JP7267879B2 - steam turbine valve drive - Google Patents

Description

Embodiments of the present invention relate to steam turbine valve drives.

Generally, in a steam turbine power generation facility, a steam turbine valve drive device controls the opening of a steam valve to control the amount of steam flowing into the steam turbine in order to adjust the rotation speed and output of the steam turbine. .

A steam turbine valve drive includes a hydraulic system to supply or exhaust hydraulic fluid. As a result, in the steam turbine valve drive device, the piston housed inside the cylinder is driven to control the operation of the steam valve.

When an abnormality occurs in the steam turbine power generation equipment, in order to protect the equipment that composes the steam turbine power generation equipment, the steam valves are quickly closed to shut off the steam path through which steam flows to the steam turbine. and shut down the steam turbine.

Conventionally, for example, hydraulic fluid is supplied from one centralized hydraulic generator to each steam turbine valve drive through hydraulic fluid lines. It has also been proposed to mount a servomotor and a pump on each steam turbine valve drive in addition to one centralized hydraulic pressure generator (see, for example, Patent Document 1). Further, a hydraulic drive system has been proposed in which each hydraulic drive system is equipped with a hydraulic pressure source without using an integrated hydraulic pressure generation source (see, for example, Patent Document 2).

In addition, as a method for driving steam valves, there has been proposed a valve drive system equipped with a hydraulic pressure source, in which each steam turbine valve drive system is equipped with a hydraulic pressure generation source without providing a single integrated hydraulic pressure generator. Here, a two-way pump is provided between the oil passages connecting the two oil chambers of the cylinder, and by controlling the rotation speed of the motor connected to the pump, the volume of the oil in the two oil chambers is controlled to generate steam. Controls the valve opening. In addition, when performing a rapid closing operation, which is important as a steam valve driving device, the oil in the load side oil chamber (high pressure side oil chamber) is discharged by the action of the self-closing spring. Specifically, when the steam valve is suddenly closed, the load side oil chamber and the anti-load side oil chamber (low pressure side oil chamber) are communicated via the solenoid valve by operating the solenoid valve. , oil is discharged from the load-side oil chamber to the anti-load-side oil chamber by the action of the self-closing spring (see Patent Document 3).

Japanese Unexamined Patent Application Publication No. 2016-70500 JP 2012-102855 A JP 2017-160890 A

When a solenoid valve is used to quickly close a steam valve, it may be difficult to perform the quick closing operation at a sufficiently high speed unless the size of the solenoid valve is increased according to the size of the cylinder.

Due to the circumstances as described above, it may not be easy to perform the rapid closing operation with high reliability.

Accordingly, the problem to be solved by the present invention is to provide a steam turbine valve drive device capable of executing a rapid closing operation with high reliability.

A steam turbine valve drive device according to an embodiment includes a cylinder, a two-way pump, an oil reservoir, a rapid closing dump valve, and a rapid closing solenoid valve, and is a steam valve installed in a steam flow path that supplies steam to a steam turbine. driving part. The cylinder accommodates a piston provided in an operating rod that operates the steam valve portion, and is divided into a load-side oil chamber and an anti-load-side oil chamber by the piston. The two-way pump performs the opening operation of the steam valve portion by supplying hydraulic oil to the load side oil chamber through the load side opening control oil passage, and also through the non-load side opening control oil passage. The closing operation of the steam valve portion is executed by supplying hydraulic oil to the anti-load side oil chamber. The oil reservoir stores hydraulic oil. The quick-closing dump valve is installed in the quick-closing oil passage that is connected to each of the load-side opening control oil passage and the non-load-side opening control oil passage. is configured to be closed when hydraulic oil is supplied to the pilot oil chamber. The rapid closing solenoid valve is provided in the solenoid valve installation oil passage that connects the oil reservoir and the pilot oil chamber. A first control oil check valve is installed in the load side control oil passage connected to the load side opening control oil passage, and an anti-load control oil passage connected to the anti-load side opening control oil passage. A second control oil check valve is installed in the side control oil passage. The first check valve for control oil is configured so that hydraulic oil flows from the oil reservoir to the load side opening control oil passage, and the second check valve for control oil is configured so that the hydraulic oil flows back from the oil reservoir. It is configured to flow through the load side opening control oil passage. When performing the opening operation and the closing operation, the rapid closing dump valve is closed by energizing the rapid closing solenoid valve and supplying hydraulic oil from the oil reservoir to the pilot oil chamber. When the quick closing operation is performed, the quick closing solenoid valve is de-energized and the hydraulic oil from the pilot oil chamber is discharged to the oil reservoir, thereby opening the quick closing dump valve and quickly closing the valve. Hydraulic oil in the load-side oil chamber flows to the anti-load-side oil chamber via the oil passage.

FIG. 1 is a diagram showing essential parts of a steam valve unit 10 and a steam turbine valve drive device 20 that constitute a steam turbine power generation facility in the first embodiment. FIG. 2 is a diagram schematically showing a state in which the steam turbine valve driving device 20 performs a normal opening operation of the steam valve unit 10 (Case 1) in the first embodiment. FIG. 3 is a diagram schematically showing a state in which the steam turbine valve driving device 20 performs a normal closing operation of the steam valve unit 10 (Case 2) in the first embodiment. FIG. 4 is a diagram schematically showing a state in which the steam turbine valve driving device 20 performs a rapid closing operation of the steam valve unit 10 (Case 3) in the first embodiment. FIG. 5 is a diagram showing essential parts of the steam valve section 10 and the hydraulic drive section 30 in a modification of the first embodiment. FIG. 6 is a diagram showing essential parts of a steam valve unit 10 and a steam turbine valve driving device 20 that constitute steam turbine power generation equipment in the second embodiment. FIG. 7 is a view showing the rapid closing solenoid valve V54 in the steam turbine valve drive system 20 of the second embodiment. FIG. 8 is a diagram showing a main part of the hydraulic circuit section 50 in the fourth embodiment. FIG. 9 is a diagram showing a main part of the hydraulic circuit section 50 in the fifth embodiment. FIG. 10 is a diagram showing a main part of the hydraulic circuit section 50 in the sixth embodiment. FIG. 11 is a diagram showing a main part of the hydraulic circuit section 50 in the seventh embodiment. FIG. 12 is a diagram showing a main part of the hydraulic circuit section 50 in the eighth embodiment. FIG. 13 is a diagram showing a main part of the hydraulic circuit section 50 in the ninth embodiment. FIG. 14 is a diagram showing a main part of the hydraulic circuit section 50 in the tenth embodiment.

<First embodiment>
[A] Configuration In the first embodiment, main parts of the steam valve unit 10 and the steam turbine valve driving device 20 that constitute the steam turbine power generation facility will be described with reference to FIG. 1 . FIG. 1 shows how the steam turbine valve driving device 20 performs the normal opening operation and the normal closing operation of the steam valve unit 10 .

As shown in FIG. 1, in the steam turbine power generation facility of the present embodiment, the steam valve unit 10 is driven by the steam turbine valve driving device 20, thereby supplying the working medium from the boiler (not shown) to the steam turbine (not shown). It is configured such that the flow of steam supplied as is controlled. Details of each unit will be described in order.

[A-1] Steam valve unit 10
The steam valve portion 10 is a steam valve main body, and as shown in FIG. The opening between and varies. The steam valve unit 10 is installed in a flow path of steam flowing to the steam turbine, and its opening is controlled, for example, to control the flow rate of steam when the steam turbine is started.

