JP7263218B2 - hydraulic circuit - Google Patents

Description

Embodiments of the present invention relate to hydraulic circuit devices.

2. Description of the Related Art In power plants such as thermal power plants and nuclear power plants, steam turbine systems are equipped with steam valves in order to adjust the flow rate of steam flowing into the inlet of the steam turbine.

[A] Overall Steam Turbine System FIG. 5 is a diagram schematically showing a steam turbine system according to related art.

As shown in FIG. 5 , the steam turbine system has a high pressure turbine 20 , a reheater 30 , an intermediate pressure turbine 40 , a low pressure turbine 50 , a condenser 60 and a generator 70 .

In the steam turbine system, a main steam pipe L10 is provided between a boiler (not shown) and the high pressure turbine 20, and a main steam valve V10 is installed in the main steam pipe L10. A low temperature reheat steam pipe L20 is provided between the high pressure turbine 20 and the reheater 30 .

A high-temperature reheat steam pipe L30 is provided between the reheater 30 and the intermediate pressure turbine 40, and the high-temperature reheat steam pipe L30 includes an intermediate steam stop valve V30a and an intercept valve V30b. They are installed in order from the 30 side to the intermediate pressure turbine 40 side. A crossover pipe L40 is provided between the intermediate pressure turbine 40 and the low pressure turbine 50 .

In the steam turbine system, steam as a working medium flows through the main steam pipe L10 and enters the high pressure turbine 20 via the main steam valve V10. The steam discharged from the high-pressure turbine 20 then flows through the low-temperature reheat steam pipe L20 and flows into the reheater 30 . Then, the steam reheated by the reheater 30 flows through the high temperature reheat steam pipe L30 and flows into the intermediate pressure turbine 40 through the intermediate steam stop valve V30a and the intercept valve V30b in sequence. Steam discharged from the intermediate pressure turbine 40 then flows through the crossover pipe L40 and flows into the low pressure turbine 50 . After that, the steam discharged from the low-pressure turbine 50 is condensed (condensed) in the condenser 60 .

In the steam turbine system described above, the turbine rotors of the high-pressure turbine 20, the intermediate-pressure turbine 40, and the low-pressure turbine 50 are connected to each other, and the steam that has flowed into each part as a working fluid expands and performs work, thereby rotating the turbine rotors. do. The rotation of the turbine rotor drives the generator 70 to generate power.

As shown in FIG. 5, in addition to the above, the steam turbine system controls the control device 100 (turbine high-speed valve controller).

Here, the controller 100 receives a detection signal S71 output by a detector 71 that detects the voltage value or current value of the generator 70 and a detection signal S72 output by a detector 72 that detects an accident in the power transmission system. be done. Along with this, the control device 100 receives the detection signal S31 output from the pressure detector 31 installed on the intermediate pressure turbine 40 side of the intercept valve V30b in the high-temperature reheat steam pipe L30.

Control device 100 is configured to control the operation of intercept valve V30b, for example, by outputting opening command signal S100. Here, when the controller 100 determines that an accident has occurred in the power transmission system, it outputs an opening degree command signal S100 for performing high-speed valve control, and performs high-speed valve control for the intercept valve V30b.

[B] Intermediate steam stop valve V30a, intercept valve V30b
FIG. 6 is a diagram schematically showing an intermediate steam stop valve V30a and an intercept valve V30b in a related art steam turbine system.

As shown in FIG. 6, the intermediate steam stop valve V30a and the intercept valve V30b are butterfly valves, and disk-shaped valve bodies 301a and 301b are installed on valve stems 302a and 302b. The intermediate steam stop valve V30a and the intercept valve V30b are opened and closed by rotating the valve bodies 301a and 301b together with the valve stems 302a and 302b when the driving devices 80a and 80b operate the operating rods 81a and 81b. is configured to do

[C] Drive device 80b, hydraulic circuit device 90J
FIG. 7 is a diagram schematically showing a hydraulic circuit device 90J that operates the driving device 80b using hydraulic oil in a steam turbine system according to related art. Here, the hydraulic circuit device 90J that operates the drive device 80b (see FIG. 6) of the intercept valve V30b will be described.

[C-1] Driving device 80b
As shown in FIG. 7, the driving device 80b is provided with a piston 82b on the operating rod 81b, and the piston 82b is accommodated in the internal space C831 of the cylinder 83b. An internal space C831 of the cylinder 83b is divided into a first oil chamber C831a and a second oil chamber C831b by the piston 82b. The driving device 80b is configured such that the operating rod 81b performs the opening and closing operation of the intercept valve V30b by operating the piston 82b in the internal space C831 of the cylinder 83b by the action of hydraulic oil.

Specifically, when performing the opening operation, the piston 82b moves from the first oil chamber C831a side to the second oil chamber C831b side by supplying hydraulic oil to the first oil chamber C831a. On the other hand, when performing the closing operation, the piston 82b moves from the second oil chamber C831b side to the first oil chamber C831a side by discharging the working oil from the first oil chamber C831a. When the opening is to be maintained, the pressure in the first oil chamber C831a and the pressure in the second oil chamber C831b are adjusted so that the piston 82b is stopped in the internal space C831.

[C-2] Hydraulic circuit device 90J
The hydraulic circuit device 90J comprises a hydraulic circuit including a pump 91, an accumulator 92, a servo valve 93, and an oil tank 96, as shown in FIG. Here, when the hydraulic circuit device 90J receives an opening degree command signal S100 for performing high-speed valve control from the control device 100, the hydraulic circuit device 90J controls the operation of each part to drive the drive device 80b, so that the intercept valve V30b controls the behavior of

[C-2-1] Pump 91
In the hydraulic circuit device 90J, the pump 91 is connected to the servo valve 93 via the oil passage L91 so that pressurized hydraulic oil is supplied from the discharge port to the servo valve 93 via the oil passage L91. It is configured. Here, a connecting portion J91 is provided in the oil passage L91.

