing portion, 12a. Intermediate steam stop valve, 12b. Intercept valves, 13a, 13b. Valve rods, 14a, 14b, 15b. Drive lever, 16b. Clutch mechanism, 17b. Control devices, 18a, 18b, 19b. Couplings, 20a. Intermediate steam stop valve drive device, 20b, 30b. Intercept valve drive device, 21a, 21b, 31b. Drive rods, 22a, 22b, 32b. Hydraulic cylinders, 23b, 33b. Disc dump valve, 40. Hydraulic circuit, 41. First hydraulic oil supply channel, 42, 52. Isolation valve, 43, 53. Servo valve, 44. First emergency oil supply channel, 45. First drainage channel, 46. First fast-acting solenoid valve, 51. Second hydraulic oil supply channel, 54. Second emergency oil supply channel, 55. Second drainage channel, 56. Second fast-acting solenoid valve, 57. Third drainage channel, 58. Third fast-acting solenoid valve

Claims (4)

A combination intermediate valve device that controls the amount of steam supplied to the steam turbine from the steam flow path through the valve body by adjusting the amount of hydraulic oil in the hydraulic cylinder and rotating the valve rod to which the valve body is attached. And,
A first and second drive device comprising the hydraulic cylinder, adjusting the amount of the hydraulic oil supplied to the hydraulic cylinder, and transmitting a driving force to the valve body via the valve rod.
Provided between the first drive device and the valve rod, and between the second drive device and the valve rod, with either the valve rod and the first and second drive devices. With the clutch mechanism that connects
A control device that outputs a control command for adjusting the connection by the clutch mechanism, and
Equipped with
During normal operation of the steam turbine, the valve rod is connected to the first drive device via the clutch mechanism, and the valve body is opened by the amount of hydraulic oil in the hydraulic cylinder of the first drive device. Adjust and
When the valve body is suddenly closed during abnormal operation of the steam turbine, the supply of the hydraulic oil to the hydraulic cylinder of the first drive device is cut off, and the hydraulic cylinder of the first drive device is said to be the same. Drain the hydraulic oil,
When the valve body is suddenly opened after the sudden closing, the clutch mechanism shuts off the first drive device and the valve rod based on a control command from the control device, and the second. The hydraulic pressure of the second drive device is filled with a predetermined amount of hydraulic oil by connecting the drive device of the above and the valve rod and cutting off the supply of the hydraulic oil to the hydraulic cylinder of the second drive device. A combined intermediate valve device that discharges the hydraulic oil from a cylinder. The first and second hydraulic oil supply channels for supplying the hydraulic oil to the hydraulic cylinders of the first and second drive devices, respectively.
The first and second discharge channels for discharging the hydraulic oil from the hydraulic cylinders of the first and second drive devices, respectively.
A first fast-acting solenoid valve that connects any of the first discharge flow path and the first supply flow path with the first drive device based on an external control command.
A second fast-acting solenoid valve that connects any of the second discharge flow path and the second supply flow path with the second drive device based on an external control command.
Equipped with
During the normal operation, the first hydraulic oil supply flow path and the first drive device are connected to the first hydraulic oil supply flow path via the first fast-acting solenoid valve, and the second rapid-acting solenoid valve is used to connect the first hydraulic oil supply flow path to the first drive device. The hydraulic oil supply flow path and the second drive device are connected to each other, and the first supply flow path is connected to the hydraulic cylinder of the first drive device, and the second supply flow path is used to drive the second drive device. Supply a predetermined amount of hydraulic oil to each hydraulic cylinder of the device,
When the valve body is suddenly closed during the abnormal operation, the first quick-acting solenoid valve is excited based on an external control command, and the first quick-acting solenoid valve is used to excite the first quick-acting solenoid valve. By connecting the discharge flow path and the first drive device, the hydraulic oil is discharged from the hydraulic cylinder of the first drive device to the first discharge flow path.
When the valve body is suddenly opened after the sudden closing, the second fast-acting solenoid valve is based on an external control command after the valve rod is connected to the second drive device by the clutch mechanism. The second discharge flow path and the second drive device are connected to each other via the second rapid-acting solenoid valve, and the second discharge from the hydraulic cylinder of the second drive device. The combined intermediate valve device according to claim 1, wherein the hydraulic oil is discharged to the flow path. When the valve body is suddenly opened after the sudden closing, the first hydraulic oil supply flow path and the first driving device are connected via the first rapid operating solenoid valve, and the first driving device is connected. The predetermined amount of the hydraulic oil is supplied from one hydraulic oil supply flow path to the hydraulic cylinder of the first drive device.
When the valve body is suddenly closed again after the sudden opening, the clutch mechanism connects the first drive device and the valve rod by a control command from the control device, and is based on a control command from the outside. The first rapid-acting solenoid valve is excited, and the first discharge flow path and the first drive device are connected via the first rapid-acting solenoid valve to connect the first drive device. The combined intermediate valve device according to claim 2, wherein the hydraulic cylinder of the above discharges the hydraulic oil to the first discharge flow path. A turbine power generation facility including the combination intermediate valve device according to any one of claims 1 to 3.

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