The valve box portion 11 of the steam valve portion 10 is formed with a steam inlet P11A through which the steam F11A flows in and a steam outlet P11B through which the steam F11B flows out. The valve seat 13 is fixed inside the valve body portion 11 . The valve seat 13 includes a portion with which the valve body 15 contacts when the steam valve portion 10 is closed.

The valve stem 14 is a rod-shaped body, and is installed so as to pass through a through-hole formed in the valve body portion 11 . A valve stem 14 is provided to move in the direction along the axis.

The valve body 15 is housed inside the valve body portion 11 . The valve body 15 is connected to one end of the valve stem 14 and moves together with the valve stem 14 . The valve body 15 moves away from the valve seat 13 when opening the steam valve portion 10 . On the other hand, when the steam valve portion 10 is closed, the valve body 15 moves closer to the valve seat 13, and the valve body 15 comes into contact with the valve seat 13, whereby the steam valve portion 10 is completely closed. become.

[A-2] Steam turbine valve drive device 20
The steam turbine valve drive device 20 is installed to operate the steam valve section 10 . The steam turbine valve driving device 20 performs opening and closing operations for the steam valve section 10 by driving the hydraulic driving section 30 by the hydraulic circuit section 50 . In the steam turbine valve drive device 20 , the operation of the hydraulic drive section 30 is controlled by the control device 70 controlling the operation of the hydraulic circuit section 50 .

[A-2-1] Hydraulic drive unit 30
In the steam turbine valve drive device 20, the hydraulic drive section 30 is a hydraulic drive device, and is installed in the steam valve section 10 as shown in FIG. The hydraulic drive unit 30 has a piston 35 provided on an operation rod 31 that operates the steam valve unit 10 , and the piston 35 is accommodated in the cylinder 32 . The hydraulic drive unit 30 is configured such that the operation rod 31 operates the steam valve unit 10 by driving the piston 35 inside the cylinder 32 by the action of hydraulic oil.

[A-2-1-1] Operating rod 31
The operating rod 31 of the hydraulic drive unit 30 is a rod-shaped body, coaxial with the valve stem 14 , and connected to the valve stem 14 via a coupling 311 at one end. An opening detector 38 is provided at the other end of the operating rod 31 . A piston 35 is provided in the central portion of the operating rod 31 . In this embodiment, the operating rod 31 and the valve stem 14 are coaxial. may be configured so as not to be coaxial.

[A-2-1-2] Cylinder 32
The cylinder 32 of the hydraulic drive unit 30 accommodates the piston 35 in the internal space C32. An internal space C32 of the cylinder 32 is divided by the piston 35 into a load side oil chamber C32a and an anti-load side oil chamber C32b. Further, the cylinder 32 is formed with a first hydraulic fluid port P32a, a second hydraulic fluid port P32b, and a third hydraulic fluid port P32c.

The load-side oil chamber C<b>32 a is positioned closer to the steam valve portion 10 than the piston 35 in the internal space C<b>32 of the cylinder 32 . The load-side oil chamber C32a is provided with a first hydraulic fluid port P32a and a third hydraulic fluid port P32c.

The anti-load side oil chamber C32b is located closer to the opening detector 38 than the piston 35 in the internal space C32 of the cylinder 32 . The anti-load side oil chamber C32b is provided with a second hydraulic oil port P32b.

[A-2-1-3] Piston 35
The piston 35 of the hydraulic drive unit 30 is configured to slide along the axial direction of the operating rod 31 in the internal space C32 of the cylinder 32 due to the action of hydraulic oil.

Specifically, when the piston 35 opens the steam valve portion 10, in the hydraulic circuit portion 50, hydraulic fluid is supplied to the load side oil chamber C32a and hydraulic fluid is discharged from the anti-load side oil chamber C32b. As a result, the piston 35 moves away from the steam valve portion 10 side. When the steam valve portion 10 is closed, the piston 35 is closed by supplying hydraulic oil to the non-load side oil chamber C32b and discharging the hydraulic oil from the load side oil chamber C32a in the hydraulic circuit portion 50. moves closer to the steam valve unit 10 side. When the opening of the steam valve portion 10 is maintained, the pressure in the load-side oil chamber C32a and the pressure in the anti-load-side oil chamber C32b are adjusted so that the piston 35 is stopped.

[A-2-1-4] Closing spring 82
In addition to the above, the hydraulic drive unit 30 is provided with a closing spring 82 . The closing spring 82 is, for example, a coil spring in which a metal wire is spirally wound, and is accommodated inside a spring box portion 81 installed between the valve box portion 11 and the cylinder 32 . The closing spring 82 is installed so that the operating rod 31 penetrates inside. The closing spring 82 is configured to be expanded and contracted by the operating rod 31 operated by the piston 35 .

Here, the closing spring 82 is interposed between the spring receiver 31R fixed to the operating rod 31 and the fixed plate portion 83 facing the spring receiver 31R in the spring box portion 81. As shown in FIG. The closing spring 82 is deformed along the axis of the operating rod 31 by changing the position of the spring bearing 31R as the operating rod 31 moves. The closing spring 82 urges the steam valve section 10 in the closing direction by pressing the spring bearing 31R toward the steam valve section 10 side.

[A-2-2] Hydraulic circuit unit 50
In the steam turbine valve drive device 20, the hydraulic circuit section 50 includes a two-way pump 51, an oil storage section 52, a control oil check valve V52a, a control oil check valve V52b, a quick closing dump valve V53, and a quick closing electromagnetic valve V54. , an emergency oil check valve V56b, and an emergency oil check valve V56b, and each part is connected via an oil passage through which hydraulic oil flows.

[A-2-2-1] Two-way pump 51
In the hydraulic circuit section 50, the two-way pump 51 supplies hydraulic oil to the load side oil chamber C32a to perform a normal opening operation of the steam valve section 10, and also supplies hydraulic oil to the non-load side oil chamber C32b. The steam valve unit 10 is configured to perform a normal closing operation by supplying it.

Specifically, the bidirectional pump 51 is, for example, a reversible pump, and the drive shaft rotates in the forward direction and the reverse direction, respectively, so that the first pump port P51a or the second pump port P51b It is configured to discharge hydraulic oil.

In the two-way pump 51, the first pump port P51a is connected to the first hydraulic fluid port P32a of the cylinder 32 via an oil passage L51a (load side opening control oil passage). The bidirectional pump 51 discharges hydraulic fluid from the first pump port P51a to supply the hydraulic fluid from the first hydraulic fluid port P32a to the load side oil chamber C32a via the oil passage L51a. A connecting portion J1a, a connecting portion J2a, and a connecting portion J3a are sequentially provided in the oil passage L51a from the two-way pump 51 side toward the cylinder 32 side.

On the other hand, the second pump port P51b of the two-way pump 51 is connected to the second hydraulic fluid port P32b of the cylinder 32 via an oil passage L51b (anti-load side opening control oil passage). The bidirectional pump 51 discharges hydraulic fluid from the second pump port P51b to supply hydraulic fluid from the second hydraulic fluid port P32b to the non-load side oil chamber C32b via the oil passage L51b. A connecting portion J1b, a connecting portion J2b, and a connecting portion J3b are sequentially provided in the oil passage L51b from the two-way pump 51 side toward the cylinder 32 side.