[C-2-2] Accumulator 92
The accumulator 92 is provided to prevent pulsation of the hydraulic circuit and compensate for the shortage of hydraulic oil supplied from the pump 91 to the driving device 80b. The accumulator 92 stores working oil inside, and the stored working oil is configured to flow to the oil passage L91 via the oil passage L92. Here, the oil passage L92 has one end connected to an oil supply/discharge port provided at the bottom of the accumulator 92, and the other end connected to a connection portion J91 of the oil passage L91.

[C-2-3] Servo valve 93
The servo valve 93 is provided to control the amount of hydraulic oil supplied from the pump 91 and the accumulator 92 to the driving device 80b. Here, the servo valve 93 is connected to the first oil chamber C831a of the driving device 80b via the oil passage L93a. In addition, the servo valve 93 is connected to an oil passage L93b through which hydraulic oil flows to the oil tank 96 as drain oil. When the intercept valve V30b is opened, hydraulic oil from the pump 91 and the accumulator 92 is supplied to the first oil chamber C831a through the servo valve 93 and the oil passage L93a in sequence. When the intercept valve V30b is closed, the working oil from the first oil chamber C831a is discharged to the oil tank 96 through the servo valve 93 and the oil passage L93b in sequence. When the intercept valve V30b is closed, the hydraulic oil discharged from the first oil chamber C831a flows as drain oil from the servo valve 93 to the oil tank 96 through the oil passage L93b. When the servo valve 93 is opened again, the hydraulic oil from the oil tank 96 is supplied from the oil passage L93b through the servo valve 93 to the first oil chamber C831a through the oil passage L93a.

[D] Operation [D-1] During start-up When performing start-up operation in the steam turbine system, the hydraulic circuit device 90J supplies hydraulic oil to the drive device 80b so that the state changes from the fully closed state to the fully opened state at a predetermined time. supply to Here, the hydraulic circuit device 90J supplies hydraulic oil from the pump 91 and the accumulator 92 to the drive device 80b, thereby fully opening the intercept valve V30b.

[D-2] Normal Operation During normal operation of the steam turbine system, the hydraulic circuit device 90J supplies hydraulic oil to the drive device 80b so that the opening degree corresponds to the requested power generation output. Here, the hydraulic circuit device 90J adjusts the degree of opening of the intercept valve V30b by supplying hydraulic fluid pressurized by the pump 91 to the drive device 80b.

[D-3] When an accident occurs in the power transmission system When performing high-speed valve control when an accident occurs in the power transmission system, the intercept valve V30b is rapidly closed from the fully open state (rapidly closed), and then rapidly opened. (Perform a rapid opening operation). When the intercept valve V30b is caused to open rapidly, hydraulic fluid is supplied from the pump 91 and the accumulator 92 to the drive device 80b in the hydraulic circuit device 90J, as in the starting operation.

JP-A-6-88504

As described above, when performing high-speed valve control when an accident occurs in the power transmission system, a rapid opening operation is performed so that steam valves such as the intercept valve V30b rapidly change from a fully closed state to a fully open state. . At this time, hydraulic fluid is supplied from the pump 91 and the accumulator 92 to the driving device 80b. In this case, since it is necessary to supply a large amount of hydraulic oil from the pump 91 and the accumulator 92 to the drive device 80b, the capacities of the pump 91 and the accumulator 92 must be increased.

However, there are few occasions when it is necessary to perform high-speed valve control as described above, and in normal operation, increasing the capacity of equipment may cause a decrease in plant efficiency including power consumption.

Therefore, the problem to be solved by the present invention is to provide a hydraulic circuit device that can perform high-speed valve control without increasing the capacity of equipment and that can suppress a decrease in plant efficiency. is.

A hydraulic circuit device of an embodiment has a pump, an accumulator, a booster, a switching valve , a servo valve, a first check valve, a second check valve, and a third check valve, and drives a steam valve. to operate the drive for The pump discharges hydraulic oil. The accumulator stores hydraulic oil inside. The booster is configured to supply hydraulic fluid to the primary port so that hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary port and the hydraulic fluid discharged from the pump is delivered from the secondary port. ing. The switching valve is configured to be switchable between a state in which the accumulator and the primary side port are blocked and a state in which the accumulator and the primary side port are in communication. A servo valve supplies the hydraulic fluid discharged from the pump to a drive device. The first check valve is interposed between the pump and the servo valve, and is configured to allow hydraulic fluid to flow from the pump side to the servo valve side. The second check valve is interposed between the accumulator and the secondary port, and is configured to allow hydraulic fluid to flow from the accumulator side to the secondary port side. The third check valve is interposed between the secondary side port and the servo valve, and is configured to allow hydraulic fluid to flow from the secondary side port side to the servo valve side.
When performing a quick opening operation for closing the steam valve more rapidly than when performing a normal opening operation for the steam valve, the switching valve is switched from a state in which the accumulator and the primary port are cut off to the accumulator and the primary port. Hydraulic oil is supplied from the accumulator to the primary side port and hydraulic oil is supplied from the secondary side port to the driving device by switching to a state in which communication is established between the accumulator and the primary side port. When executing the opening operation, the hydraulic oil discharged from the pump is supplied to the driving device via the servo valve, and the pump and the accumulator are in communication via the switching valve. Hydraulic oil that has passed through the switching valve from and the hydraulic oil that has flowed out of the accumulator are supplied to the secondary side port through the second check valve, and when performing the rapid opening operation, the secondary side Hydraulic oil discharged from the port is supplied to the driving device via the third check valve and the servo valve without flowing into the pump and the accumulator by the first check valve and the second check valve. is configured as

FIG. 1A is a diagram schematically showing a hydraulic circuit device 90 according to the first embodiment (normal opening operation and normal closing operation). FIG. 1B is a diagram schematically showing the hydraulic circuit device 90 according to the first embodiment (rapid opening operation). FIG. 2A is a diagram schematically showing a hydraulic circuit device 90 according to the second embodiment (normal opening operation and normal closing operation). FIG. 2B is a diagram schematically showing a hydraulic circuit device 90 according to the second embodiment. (rapid opening operation). FIG. 3A is a diagram schematically showing a hydraulic circuit device 90 according to the third embodiment (normal opening operation and normal closing operation). FIG. 3B is a diagram schematically showing the hydraulic circuit device 90 according to the third embodiment (rapid opening operation). FIG. 4A is a diagram schematically showing a hydraulic circuit device 90 according to the fourth embodiment (normal opening operation and normal closing operation). FIG. 4B is a diagram schematically showing the hydraulic circuit device 90 according to the fourth embodiment (rapid opening operation). FIG. 5 is a diagram schematically showing a steam turbine system according to related art. FIG. 6 is a diagram schematically showing an intermediate steam stop valve V30a and an intercept valve V30b in a related art steam turbine system. FIG. 7 is a diagram schematically showing a hydraulic circuit device 90J that operates the driving device 80b using hydraulic oil in a steam turbine system according to related art.

Embodiments will be described with reference to the drawings.

<First embodiment>
[A] Hydraulic circuit device 90
1A and 1B are diagrams schematically showing a hydraulic circuit device 90 according to the first embodiment. FIGS. 1A and 1B show, for example, a hydraulic circuit device 90 that operates a drive device 80b (see FIG. 6) for driving an intercept valve V30b, which is a steam valve.

FIG. 1A shows how the intercept valve V30b is normally opened and closed. FIG. 1B shows how the intercept valve V30b is opened more rapidly than the normal opening operation (rapid opening operation) when an accident occurs in the transmission system.

As shown in FIGS. 1A and 1B, the hydraulic circuit device 90 of this embodiment includes a pump 91, an accumulator 92, a servo valve 93, a booster 94, a switching valve V95, and a check valve V11 (first check valve), check valve V12 (second check valve), and check valve V13 (third check valve). That is, the hydraulic circuit device 90 of the present embodiment includes a booster 94, a switching valve V95, a check valve V11 (first check valve), a check The arrangement relationship of the hydraulic circuit further including a valve V12 (second check valve) and a check valve V13 (third check valve) and configured by these is different from the related art. Except for this point and related points, the present embodiment is the same as the related art described above. Therefore, descriptions of matters that overlap with the related art will be omitted as appropriate.

[A-1] Pump 91
In the hydraulic circuit device 90 of this embodiment, the pump 91 is a device that discharges hydraulic oil, and is connected to the servo valve 93 via the oil passage L91 as in the related art. Here, in the oil passage L91, unlike the related art, a connecting portion J91a and a connecting portion J91b are sequentially provided from the pump 91 side to the servo valve 93 side. An oil passage L911 is provided between the connection portion J91a and the connection portion J91b. A connecting portion J911a and a connecting portion J911b are sequentially provided in the oil passage L911 from the connecting portion J91a side to the connecting portion J91b side. One end of an oil passage L942 is connected to the connection portion J911b of the oil passage L911.

[A-2] Accumulator 92
The accumulator 92 is a device that internally stores hydraulic oil, and one end of an oil passage L92 is connected to an oil supply/discharge port provided at the bottom. The other end of the oil passage L92 is connected to the connection portion J911a of the oil passage L911.

[A-3] Booster 94
The booster 94 is a pressure intensifier, and is supplied to the primary side port P941 with hydraulic oil so that hydraulic oil having a higher pressure than the hydraulic oil supplied to the primary side port P941 is sent out from the secondary side port P942. is configured to Here, the booster 94 is configured such that the pressure of the hydraulic fluid discharged by the booster 94 is higher than the pressure of the hydraulic fluid discharged by the pump 91 .

Specifically, the booster 94 has a primary side cylinder 941 and a secondary side cylinder 942 . The primary side cylinder 941 has a drive chamber C941 inside, and the primary side piston 943 is accommodated in the drive chamber C941. The drive chamber C941 is partitioned by a primary side piston 943 into a first drive chamber portion C941a and a second drive chamber portion C941b. The secondary side cylinder 942 has a pressure increasing chamber C942 inside, and a secondary side piston 944 is accommodated in the pressure increasing chamber C942. The pressure-increasing chamber C942 is divided by a secondary-side piston 944 into a first pressure-increasing chamber portion C942a and a second pressure-increasing chamber portion C942b.

The primary side cylinder 941 and the secondary side cylinder 942 are connected to each other, and the primary side piston 943 and the secondary side piston 944 are connected via a connecting rod 945 . Here, the cross-sectional area of the secondary side piston 944 is configured to be smaller than the cross-sectional area of the primary side piston 943 .