In addition, the bidirectional pump 51 is configured such that hydraulic oil leaked from the bidirectional pump 51 flows out to the oil reservoir 52 as drain oil through the oil passage L51c (drain oil passage). A connection portion J4 is provided in the oil passage L51c.

Here, the bidirectional pump 51 is connected to a drive shaft of a servomotor 512, and the servomotor 512 changes the direction of rotation of the driveshaft, thereby changing the direction in which the bidirectional pump 51 discharges hydraulic oil. Along with this, the servomotor 512 is configured to change the rotation speed of the drive shaft, thereby changing the amount of hydraulic oil discharged by the bidirectional pump 51 .

The servo motor 512 operates based on control signals output from the servo driver 514 . The servo driver 514 receives actual rotation speed data of the servo motor 512 as a detection signal from a resolver (not shown), which is a rotation speed detector. In addition, the servo driver 514 receives a rotation speed command from the control device 70 as a control signal. The servo driver 514 drives the servo motor 512 based on the actual rotation speed data input from the resolver 513 and the rotation speed command input from the control device 70 . Here, the servo driver 514 controls the operation of the servomotor 512 so that the rotation speed of the servomotor 512 becomes the rotation speed corresponding to the rotation speed command. That is, in the steam valve section 10, feedback control is performed so that the preset required opening degree and the opening degree detected for the steam valve section 10 by the opening degree detector 38 match.

[A-2-2-2] Oil storage unit 52
The oil reservoir 52 is, for example, an accumulator that stores hydraulic oil therein. Here, hydraulic oil stored in the oil reservoir 52 is connected to an oil passage L51a via an oil passage L52 (oil reservoir oil passage), and an oil passage L52a (load-side control oil passage). It is configured to be supplied to each of the oil passages L52b (anti-load side control oil passages) connected to the oil passage L51b.

Specifically, the oil reservoir 52 has an oil supply/drainage port at the bottom to which the oil passage L52 is connected. A connection portion J5 and a connection portion J6 are provided in the oil passage L52 from the oil storage portion 52 side. One end of the oil passage L51c is connected to the connection portion J5 of the oil passage L52. One end of the oil passage L52a and one end of the oil passage L52b are connected to the connection portion J6 of the oil passage L52. The other end of the oil passage L52a is connected to the connection portion J1a of the oil passage L51a, and the other end of the oil passage L52b is connected to the connection portion J1b of the oil passage L51b.

The oil reservoir 52 is connected to the oil passage L51a via the oil passage L52 when hydraulic oil leaks from the two-way pump 51, the rapid closing dump valve V53, and the rapid closing electromagnetic valve V54. Hydraulic oil can be supplied to each of the passage L52a and the oil passage L52b connected to the oil passage L51b.

[A-2-2-3] Control oil check valve V52a, control oil check valve V52b
The control oil check valve V52a (first control oil check valve) is installed in the oil passage L52a. The control oil check valve V52a is configured so that hydraulic oil flows from the oil storage portion 52 side to the oil passage L51a side in the oil passage L52a, but hydraulic oil does not flow from the oil passage L51a side to the oil storage portion 52 side. It is

On the other hand, the control oil check valve V52b (second control oil check valve) is installed in the oil passage L52b. The control oil check valve V52b is configured so that hydraulic oil flows from the oil storage portion 52 side to the oil passage L51b side in the oil passage L52b, but hydraulic oil does not flow from the oil passage L51b side to the oil storage portion 52 side. It is

[A-2-2-4] Rapid closing dump valve V53
The rapid closing dump valve V53 is installed in an oil passage L53 (rapid closing oil passage) having both ends connected to a connection portion J3a of the oil passage L51a and a connection portion J3b of the oil passage L51b.

In the oil passage L53, a connection portion J7 is provided between the rapid closing dump valve V53 and the connection portion J3a of the oil passage L51a. Between the connecting portion J7 of the oil passage L53 and the third hydraulic oil port P32c of the cylinder 32, an oil passage L53a (rapid closing oil passage) is connected. An orifice S53a is provided in the oil passage L53a.

The quick-closing dump valve V53 is provided with an A port, a B port, and a pilot port. It is configured to be in a communication state or a cut-off state between them.

Although the details will be described later, when the steam valve unit 10 performs the normal opening operation and the normal closing operation of the quick closing dump valve V53, the connection between the A port and the B port is cut off. closed. On the other hand, when the steam valve unit 10 is to be rapidly closed, the rapid closing dump valve V53 is opened while the A port and the B port are in communication.

[A-2-2-5] Rapid closing solenoid valve V54
The rapid closing solenoid valve V54 is installed in an oil passage L54 (solenoid valve installation oil passage) having both ends connected to the connection portion J4 of the oil passage L51c and the pilot port of the rapid closing dump valve V53.

The rapid closing solenoid valve V54 is provided with an A port, a P port and a T port. The rapid closing solenoid valve V54 communicates between the A port and the P port when the solenoid portion is in an excited state, and communicates between the T port and the A port when the solenoid portion is in a non-excited state. are configured to be in communication with each other.

Although the details will be described later, the rapid closing solenoid valve V54 is in an energized state when the steam valve unit 10 performs a normal opening operation and a normal closing operation, and the A port and the P port are in communication. Then, the oil passage L54 is cut off. As a result, the oil passage L56c, which is connected to the P port of the quick-closing solenoid valve V54 and has the orifice S56c installed therein, communicates with the portion of the oil passage L54 located on the quick-closing dump valve V53 side. become. On the other hand, when the steam valve portion 10 is to be rapidly closed, the rapid closing solenoid valve V54 is in a non-excited state, the T port and the A port are communicated, and the oil passage L54 is closed. be in communication.

[A-2-2-6] Emergency oil check valve V56a, emergency oil check valve V56b
The emergency oil check valve V56a (first emergency oil check valve) is installed in the oil passage L56a. One end of the oil passage L56a is connected to the oil passage L56c at the connection portion J8, and the other end is connected to the oil passage L51a at the connection portion J2a. The emergency oil check valve V56a is configured so that hydraulic oil flows from the connecting portion J2a side to the connecting portion J8 side in the oil passage L56a, but hydraulic oil does not flow from the connecting portion J8 side to the connecting portion J2a side. It is

On the other hand, the emergency oil check valve V56b (second emergency oil check valve) is installed in the oil passage L56b. One end of the oil passage L56b is connected to the oil passage L56c at the connection portion J8, and the other end is connected to the oil passage L51b at the connection portion J2b. The emergency oil check valve V56b is configured so that hydraulic oil flows from the connecting portion J2b side to the connecting portion J8 side in the oil passage L56b, but hydraulic oil does not flow from the connecting portion J8 side to the connecting portion J2b side. It is

[A-3] Control device 70
The control device 70 includes an arithmetic unit (not shown) and a memory device (not shown), and the arithmetic unit performs arithmetic processing using a program stored in the memory device to control each part. A detection signal obtained by detecting the state of each part is input to the control device 70 . In addition, the control device 70 receives, for example, an operation command signal input by an operator to an operation device (not shown). The control device 70 controls the operation of the steam valve section 10 by driving the hydraulic drive section 30 in the hydraulic circuit section 50 based on various signals that are input.

[B] Operation From the following, for the above steam valve unit 10, when performing a normal opening operation (Case 1), when performing a normal closing operation (Case 2), and when performing a sudden closing operation (Case 3) ) will be explained sequentially.