In the booster 94, the primary side port P941 is provided so as to communicate with the first drive chamber portion C941a. One end of an oil passage L941 is connected to the primary port P941. The secondary side port P942 is provided so as to communicate with the second pressure increasing chamber portion C942b. The other end of the oil passage L942 is connected to the secondary port P942.

[A-4] Switching valve V95
The switching valve V95 is a four-way solenoid valve in this embodiment, and connects a first switching valve port P951, a second switching valve port P952, a third switching valve port P953, and a fourth switching valve port P954. include.

As shown in FIG. 1A, when the intercept valve V30b performs the normal opening operation and the normal closing operation, the switching valve V95 is in a non-excited state, and the first switching valve port P951 and the second switching valve port P951 are in a non-excited state. P952 and P952 are communicated, and communication is provided between the third switching valve port P953 and the fourth switching valve port P954.

On the other hand, as shown in FIG. 1B, when the intercept valve V30b is rapidly opened, the switching valve V95 is changed to an excited state, and the first switching valve port P951 and the second switching valve port P952 are connected. and between the third switching valve port P953 and the fourth switching valve port P954 are cut off without communication, and are blocked through the second switching valve port P952 and the third switching valve port P953. are configured to communicate with each other. That is, the switching valve V95 is configured to switch between a state in which the accumulator 92 and the primary side port P941 are blocked and a state in which the accumulator 92 and the primary side port P941 are in communication. Note that the switching valve port P954 is communicated with the oil tank 96 .

[A-5] Check valve V11
The check valve V11 is installed between the connecting portion J91a and the connecting portion J91b in the oil passage L91. Here, the check valve V11 is interposed between the pump 91 and the servo valve 93, and is configured so that hydraulic fluid flows from the pump 91 side to the servo valve 93 side.

[A-6] Check valve V12
The check valve V12 is installed between the connecting portion J911a and the connecting portion J911b in the oil passage L911. Here, the check valve V12 is interposed between the accumulator 92 and the secondary side port P942, and configured so that hydraulic fluid flows from the accumulator 92 side to the secondary side port P942 side.

[A-7] Check valve V13
The check valve V13 is installed between the connecting portion J911b and the connecting portion J91b in the oil passage L911. Here, the check valve V13 is interposed between the secondary side port P942 and the servo valve 93, and is configured so that hydraulic fluid flows from the secondary side port P942 side to the servo valve 93 side. there is The check valve V13 is configured such that the cracking pressure is higher than that of the check valve V11.

[B] Operation [B-1] Normal Opening Operation A case where the intercept valve V30b is caused to perform a normal opening operation will be described with reference to FIG. 1A.

When the intercept valve V30b is normally opened, the switching valve V95 allows the discharge port of the pump 91 and the oil supply/discharge port of the accumulator 92 to communicate with each other, as shown in FIG. 1A. As a result, hydraulic fluid pressurized by the pump 91 is supplied to the accumulator 92 via the switching valve V95. Along with this, the hydraulic fluid pressurized by the pump 91 flows into the secondary side port P942 of the booster 94 via the switching valve V95.

Specifically, the switching valve V95 maintains the non-excited state. When the switching valve V95 is in a non-excited state, communication is established between the first switching valve port P951 and the second switching valve port P952. Therefore, the connection portion J911a and the connection portion J911b are in communication with each other in the oil passage L911, so that the discharge port of the pump 91 and the oil supply/discharge port of the accumulator 92 are in communication with each other through the switching valve V95. Become.

Along with this, when the switching valve V95 is in the non-excited state, communication is established between the third switching valve port P953 and the fourth switching valve port P954. Therefore, the oil passage L941 is in a state of communication via the switching valve V95.

When the intercept valve V30b is to be normally opened, the hydraulic oil pressurized by the pump 91 is supplied to the servo valve 93 through the check valve V11 in the oil passage L91.

In addition, hydraulic oil pressurized by the pump 91 flows into the oil passage L911 from the connection portion J91a of the oil passage L91. Hydraulic oil that has flowed into the oil passage L911 passes between the first switching valve port P951 and the second switching valve port P952 of the switching valve V95 in the non-excited state, and then flows from the connecting portion J911a to the oil passage L92. It flows in and is supplied to the oil supply/discharge port of the accumulator 92 . As a result, the accumulator 92 is filled with hydraulic oil.

When the accumulator 92 is filled with hydraulic oil, the hydraulic oil that has passed through the connecting portion J911a in the oil passage L911 flows into the oil passage L942 from the connecting portion J911b via the check valve V11. The hydraulic oil that has flowed into the oil passage L942 flows into the secondary side port P942 of the booster 94 . That is, the hydraulic fluid from the pump 91 that has passed through the switching valve V95 and the hydraulic fluid that has flowed out from the accumulator 92 are supplied to the secondary side port P942 via the check valve V12. As a result, in the booster 94, the hydraulic oil filled in the primary side port P941 flows into the oil passage L941, and the third switching valve port P953 and the fourth switching valve port P953 of the switching valve V95 in the non-excited state. After passing through P954, it is discharged to the oil tank 96.

As described above, the check valve V13 has a higher cracking pressure than the check valve V11. Therefore, the check valve V13 is closed without chattering.

When the intercept valve V30b is closed, hydraulic oil is drained from the first oil chamber C831a of the drive device 80b via the servo valve 93 as in the related art.

[B-2] High-speed valve control (rapid opening operation)
Next, after the intercept valve V30b is fully closed due to the occurrence of an accident in the power transmission system, the intercept valve V30b is rapidly fully opened from the fully closed state (rapidly opened) in order to restore valve control. The case will be described with reference to FIG. 1B. That is, the operation when the hydraulic circuit device 90 receives the opening degree command signal S100 for high-speed valve control via the control device 100 will be described.

When the intercept valve V30b is to be rapidly opened, the switching valve V95, as shown in FIG. Switch to connected state. As a result, the hydraulic oil that has flowed out of the accumulator 92 flows into the primary side port P941 of the booster 94 via the switching valve V95. As a result, in the booster 94, hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary side port P941 is discharged from the secondary side port P942. Hydraulic oil discharged from the booster 94 is supplied to the drive device 80b via the servo valve 93 .

Specifically, the switching valve V95 is changed from the non-excited state to the excited state. When the switching valve V95 is energized, communication is established between the second switching valve port P952 and the third switching valve port P953. Accordingly, the first switching valve port P951 and the second switching valve port P952 and the third switching valve port P953 and the fourth switching valve port P954 are blocked. Therefore, the oil supply/discharge port of the accumulator 92 and the primary side port P941 of the booster 94 communicate with each other via the switching valve V95.

As a result, the hydraulic oil flowing out from the accumulator 92 to the oil passage L92 flows through the connection portion J911a of the oil passage L91 and then flows into the primary port P941 of the booster 94 via the switching valve V95. As a result, in the booster 94, hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary side port P941 is discharged from the secondary side port P942 to the oil passage L942.

Hydraulic oil discharged from the booster 94 to the oil passage L942 flows into the oil passage L911 from the connection J911b, and passes through the check valve V13 that is opened according to the discharge pressure of the booster 94 in the oil passage L911. The hydraulic oil that has flowed through the check valve V13 is supplied to the driving device 80b via the servo valve 93 after flowing into the oil passage L91 from the connecting portion J91b.

When the intercept valve V30b is changed from the fully closed state to the fully open state in order to perform high-speed valve control, the servo valve 93 outputs an opening degree command signal S100 to the control device 100 (see FIG. 5) to fully open the intercept valve V30b. It is in a state of receiving from Therefore, since the servo valve 93 is in a state in which the internal spool (not shown) has moved to the maximum extent, the supply amount of hydraulic oil to the drive device 80b increases. As a result, the hydraulic fluid discharged from the booster 94 is used for the rapid opening operation of the intercept valve V30b until the pressure of the hydraulic fluid discharged from the pump 91 is balanced. subsidize As a result, the intercept valve V30b is rapidly changed from the fully closed state to the fully opened state.

Note that the pressure of the hydraulic fluid discharged from the booster 94 is higher than the pressure of the hydraulic fluid discharged from the accumulator 92 . Therefore, since the check valve V12 is closed, the hydraulic oil discharged from the accumulator 92 is not directly supplied to the servo valve 93 without the intervention of the booster 94 .

Also, the pressure of the hydraulic fluid discharged from the booster 94 is higher than the pressure of the hydraulic fluid discharged from the pump 91 . Therefore, since the check valve V11 is closed, the hydraulic oil discharged from the pump 91 is not supplied to the servo valve 93.

As described above, in the present embodiment, when the intercept valve V30b is rapidly opened, the hydraulic oil discharged from the secondary side port P942 is caused to flow into the pump 91 and the accumulator 92 by the check valves V11 and V12. It is supplied to the driving device 80b via the check valve V13 and the servo valve 93 without being stopped.

After the high-speed valve control is completed, the switching valve V95 returns to the non-excited state as shown in FIG. 1A in the same manner as in the normal opening operation and normal closing operation. As a result, hydraulic oil pressurized by the pump 91 is supplied to the accumulator 92 via the switching valve V95. Along with this, the hydraulic oil pressurized by the pump 91 flows through the switching valve V95 and the check valve V11 in sequence, flows into the secondary side port P942 of the booster 94, and flows from the primary side port P941 of the booster 94. is discharged.

[C] Summary As described above, in the present embodiment, when the intercept valve V30b is to be rapidly opened, the switching valve V95 is in a state in which the communication between the accumulator 92 and the primary side port P941 of the booster 94 is cut off. , the accumulator 92 and the primary side port P941 of the booster 94 are switched to a state in which communication is established. Thereby, hydraulic oil is supplied from the accumulator 92 to the primary side port P941 of the booster 94 . As a result, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary port P941 and hydraulic fluid discharged from the pump 91 is supplied from the secondary port P942 of the booster 94 to the driving device 80b.

Therefore, in this embodiment, high-speed valve control can be performed without increasing the capacities of devices such as the pump 91 and the accumulator 92, and the plant efficiency can be improved.

<Second embodiment>
[A] Hydraulic circuit device 90
2A and 2B are diagrams schematically showing a hydraulic circuit device 90 according to the second embodiment. 2A and 2B show the hydraulic circuit device 90 that operates the drive device 80b (see FIG. 6) of the intercept valve V30b.

Similar to FIG. 1A, FIG. 2A shows how the intercept valve V30b is normally opened and closed. Similarly to FIG. 1B, FIG. 2B shows how the intercept valve V30b is rapidly opened when an accident occurs in the transmission system.

As shown in FIGS. 2A and 2B, the hydraulic circuit device 90 of this embodiment includes a pump 91, an accumulator 92, a servo valve 93 and a booster 94, as in the case of the first embodiment (see FIGS. 1A and 1B). and a switching valve V95. Further, the hydraulic circuit device 90 of this embodiment has a check valve V21 (first check valve), a check valve V23 (second check valve), and an orifice R23. The hydraulic circuit device 90 of this embodiment includes portions that are arranged differently from those of the first embodiment. Except for this point and related points, this embodiment is the same as the above-described first embodiment. Therefore, descriptions of overlapping items will be omitted as appropriate.