[B-1] When performing normal opening operation (Case 1)
First, a case (Case 1) in which the steam turbine valve driving device 20 performs a normal opening operation of the steam valve unit 10 will be described with reference to FIG. In FIG. 2 , solid line arrows indicate main flows of hydraulic oil for opening the steam valve portion 10, and broken line arrows indicate main flows of hydraulic oil for closing the quick-closing dump valve V53. ing.

When the steam valve unit 10 performs a normal opening operation, the control device 70 operates the servo motor 512 using the servo driver 514 so that the two-way pump 51 discharges hydraulic oil from the first pump port P51a.

Specifically, the hydraulic fluid flows into the second pump port P51b of the two-way pump 51 from the second hydraulic fluid port P32b of the anti-load side oil chamber C32b of the cylinder 32 . Along with this, when hydraulic oil leaks, the hydraulic oil flows from the oil reservoir 52 into the second pump port P51b of the two-way pump 51 via the control oil check valve V52b. Then, the bidirectional pump 51 discharges the hydraulic fluid that has flowed into the second pump port P51b from the first pump port P51a. Hydraulic oil discharged from the first pump port P51a flows into the load side oil chamber C32a of the cylinder 32 . As a result, in the internal space C32 of the cylinder 32, the pressure in the load side oil chamber C32a becomes higher than the pressure in the anti-load side oil chamber C32b, and the piston 35 moves from the side of the load side oil chamber C32a to the side of the anti-load side oil chamber C32b. move to the side of As a result, in the steam valve portion 10, the valve element 15 moves, and the distance between the valve seat 13 and the valve element 15 increases, thereby increasing the opening.

As described above, when the normal opening operation is performed, in the hydraulic circuit unit 50 of the present embodiment, the rapid closing solenoid valve V54 is in an excited state, and the A port and the P port are communicated to The path L54 is blocked. As a result, the oil passage L56c connected to the P port of the quick closing solenoid valve V54 and the portion of the oil passage L54 located on the quick closing dump valve V53 side are in a state of communication.

When the normal opening operation is started, in a state where the pressure in the anti-load side opening control oil passage L51b is higher than the pressure in the load side opening control oil passage L51a, the hydraulic oil is forced to the anti-load side opening From the control oil passage L51b, the oil passes through the emergency oil check valve V56b between the P port and the A port of the quick closing electromagnetic valve V54, and is supplied to the pilot oil chamber P53 of the quick closing dump valve V53. As a result, the rapid closing dump valve V53 is kept closed.

After that, when the pressure of the load side opening control oil passage L51a becomes higher than the pressure of the non-load side opening control oil passage L51b, the hydraulic oil is discharged from the load side opening control oil passage L51a. It passes between the P port and the A port of the rapid closing solenoid valve V54 via the oil check valve V56a, and is supplied to the pilot oil chamber P53 of the rapid closing dump valve V53. As a result, the quick-closing dump valve V53 maintains the closed state in the same manner as when the normal opening operation was started.

[B-2] Normal closing operation (Case 2)
Next, a case (Case 2) where the steam turbine valve driving device 20 performs a normal closing operation of the steam valve unit 10 will be described with reference to FIG. In FIG. 3 , the flow of hydraulic oil for closing the steam valve portion 10 is indicated by solid arrows, and the flow of hydraulic oil for closing the quick closing dump valve V53 is indicated by broken arrows.

When the steam valve unit 10 performs a normal closing operation, the control device 70 operates the servo motor 512 using the servo driver 514 so that the two-way pump 51 discharges hydraulic oil from the second pump port P51b.

Specifically, the hydraulic oil flows from the oil reservoir 52 into the first pump port P51a of the two-way pump 51 via the control oil check valve V52a. Along with this, hydraulic fluid flows from the first hydraulic fluid port P32a of the load-side oil chamber C32a of the cylinder 32 into the first pump port P51a of the two-way pump 51 . The bidirectional pump 51 then discharges the hydraulic oil that has flowed into the first pump port P51a from the second pump port P51b. The hydraulic oil discharged from the second pump port P51b flows into the anti-load side oil chamber C32b of the cylinder 32. As a result, in the internal space C32 of the cylinder 32, the pressure in the non-load side oil chamber C32b becomes higher than the pressure in the load side oil chamber C32a, and the piston 35 moves from the side of the non-load side oil chamber C32b to the load side oil chamber C32a. move to the side of As a result, in the steam valve portion 10, the valve body 15 moves, and the distance between the valve seat 13 and the valve body 15 narrows, thereby reducing the opening degree.

When the normal closing operation is performed, the rapid closing solenoid valve V54 is in an excited state, and the A port and the P port are communicated, and the oil passage L54 is cut off, as in the case of the normal opening operation. state. As a result, the oil passage L56c connected to the P port of the quick closing solenoid valve V54 and the portion of the oil passage L54 located on the quick closing dump valve V53 side are in a state of communication.

When the normal closing operation is started, when the pressure in the load side opening control oil passage L51a is higher than the pressure in the non-load side opening control oil passage L51b, the hydraulic oil is used for the load side opening control. The emergency oil passage L51a passes through the emergency oil check valve V56a between the P port and the A port of the quick closing solenoid valve V54, and is supplied to the pilot oil chamber P53 of the quick closing dump valve V53. As a result, the rapid closing dump valve V53 is kept closed.

Thereafter, when the pressure in the anti-load-side opening control oil passage L51b becomes higher than the pressure in the load-side opening control oil passage L51a, the hydraulic oil is discharged from the anti-load-side opening control oil passage L51b. The oil passes through the emergency oil check valve V56b between the P port and the A port of the rapid closing solenoid valve V54, and is supplied to the pilot oil chamber P53 of the rapid closing dump valve V53. As a result, the quick-closing dump valve V53 maintains the closed state in the same manner as when the normal closing operation was started.

[B-3] When performing sudden closing operation (Case 3)
Next, a case (Case 3) in which the steam turbine valve driving device 20 performs a rapid closing operation of the steam valve unit 10 will be described with reference to FIG. That is, a case will be described in which the steam valve section 10 is rapidly closed at a speed higher than the speed at which the steam valve section 10 is closed in a normal closing operation. In FIG. 4, the flow of hydraulic fluid for rapidly closing the steam valve portion 10 is indicated by solid arrows, and the flow of hydraulic fluid for opening the quick closing dump valve V53 is indicated by broken arrows. .

The rapid closing operation is performed by the control device 70 controlling the operation of each part that constitutes the rapid closing mechanism, for example, when an abnormality occurs in the steam turbine power generation equipment. By executing the rapid closing operation, the flow of steam supplied as a working medium to the steam turbine is interrupted, and the steam turbine stops.

When the quick closing operation is performed, the quick closing solenoid valve V54 is changed from the excited state to the non-excited state based on the control signal from the control device 70, unlike the case of the normal closing operation. That is, the rapid closing solenoid valve V54 is in a non-excited state, the T port and the A port are communicated, and the oil passage L54 is in a communicated state. As a result, in the pilot oil chamber P53 of the rapid closing dump valve V53, hydraulic oil is discharged to the oil reservoir 52 via the rapid closing electromagnetic valve V54.

As a result, the quick-closing dump valve V53 is in a state in which the spring inside the pilot oil chamber P53 is compressed, the A port and the B port are communicated, and the oil passage L53 is opened. Become. In other words, the load-side oil chamber C32a and the anti-load-side oil chamber C32b communicate with each other through the oil passage L53 in which the quick-closing dump valve V53 is installed. Therefore, due to the action of the closing spring 82 and the action of the steam flowing through the steam valve portion 10, hydraulic oil rapidly flows from the load side oil chamber C32a to the non-load side oil chamber C32b via the oil passage L53.