[A-1] Pump 91
In the hydraulic circuit device 90 of this embodiment, the pump 91 is connected to the servo valve 93 via the oil passage L91. Here, a connection portion J91a and a connection portion J91b are sequentially provided in the oil passage L91 from the pump 91 side to the servo valve 93 side. One end of the oil passage L911 is connected to the connection portion J91a. One end of an oil passage L942 is connected to the connection portion J91b.

[A-2] Accumulator 92
The accumulator 92 has the other end of the oil passage L911 connected to an oil supply/discharge port provided at the bottom.

[A-3] Booster 94
The booster 94 has a primary side port P941 connected to one end of an oil passage L941. The secondary port P942 of the booster 94 is connected to the other end of the oil passage L942.

[A-4] Switching valve V95
As in the first embodiment, the switching valve V95 is a four-way solenoid valve, and includes a first switching valve port P951, a second switching valve port P952, a third switching valve port P953, and a fourth switching valve port P953. switching valve port P954.

As shown in FIG. 2A, when the switching valve V95 is in the non-excited state, the discharge port of the pump 91 and the oil supply/discharge port of the accumulator 92 are connected to the first switching valve port P951 as in the first embodiment. and the second switching valve port P952.

As shown in FIG. 2B, when the switching valve V95 is in the energized state, a second A switching valve V95 is configured to allow communication between the switching valve port P952 and the third switching valve port P953.

[A-5] Check valve V21
The check valve V21 is installed between the connecting portion J91a and the connecting portion J91b in the oil passage L91. Here, the check valve V21 is interposed between the pump 91 and the servo valve 93, and is configured so that hydraulic oil flows from the pump 91 side to the servo valve 93 side.

[A-6] Check valve V23
The check valve V23 is installed in the oil passage L942. In the oil passage L942, a connection portion J942a and a connection portion J942b are sequentially provided from the connection portion J91b side toward the booster 94 side, and the check valve V23 is provided between the connection portion J942a and the connection portion J942b. is installed in Here, the check valve V23 is interposed between the secondary side port P942 and the servo valve 93, and is configured so that hydraulic fluid flows from the secondary side port P942 side to the servo valve 93 side. there is

[A-9] Orifice R23
The orifice R23 is installed in an oil passage L942b provided between the connection portion J942a and the connection portion J942b so as to bypass the check valve V23. Here, the orifice R23 is interposed between the secondary side port P942 and the servo valve 93, and is provided so as to bypass the second check valve V23.

[B] Operation [B-1] Normal Opening Operation A case where the intercept valve V30b is caused to perform a normal opening operation will be described with reference to FIG. 2A.

In this embodiment, when the intercept valve V30b is normally opened, the pump 91 and the accumulator 92 are in communication via the switching valve V95, as shown in FIG. 2A. Along with this, the hydraulic oil discharged from the pump 91 is supplied to the secondary side port P942 sequentially via the first check valve V21 and the orifice R23 without passing through the switching valve V95.

Specifically, the switching valve V95 maintains the non-excited state. When the switching valve V95 is in a non-excited state, communication is established between the first switching valve port P951 and the second switching valve port P952. Therefore, the discharge port of the pump 91 and the oil supply/discharge port of the accumulator 92 communicate with each other via the switching valve V95.

Along with this, when the switching valve V95 is in the non-excited state, communication is established between the third switching valve port P953 and the fourth switching valve port P954. Therefore, the oil passage L941 is in a state of communication via the switching valve V95.

Hydraulic oil pressurized by the pump 91 is supplied to the servo valve 93 via the check valve V21 in the oil passage L91.

At this time, the hydraulic fluid pressurized by the pump 91 flows into the oil passage L911 from the connection portion J91a of the oil passage L91. Hydraulic oil that has flowed into the oil passage L911 passes between the first switching valve port P951 and the second switching valve port P952 of the switching valve V95 in the non-excited state. Hydraulic oil is then supplied to the oil supply/discharge port of the accumulator 92 . As a result, the accumulator 92 is filled with hydraulic oil.

In addition, hydraulic oil pressurized by the pump 91 flows into the oil passage L942 from the connection portion J91b of the oil passage L91. The hydraulic oil that has flowed into the oil passage L942 flows into the secondary side port P942 of the booster 94 after passing through the orifice R23 installed in the oil passage L942b. As a result, in the booster 94, hydraulic oil flows from the primary side port P941 into the oil passage L941, and the switching valve V95 in the non-excited state flows between the third switching valve port P953 and the fourth switching valve port P954. After passing through, it is discharged as drain oil.

[B-2] High-speed valve control (rapid opening operation)
Next, after the intercept valve V30b is fully closed due to the occurrence of an accident in the power transmission system, the intercept valve V30b is rapidly fully opened from the fully closed state (rapidly opened) in order to restore valve control. The case will be described with reference to FIG. 2B.

When the intercept valve V30b is to be rapidly opened, the switching valve V95 is switched from the state in which the connection between the accumulator 92 and the primary side port P941 is blocked to the accumulator 92 and the primary side port P941, as in the first embodiment. It switches to a state in which communication with the port P941 is established. As a result, hydraulic fluid is supplied from the accumulator 92 to the primary side port P941, and hydraulic fluid is supplied to the drive device 80b from the secondary side port P942.

Specifically, the switching valve V95 is changed from the non-excited state to the excited state. When the switching valve V95 is in an excited state, communication is established between the second switching valve port P952 and the third switching valve port P953. Therefore, the oil supply/discharge port of the accumulator 92 and the primary side port P941 of the booster 94 communicate with each other via the switching valve V95.