In this embodiment, hydraulic fluid discharged from the first hydraulic fluid port P32a of the load-side oil chamber C32a flows into the oil passage L53 via the connecting portion J3a of the oil passage L51a. Along with this, the hydraulic oil discharged from the third hydraulic oil port P32c of the load-side oil chamber C32a flows through the oil passage L53a provided with the orifice S53a and then flows into the oil passage L53 from the connection J7.

As a result, in the internal space C32 of the cylinder 32, the piston 35 rapidly moves from the anti-load side oil chamber C32b side to the load side oil chamber C32a side. As a result, all of the steam valve sections 10 are rapidly closed. For example, the diameter of the oil passage L53 and the diameter of the passage through which hydraulic oil flows between the A port and the B port of the quick closing dump valve V53 are set to the opposite load side opening control oil passage L51b and the load side By increasing the diameter of the opening control oil passage L51a, it is possible to execute the rapid closing operation at a sufficiently high speed. Further, by adjusting the diameter of the orifice S53a installed in the oil passage L53a, the rapid closing speed can be adjusted appropriately. If the rapid closing speed can be adjusted without the orifice S53a, the oil passage L53a provided with the orifice S53a is unnecessary.

[C] Summary As described above, in the present embodiment, when the steam valve unit 10 performs the rapid closing operation, the hydraulic oil flows from the pilot oil chamber P53 of the rapid closing dump valve V53 to the rapid closing solenoid valve V54. The rapid closing dump valve V53 is opened by being discharged to the oil storage portion 52 via. Hydraulic oil flows from the load-side oil chamber C32a to the non-load-side oil chamber C32b via the oil passage L53 in which the quick closing dump valve V53 is installed. As a result, the steam valve portion 10 is quickly closed. Thus, in the present embodiment, the rapid closing operation of the steam valve section 10 is performed by opening the rapid closing dump valve V53 using the rapid closing solenoid valve V54. Therefore, in this embodiment, the rapid closing operation can be performed at a sufficiently high speed without increasing the size of the rapid closing solenoid valve V54.

In this embodiment, a control oil check valve V52a is installed in the oil passage L52a, and a control oil check valve V52b is installed in the oil passage L52b. Therefore, due to the action of the control oil check valve V52a and the control oil check valve V52b, hydraulic oil does not flow into the oil reservoir 52 from the load side oil chamber C32a and the anti-load side oil chamber C32b. As a result, the hydraulic pressure of the oil storage portion 52 does not fluctuate according to the opening degree of the steam valve portion 10 and is held at a constant value. In the present embodiment, as described above, when the rapid closing operation is performed, hydraulic oil is discharged from the pilot oil chamber P53 of the rapid closing dump valve V53 to the oil reservoir 52 via the rapid closing solenoid valve V54. Since the hydraulic pressure of the oil reservoir 52 is constant, the working oil is discharged to the oil reservoir 52 accurately. As a result, in this embodiment, the quick closing operation can be performed with high reliability.

[D] Release operation (reset operation)]
Note that, in the present embodiment, for example, when performing a cancellation operation (reset operation) for canceling the rapid closing operation of the steam valve unit 10 at turbine start-up, it is the same as when performing the normal opening operation and the normal closing operation. Then, the two-way pump 51 is driven with the rapid closing solenoid valve V54 returned to the excited state. As a result, hydraulic oil is supplied as emergency oil to the pilot oil chamber P53 of the rapid closing dump valve V53 to close the rapid closing dump valve V53. In the present embodiment, hydraulic oil can be supplied to the pilot oil chamber P53 of the quick-closing dump valve V53 from each of the load side opening control oil passage L51a and the non-load side opening control oil passage L51b.

However, when hydraulic oil is supplied as emergency oil from the load-side opening control oil passage L51a to the pilot oil chamber P53 of the quick-closing dump valve V53, the steam valve portion 10 is performed, the control of the steam valve portion 10 and the turbine may become unstable when the turbine is started. On the other hand, when hydraulic oil is supplied as emergency oil from the anti-load side opening control oil passage L51b to the pilot oil chamber P53 of the quick-closing dump valve V53, when the quick-closing dump valve V53 closes, Since the steam valve unit 10 maintains the fully closed state, it is possible to stably control the steam valve unit 10 and the turbine when starting the turbine.

[E] Modification

A modification of the above embodiment will be described with reference to FIG. FIG. 5 shows main parts of the steam valve portion 10 and the hydraulic drive portion 30, and the hydraulic circuit portion 50 is omitted from the illustration.

FIG. 1 shows the "React to Open" type in which the opening operation of the steam valve portion 10 is executed by moving the valve stem 14 and the operating rod 31 closer to the cylinder 32 side, but this is not the only case. do not have. As shown in FIG. 5, in the "Extend to Open" type in which the opening operation of the steam valve portion 10 is executed by moving the valve stem 14 and the operating rod 31 away from the cylinder 32 side, Each part may be configured.

<Second embodiment>
[A] Configuration In the second embodiment, main parts of the steam valve unit 10 and the steam turbine valve driving device 20 that constitute the steam turbine power generation facility will be described with reference to FIG. 6 . Similar to FIG. 1, FIG. 6 shows how the steam turbine valve drive device 20 performs the normal opening operation and the normal closing operation of the steam valve unit 10. As shown in FIG.

As shown in FIG. 6, unlike the first embodiment, this embodiment has two rapid closing dump valves V53, V53_2 and two rapid closing electromagnetic valves V54, V54_2. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

[A-1] Rapid closing dump valve V53_2
Of the two rapid closing dump valves V53 and V53_2, the rapid closing dump valve V53_2 is installed in the same manner as the rapid closing dump valve V53 in the first embodiment.

Specifically, the rapid closing dump valve V53_2 is installed in an oil passage L53_2 (dump valve installation oil passage) having both ends connected to the connection portion J7_2 of the oil passage L53 and the connection portion J3b_2 of the oil passage L51b. ing. The rapid closing dump valve V53_2 is provided with an A port, a B port, and a pilot port. It is configured to be in a communication state or a cut-off state between them.

[A-2] Rapid closing solenoid valve V54_2
Further, of the two quick closing solenoid valves V54 and V54_2, the quick closing solenoid valve V54_2 is installed in the same manner as the quick closing solenoid valve V54 in the first embodiment.

Specifically, the rapid closing solenoid valve V54_2 is connected to the oil passage L54_2 (solenoid valve installed oil passage) having both ends connected to the connecting portion J5 of the oil passage L52 and the pilot port of the rapid closing dump valve V53_2. is set up. The rapid closing solenoid valve V54_2 is provided with an A port, a P port and a T port. The rapid closing solenoid valve V54_2 communicates between the A port and the P port when the solenoid portion is in an excited state, and communicates between the T port and the A port when the solenoid portion is in a non-excited state. are configured to be in communication with each other.

[B] Operation The quick-closing mechanism including the quick-closing dump valve V53_2 and the quick-closing solenoid valve V54_2 causes an abnormality in another quick-closing mechanism including, for example, the quick-closing dump valve V53 and the quick-closing solenoid valve V54. It is used to perform a quick closing operation when the That is, when performing the quick closing operation, the quick closing solenoid valve V54_2 is in a non-excited state, the T port and the A port are communicated, and the oil passage L54_2 is in a communicated state. Then, the rapid closing dump valve V53_2 is opened when the A port and the B port are communicated with each other. As a result, in the internal space C32 of the cylinder 32, the piston 35 rapidly moves from the load side oil chamber C32a side to the anti-load side oil chamber C32b side. As a result, all of the steam valve sections 10 are rapidly closed.

[C] Summary As described above, in the present embodiment, in addition to the quick-closing mechanism including the quick-closing dump valve V53 and the quick-closing solenoid valve V54, the quick-closing dump valve V53_2 and the quick-closing solenoid valve V54_2 are provided. Equipped with a quick closing mechanism. Therefore, even if one of the two quick closing mechanisms malfunctions, the other can be used to perform the quick closing operation. Therefore, in the present embodiment, the rapid closing operation can be performed more reliably, and reliability can be improved.

<Third Embodiment>
[A] Configuration The rapid closing solenoid valve V54 in the second embodiment will be described with reference to FIG. As in FIG. 1, FIG. 7 shows how the steam turbine valve drive device 20 performs the normal opening operation and the normal closing operation of the steam valve unit 10 (see FIG. 1).

As shown in FIG. 7, in this embodiment, the configuration of a part of the rapid closing solenoid valve V54 is different from that in the first embodiment (see FIG. 1). Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

As shown in FIG. 7, the rapid closing solenoid valve V54 of the present embodiment has two solenoid portions, unlike the case of the first embodiment (see FIG. 1). In the present embodiment, when the rapid closing solenoid valve V54 executes the rapid closing operation, all of the two solenoid portions are in the non-excited state, and the rapid closing dump valve V53 is opened from the closed state. (See FIG. 1).

[B] Summary For this reason, in the present embodiment, even if, for example, the wire for excitation in one of the two solenoid units is broken, the quick closing operation is not executed, so the operation is possible only in emergencies. In this case, it is possible to prevent the turbine from stopping. As a result, in the present embodiment, it is possible to prevent problems such as loss of power generation opportunities and disturbances in the power system from occurring.

<Fourth Embodiment>
[A] Configuration In the fourth embodiment, a main part of the steam turbine valve drive device 20 that constitutes the steam turbine power generation facility will be described with reference to FIG. 8 .

As shown in FIG. 8, in this embodiment, unlike the first embodiment, a filter 91 (first filter) and a filter bypass check valve V91 (first filter bypass check valve) are provided. Further, in this embodiment, unlike the case of the first embodiment, a filter 92 (second filter) and a filter bypass check valve V92 (second filter bypass check valve) are provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

[A-1] Filter 91
The filter 91 is provided in an oil passage L51c (drain oil passage) through which hydraulic oil leaked from the bidirectional pump 51 flows to the oil storage portion 52 as drain oil.

[A-2] Filter bypass check valve V91
In the oil passage L51c, a connection portion J91a and a connection portion J91b are provided so as to sandwich the filter 91 therebetween. and connected to. An oil passage L91 that bypasses the filter 91 is provided with a filter bypass check valve V91. The filter bypass check valve V91 prevents the hydraulic oil from flowing from the oil reservoir 52 side to the two-way pump 51 side, although the hydraulic oil flows from the bidirectional pump 51 side to the oil reservoir 52 side in the oil passage L91. It is configured. Therefore, when the filter 91 is clogged by foreign matter caught, the hydraulic oil flows to the oil reservoir 52 side through the oil passage L91 that bypasses the filter 91 .

[A-3] Filter 92
Filter 92 is provided in oil passage L52 through which hydraulic oil stored in oil storage portion 52 flows to oil passages L51a and L51b through oil passages L52a and L52b, respectively.

[A-2] Filter bypass check valve V92
In the oil passage L52, a connection portion J92a and a connection portion J92b are provided so as to sandwich the filter 92, and both ends of the oil passage L92 (filter bypass oil passage) bypassing the filter 92 are connected to the connection portion J92a and the connection portion J92b. and connected to. An oil passage L92 that bypasses the filter 92 is provided with a filter bypass check valve V92. The filter bypass check valve V92 prevents hydraulic oil from flowing from the oil reservoir 52 side to the bidirectional pump 51 side in the oil passage L92, but prevents the hydraulic oil from flowing from the bidirectional pump 51 side to the oil reservoir 52 side. is configured to Therefore, when the filter 92 is clogged by foreign matter caught, the hydraulic oil flows to the bidirectional pump 51 side through the oil passage L92 that bypasses the filter 92 .

[B] Summary As described above, the filter 91 and the filter 92 are provided in this embodiment. Therefore, in the present embodiment, foreign matter such as sludge generated in the hydraulic circuit portion 50 is removed from the working oil by the filters 91 and 92, and the cleanliness of the working oil can be maintained in a suitable state. As a result, in this embodiment, it is possible to prevent the performance of the two-way pump 51 and the quick closing solenoid valve V54 from deteriorating due to foreign matter such as sludge.

<Fifth Embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 in the fifth embodiment will be described with reference to FIG. 9 .

As shown in FIG. 9, in this embodiment, unlike the first embodiment, a load side relief valve V93a and an anti-load side relief valve V93b are provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

[A-1] Load side relief valve V93a
The load side relief valve V93a is installed in an oil passage L93a (load side relief valve installation oil passage L93a). The oil passage L93a has one end connected to the connection portion J54a of the oil passage L54, and the other end connected to the connection portion J93a of the oil passage L51a.

[A-2] Load side relief valve V93a
The anti-load side relief valve V93b is installed in an oil passage L93b (an anti-load side relief valve installation oil passage). The oil passage L93b has one end connected to the connection portion J5 of the oil passage L52 and the other end connected to the connection portion J93b of the oil passage L51b.

[B] Operation In the present embodiment, when the pressure in the oil passage L51a (load-side opening control oil passage) exceeds a predetermined value, the load-side relief valve V93a changes from the closed state to the open state. . As a result, hydraulic oil flows from the oil passage L51a to the oil reservoir 52 via the load-side relief valve V93a of the oil passage L93a.

On the other hand, when the pressure of the oil passage L51b (anti-load side opening control oil passage) exceeds a predetermined value, the anti-load side relief valve V93b changes from the closed state to the open state. As a result, hydraulic oil flows from the oil passage L51b to the oil reservoir 52 via the non-load side relief valve V93b of the oil passage L93b.

For example, when an abnormality occurs in the servo driver 514 (see FIG. 2) and the rotation speed control is not properly executed in the servo motor 512, the pressure in the oil passage L51a or the pressure in the oil passage L51b reaches a predetermined value. may exceed. In such a case, the load-side relief valve V93a or the anti-load-side relief valve V93b is opened, and the pressure in the oil passage L51a or the pressure in the oil passage L51b returns to a predetermined proper value.

[C] Summary Therefore, in the present embodiment, the hydraulic circuit section 50 of the steam turbine valve drive device 20 can be appropriately protected.

<Sixth Embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 in the sixth embodiment will be described with reference to FIG. 10 .

As shown in FIG. 10, in this embodiment, unlike the first embodiment, a load side pressure detector 94a and an anti-load side pressure detector 94b are provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

[A-1] Load side pressure detector 94a
The load side pressure detector 94a is installed to detect the pressure of hydraulic fluid in the load side opening control oil passage L51a. Here, a load side pressure detector 94a is provided so as to detect the pressure between the connecting portion J3a and the first hydraulic fluid port P32a in the load side opening control oil passage L51a.