As a result, the hydraulic fluid that has flowed out of the accumulator 92 flows into the primary side port P941 of the booster 94 via the switching valve V95. As a result, in the booster 94, hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary side port P941 is discharged from the secondary side port P942.

Hydraulic oil discharged from the secondary side port P942 of the booster 94 passes through the check valve V23, which is opened according to the discharge pressure of the booster 94, in the oil passage L942. The hydraulic oil that has flowed through the check valve V23 is supplied to the driving device 80b via the servo valve 93. As shown in FIG. Here, the hydraulic oil discharged from the secondary side port P942 is supplied to the driving device 80b via the check valve V23 without flowing into the pump 91 by the check valve V21. As a result, the intercept valve V30b is rapidly changed from the fully closed state to the fully opened state.

Note that after the high-speed valve control is completed, the switching valve V95 returns to the non-excited state as shown in FIG. 2A in the same manner as in the normal opening operation and normal closing operation. As a result, hydraulic oil pressurized by the pump 91 is supplied to the accumulator 92 via the switching valve V95. Along with this, the hydraulic fluid pressurized by the pump 91 flows into the secondary side port P942 of the booster 94 and is discharged from the primary side port P941 of the booster 94 .

[C] Summary As described above, in the present embodiment, when the intercept valve V30b is to be rapidly opened, the switching valve V95 is connected to the primary side of the accumulator 92 and the booster 94, as in the first embodiment. The state in which the port P941 is cut off is switched to the state in which the primary side port P941 of the accumulator 92 and the booster 94 is in communication. Thereby, hydraulic oil is supplied from the accumulator 92 to the primary side port P941 of the booster 94 . As a result, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary port P941 and hydraulic fluid discharged from the pump 91 is supplied from the secondary port P942 of the booster 94 to the driving device 80b.

Therefore, in the present embodiment, as in the first embodiment, high-speed valve control can be executed without increasing the capacities of devices such as the pump 91 and the accumulator 92, thereby improving plant efficiency. It is possible.

In the first embodiment, when the intercept valve V30b is rapidly opened, the pressure from the accumulator 92 to the servo valve 93 increases until the discharge pressure of the booster 94 rises and the check valve V12 is fully closed. Some of the hydraulic oil may flow out. However, in the present embodiment, the switching valve V95 shuts off the connection between the accumulator 92 and the servo valve 93 during the rapid opening operation. Therefore, in this embodiment, it is possible to further prevent hydraulic fluid from flowing out from the accumulator 92 to the servo valve 93 .

<Third Embodiment>
[A] Hydraulic circuit device 90
3A and 3B are diagrams schematically showing a hydraulic circuit device 90 according to the third embodiment. 3A and 3B show the hydraulic circuit device 90 that operates the drive device 80b (see FIG. 6) of the intercept valve V30b.

Similar to FIG. 1A, FIG. 3A shows how the intercept valve V30b is normally opened and closed. FIG. 3B, like FIG. 1B, shows how the intercept valve V30b is made to open rapidly when an accident occurs in the transmission system.

As shown in FIGS. 3A and 3B, the hydraulic circuit device 90 of this embodiment includes a pump 91, an accumulator 92, a servo valve 93, and a booster 94, as in the case of the first embodiment (see FIGS. 1A and 1B). and a switching valve V95. Further, the hydraulic circuit device 90 of this embodiment has a check valve V31 (first check valve), a check valve V32 (second check valve), and an orifice R32. The hydraulic circuit device 90 of this embodiment includes portions that are arranged differently from those of the first embodiment. Also, the configuration of the switching valve V95 is different from that of the first embodiment. Except for this point and related points, this embodiment is the same as the above-described first embodiment. Therefore, descriptions of overlapping items will be omitted as appropriate.

[A-1] Pump 91
In the hydraulic circuit device 90 of this embodiment, the pump 91 is connected to the servo valve 93 via the oil passage L91. Here, a connecting portion J91a, a connecting portion J91b, and a connecting portion J91c are sequentially provided in the oil passage L91 from the pump 91 side to the servo valve 93 side. One end of the oil passage L911 is connected to the connection portion J91a. One end of the oil passage L92 is connected to the connection portion J91b. One end of an oil passage L942 is connected to the connection portion J91c.

[A-2] Accumulator 92
The accumulator 92 has the other end of the oil passage L92 connected to an oil supply/discharge port provided at the bottom.

[A-3] Booster 94
The booster 94 has a primary side port P941 connected to one end of an oil passage L941. The secondary port P942 of the booster 94 is connected to the other end of the oil passage L942.

[A-4] Switching valve V95
Unlike the first embodiment, the switching valve V95 is a two-way solenoid valve and includes a first switching valve port P951, a second switching valve port P952, and a third switching valve port P953.

As shown in FIG. 3A, when the switching valve V95 is in the non-excited state, the communication between the first switching valve port P951 and the second switching valve port P952 is blocked. The switching valve V95 is configured such that the second switching valve port P952 and the third switching valve port P953 communicate with each other.

On the other hand, as shown in FIG. 3B, when the switching valve V95 is in an excited state, the communication between the second switching valve port P952 and the third switching valve port P953 is interrupted. The switching valve V95 is configured such that the switching valve port P951 and the second switching valve port P952 are in communication.

[A-5] Check valve V31
The check valve V31 is installed between the connecting portion J91b and the connecting portion J91c in the oil passage L91. Here, the check valve V31 is interposed between the pump 91 and the servo valve 93, and configured so that hydraulic oil flows from the pump 91 side to the servo valve 93 side.