[A-2] Anti-load side pressure detector 94b
The anti-load side pressure detector 94b is installed to detect the pressure of hydraulic fluid in the anti-load side opening control oil passage L51b. Here, an anti-load side pressure detector 94b is provided to detect the pressure between the connecting portion J3b and the third hydraulic fluid port P32b in the anti-load side opening control oil passage L51b.

[B] Operation

In this embodiment, the controller 70 controls the operation of the servomotor 512 based on the pressure detected by the load side pressure detector 94a and the pressure detected by the anti-load side pressure detector 94b. Here, control is performed so as to prevent the hydraulic oil pressure from exceeding a specified value.

For example, if the two-way pump 51 discharges hydraulic oil when the valve stem 14 and the operating rod 31 cannot move due to the mechanical end, the load side pressure detector 94a or the anti-load side pressure detector 94b The pressure detected at may increase. Therefore, when the pressure detected by the load-side pressure detector 94a or the anti-load-side pressure detector 94b exceeds a set value lower than the specified value, the control device 70 limits the rotation of the servomotor 512, The two-way pump 51 stops discharging hydraulic oil. Thereby, it is possible to prevent the pressure of the hydraulic oil from exceeding the specified value.

[C] Summary Therefore, in the present embodiment, the hydraulic circuit section 50 of the steam turbine valve drive device 20 can be appropriately protected.

<Seventh Embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 in the seventh embodiment will be described with reference to FIG. 11 .

As shown in FIG. 11, in this embodiment, unlike the case of the first embodiment, an oil supply port P95 is provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

The oil supply port P95 is provided to supply hydraulic oil to the oil reservoir 52 . Here, an oil supply port P95 is provided at the other end of the oil passage L95, one end of which is connected to the connection portion J5. A check valve V95 is installed in the oil passage L95. The check valve V95 is configured so that hydraulic fluid flows from the oil supply port P95 side to the connection portion J5 side in the oil passage L95, but hydraulic fluid does not flow from the connection portion J5 side to the oil supply port P95 side. there is

[B] Summary Therefore, in the present embodiment, since the hydraulic oil can be easily replenished in the oil storage section 52, the opening of the steam valve section 10 can be appropriately controlled.

In particular, the valve drive device of the present embodiment is of a type equipped with a hydraulic source, and in general, the hydraulic system is divided for each steam valve unit 10 . Therefore, the amount of oil filled in each hydraulic device is extremely small compared to a conventional hydraulic system (a system that supplies control oil from a hydraulic pressure generator to the hydraulic device of each steam valve through a control oil pipe). Therefore, in this embodiment, even if a small amount of hydraulic oil leaks, there is a possibility that the controllability will be affected. However, in the present embodiment, as described above, hydraulic oil can be easily replenished, so that it is less likely to be affected by leakage of hydraulic oil. In this embodiment, since the oil pressure is kept constant in the oil passage connected to the oil reservoir 52, the oil can be filled regardless of the degree of opening of the steam valve portion 10. FIG.

<Eighth embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 in the eighth embodiment will be described with reference to FIG. 12 .

As shown in FIG. 12, in this embodiment, unlike the case of the first embodiment, a cooling unit 96 is provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

A cooling unit 96 is installed to cool the servomotor 512 . For example, the cooling unit 96 includes a cooling fan and performs cooling with cooling air from the cooling fan.

[B] Summary For this reason, in the present embodiment, the cooling unit 96 cools the servomotor 512 , so that the heat of the servomotor 512 can prevent the viscosity of the hydraulic oil from decreasing.

For example, in a warm climate, if the temperature of the hydraulic oil rises and the viscosity drops due to the action of the heat of the servomotor 512, the amount of hydraulic oil leakage may increase in the two-way pump 51 and the rapid closing solenoid valve V54. . As a result, the pressure of the working oil in the internal space C32 of the cylinder 32 cannot be accurately controlled, and it may be difficult to accurately control the opening of the steam valve portion 10 . In addition, the temperature of the hydraulic oil may rise and the hydraulic oil may deteriorate. However, in the present embodiment, the viscosity of the hydraulic oil can be brought to an appropriate state, so the occurrence of the above problems can be suppressed. It should be noted that the cooling unit 96 may be composed of something other than a cooling fan, and for example, may use compressed air for operation or a cooling device.

<Ninth Embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 in the ninth embodiment will be described with reference to FIG. 13 .

As shown in FIG. 13, in this embodiment, unlike the case of the first embodiment, a heating unit 97 is provided. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

A heating unit 97 is installed to heat the hydraulic oil. For example, the heating unit 97 includes a heater and heats the hydraulic oil with the heater. In this embodiment, for example, the heating section 97 is configured to heat the hydraulic oil stored in the oil storage section 52 .

[B] Summary Therefore, in the present embodiment, when the viscosity of the hydraulic oil increases, the viscosity of the hydraulic oil can be brought to an appropriate state.

For example, in cold regions, when the temperature of the hydraulic oil drops and the viscosity rises, the hydraulic oil heating unit 97 heats the hydraulic oil to bring the viscosity of the hydraulic oil into an appropriate state. When the viscosity of hydraulic oil increases, the servo motor 512 may not be started in order to protect the bidirectional pump 51 . However, in the present embodiment, the viscosity of the hydraulic oil can be brought to an appropriate state, so the occurrence of the above problems can be suppressed.

<Tenth Embodiment>
[A] Configuration A main part of the hydraulic circuit unit 50 according to the tenth embodiment will be described with reference to FIG. 14 .

As shown in FIG. 14, the present embodiment includes a dynamic braking device 515 and a switch 516 unlike the first embodiment. Except for this point and related points, this embodiment is similar to the above embodiment. Therefore, descriptions of overlapping points will be omitted as appropriate.

The dynamic braking device 515 is configured to generate braking force by short-circuiting the windings of the servomotor 512 .

A switch 516 switches such that the servo motor 512 is electrically connected to either the servo driver 514 or the dynamic braking device 515 .

Specifically, when an abnormality occurs in the servo driver 514 and the rotation speed of the servo motor 512 becomes uncontrollable, the servo motor 512 and Switch 516 is switched so that dynamic brake device 515 is electrically connected. As a result, the dynamic braking device 515 brakes the servomotor 512 and stops the operation of the servomotor 512 .

For example, when an abnormality occurs in the servo driver 514 and the servo motor 512 is disconnected from the rotation speed control (during servo OFF), the servo motor 512 and the two-way pump 51 exceed the allowable rotation speed due to the flow of hydraulic oil. may rotate at a higher number of revolutions. However, in this embodiment, when the rotational speed control of the servo motor 512 is disconnected from the servo driver 514, the servo OFF signal from the servo driver 514 is used as a trigger, and the servo motor 512 and the dynamic brake device 515 are operated. switch 516 is switched so that the . As a result, the servomotor 512 is braked by the braking force of the dynamic brake device 515 .

[B] Summary Therefore, in the present embodiment, it is possible to prevent the rotation speed of the bidirectional pump 51 and the rotation speed of the servo motor 512 from exceeding the allowable rotation speed.

<Others>
While several embodiments of the invention have been described, these embodiments have been presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the scope of the invention described in the claims and equivalents thereof.

DESCRIPTION OF SYMBOLS 10... Steam valve part 11... Valve box part 13... Valve seat 14... Valve stem 15... Valve body 20... Steam turbine valve drive unit 30... Hydraulic drive part 31... Operation rod 32... Cylinder, 35 Piston 38 Opening detector 50 Hydraulic circuit 51 Two-way pump 52 Oil reservoir 70 Control device 81 Spring box 82 Closing spring 83 Fixed plate , 91... Filter (first filter), 92... Filter (second filter), 94a... Load side pressure detector, 94b... Anti-load side pressure detector, 96... Cooling part, 97... Heating part, 311... Coupling , 512...servo motor, 513...resolver, 514...servo driver, 515...dynamic braking device, 516...switch, C32...internal space, C32a...load side oil chamber, C32b...anti-load side oil chamber, F11A...steam, F11B ... steam, J1a... connection part, J1b... connection part, J2a... connection part, J2b... connection part, J3a... connection part, J3b... connection part, J3b_2... connection part, J4... connection part, J5... connection part, J54a... Connection part J6... Connection part J7... Connection part J7_2... Connection part J8... Connection part J91a... Connection part J91b... Connection part J92... Connection part L51a... Oil passage (load side opening control oil oil passage), L51b... Oil passage (anti-load side opening control oil passage), L51c... Oil passage (drain oil passage), L52... Oil passage (oil reservoir oil passage), L52a... Oil passage (load side control oil oil passage), L52b... oil passage (anti-load side control oil passage), L53... oil passage (rapid closing oil passage), L53_2... oil passage (rapid closing oil passage), L53a... oil passage, L54 ... Oil passage L54_2 ... Oil passage L56a ... Oil passage L56b ... Oil passage L56c ... Oil passage L91 ... Oil passage L92 ... Oil passage L93a ... Oil passage (load side relief valve installed oil passage) L93b ... Oil passage Oil passage (anti-load side relief valve installation oil passage), L95... oil passage, P11A... steam inlet, P11B... steam outlet, P32a... first hydraulic oil port, P32b... second hydraulic oil port, P32c... third hydraulic oil Port P51a...First pump port P51b...Second pump port P53...Pilot oil chamber P53_2...Pilot oil chamber P95...Oil supply port S53a...Orifice S56c...Orifice V52a...Control oil check valve V52b ...Control oil check valve V53...Quick closing dump valve V53_2...Quick closing dump valve V54...Quick closing solenoid valve V54_2...Quick closing solenoid valve V56a...Emergency oil check valve V56b...Emergency Oil check valve V91 Filter bypass check valve V92 Filter bypass check valve V93a Load side relief valve V93b Anti-load side relief valve V95 Check valve

Claims (12)

A steam turbine valve driving device for driving a steam valve unit installed in a steam flow path that supplies steam to a steam turbine,
a cylinder that houses a piston provided on an operating rod that operates the steam valve portion and that is partitioned into a load-side oil chamber and an anti-load-side oil chamber by the piston;
Hydraulic oil is supplied to the load-side oil chamber through the load-side opening control oil passage to execute the opening operation of the steam valve portion, and the hydraulic oil is supplied through the non-load-side opening control oil passage. to the non-load side oil chamber to execute the closing operation of the steam valve portion;
an oil reservoir in which hydraulic oil is stored;
It is installed in a sudden closing oil passage connected to each of the load side opening control oil passage and the anti-load side opening control oil passage, and when performing the opening operation and the closing operation, a pilot a quick-closing dump valve configured to be closed when hydraulic oil is supplied to the oil chamber;
a rapid closing solenoid valve provided in a solenoid valve installation oil passage that connects the oil reservoir and the pilot oil chamber;
with
A first control oil check valve is installed in the load side control oil passage connected to the load side opening control oil passage,
A second control oil check valve is installed in the anti-load side control oil passage connected to the anti-load side opening control oil passage,
The first control oil check valve is configured such that hydraulic oil flows from the oil reservoir to the load side opening control oil passage,
The second control oil check valve is configured such that hydraulic oil flows from the oil reservoir to the anti-load side opening control oil passage,
When performing the opening operation and the closing operation, the quick-closing dump valve is operated by energizing the quick-closing solenoid valve and supplying hydraulic oil from the oil reservoir to the pilot oil chamber. be closed and
When the rapid closing operation is performed, the rapid closing dump valve is opened by deenergizing the rapid closing solenoid valve and discharging hydraulic oil from the pilot oil chamber to the oil reservoir. and the hydraulic oil in the load side oil chamber flows to the anti-load side oil chamber via the rapid closing oil passage,
Steam turbine valve drive.
further comprising a closing spring that biases the steam valve portion in a closing direction;
When performing the rapid closing operation, the action of the closing spring causes hydraulic fluid to flow from the load side oil chamber to the non-load side oil chamber via the rapid closing oil passage.
The steam turbine valve drive system of claim 1. When performing the opening operation and the closing operation, hydraulic oil flowing through the load side opening control oil passage is supplied to the pilot oil chamber via the first emergency oil check valve, The hydraulic oil flowing through the side opening control oil passage is supplied to the pilot oil chamber via the second emergency oil check valve,
The steam turbine valve drive system according to claim 1 or 2 . There are a plurality of the quick-closing dump valves and the quick-closing solenoid valves,
A steam turbine valve drive device according to any one of claims 1 to 3 . The quick-closing solenoid valve has a plurality of solenoid portions, and is configured such that the quick-closing dump valve changes to an open state when all of the plurality of solenoid portions are in a non-excited state.
A steam turbine valve drive device according to any one of claims 1 to 4 . a drain oil passage through which hydraulic oil leaked from the bidirectional pump flows to the oil reservoir as drain oil,
The drain oil passage is provided with a first filter,
A steam turbine valve drive device according to any one of claims 1 to 5 . an oil storage section oil passage that supplies hydraulic oil stored in the oil storage section to the load side opening control oil passage and the non-load side opening control oil passage,
A second filter is provided in the oil reservoir oil passage,
A steam turbine valve drive device according to any one of claims 1 to 6 . When the pressure of the load-side opening control oil passage exceeds a predetermined value, hydraulic oil flows from the load-side opening control oil passage through the load-side relief valve to the oil reservoir,
When the pressure of the anti-load side opening control oil passage exceeds a predetermined value, hydraulic oil flows from the anti-load side opening control oil passage through the anti-load side relief valve to the oil reservoir. configured as
A steam turbine valve drive device according to any one of claims 1 to 7 . a load side pressure detector that detects the pressure of the load side opening control oil passage;
an anti-load side pressure detector that detects the pressure of the anti-load side opening control oil passage;
Based on the pressure detected by the load side pressure detector and the pressure detected by the anti-load side pressure detector, the operation of a servo motor that drives the bidirectional pump is controlled.
A steam turbine valve drive device according to any one of claims 1 to 8 . a cooling unit that cools the servomotor,
10. The steam turbine valve drive system of claim 9 . a heating unit that heats the hydraulic oil stored in the oil storage unit;
A steam turbine valve drive device according to any one of claims 1 to 10 . a dynamic braking device;
a switch for switching so that the servo motor is electrically connected to either the servo driver or the dynamic brake device,
When an abnormality occurs in the servo driver, the dynamic brake device stops the operation of the servo motor by switching the switch so that the servo motor and the dynamic brake device are electrically connected.
A steam turbine valve drive as claimed in any one of claims 9 to 11 .

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