[A-6] Check valve V32
The check valve V32 is installed in the oil passage L942. In the oil passage L942, a connection portion J942a and a connection portion J942b are sequentially provided from the connection portion J91b side toward the booster 94 side, and the check valve V32 is provided between the connection portion J942a and the connection portion J942b. is installed in Here, the check valve V32 is interposed between the secondary side port P942 and the servo valve 93, and is configured so that hydraulic fluid flows from the secondary side port P942 side to the servo valve 93 side. there is

[A-7] Orifice R32
The orifice R32 is installed in an oil passage L942b provided between the connection portion J942a and the connection portion J942b so as to bypass the check valve V32. Here, the orifice R32 is interposed between the secondary side port P942 and the servo valve 93, and is provided so as to bypass the second check valve V32.

[B] Operation [B-1] Normal Opening Operation A case where the intercept valve V30b is caused to perform a normal opening operation will be described with reference to FIG. 3A.

In the present embodiment, when the intercept valve V30b is normally opened, the hydraulic fluid discharged from the pump 91 and the hydraulic fluid flowing out from the accumulator 92 pass through the orifice R32 without passing through the switching valve V95. and supplied to the secondary side port P942.

Specifically, the switching valve V95 maintains the non-excited state. When the switching valve V95 is in a non-excited state, communication is established between the second switching valve port P952 and the third switching valve port P953. Therefore, the oil passage L941 is in a state of communication via the switching valve V95.

Hydraulic oil pressurized by the pump 91 is supplied to the servo valve 93 via the check valve V31 in the oil passage L911.

At this time, the hydraulic oil pressurized by the pump 91 flows into the oil passage L92 from the connection portion J91b of the oil passage L91. The hydraulic oil that has flowed into the oil passage L92 is supplied to the oil supply/discharge port of the accumulator 92 . As a result, the accumulator 92 is filled with hydraulic oil.

In addition, hydraulic oil pressurized by the pump 91 flows into the oil passage L942 from the connection portion J91c of the oil passage L91. The hydraulic oil that has flowed into the oil passage L942 flows into the secondary side port P942 of the booster 94 after passing through the orifice R23 installed in the oil passage L942b. As a result, in the booster 94, hydraulic oil flows from the primary side port P941 into the oil passage L941, and the switching valve V95 in the non-excited state flows between the second switching valve port P952 and the third switching valve port P953. After passing through, it is discharged as drain oil.

The check valve V32 is closed because the pressure on the discharge side of the booster 94 is lower than the pressure on the servo valve 93 side.

[B-2] High-speed valve control (rapid opening operation)
Next, after the intercept valve V30b is fully closed due to the occurrence of an accident in the power transmission system, the intercept valve V30b is rapidly fully opened from the fully closed state (rapidly opened) in order to restore valve control. The case will be described with reference to FIG. 3B.

When the intercept valve V30b is to be rapidly opened, the switching valve V95 is switched from the state in which the connection between the accumulator 92 and the primary side port P941 is blocked to the accumulator 92 and the primary side port P941, as in the first embodiment. P941 is switched to a state in which communication is established. As a result, hydraulic fluid is supplied from the accumulator 92 to the primary side port P941, and hydraulic fluid is supplied to the drive device 80b from the secondary side port P942.

Specifically, the switching valve V95 is changed from the non-excited state to the excited state. When the switching valve V95 is in an excited state, the first switching valve port P951 and the second switching valve port P952 communicate with each other. Therefore, the oil supply/discharge port of the accumulator 92 and the primary side port P941 of the booster 94 communicate with each other via the switching valve V95.

As a result, the hydraulic fluid that has flowed out of the accumulator 92 flows into the primary side port P941 of the booster 94 via the switching valve V95. As a result, in the booster 94, hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary side port P941 is discharged from the secondary side port P942.

Hydraulic oil discharged from the booster 94 passes through the check valve V32, which is opened according to the discharge pressure of the booster 94, in the oil passage L942. The hydraulic oil that has flowed through the check valve V32 is supplied to the driving device 80b via the servo valve 93. As a result, the intercept valve V30b is rapidly changed from the fully closed state to the fully opened state.

The pressure of hydraulic fluid discharged from the pump 91 and the pressure of hydraulic fluid flowing out from the accumulator 92 are lower than the pressure of hydraulic fluid discharged from the booster 94 . Therefore, the check valve V31 is closed and the check valve V32 is open. As a result, in the present embodiment, the hydraulic oil discharged from the secondary side port P942 is supplied to the driving device 80b via the check valve V32 without flowing into the pump 91 and the accumulator 92 through the check valve V31. be.

Further, after the high-speed valve control is completed, the switching valve V95 returns to the non-excited state as shown in FIG. 3A in the same manner as in the normal opening operation and normal closing operation. As a result, the hydraulic fluid pressurized by the pump 91 is supplied to the accumulator 92, flows into the secondary side port P942 of the booster 94, and is discharged from the primary side port P941 of the booster 94.

[C] Summary As described above, in the present embodiment, when the intercept valve V30b is to be rapidly opened, the switching valve V95 is connected to the primary side of the accumulator 92 and the booster 94, as in the first embodiment. The state in which the port P941 is cut off is switched to the state in which the primary side port P941 of the accumulator 92 and the booster 94 is in communication. Thereby, hydraulic oil is supplied from the accumulator 92 to the primary side port P941 of the booster 94 . As a result, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary port P941 and hydraulic fluid discharged from the pump 91 is supplied from the secondary port P942 of the booster 94 to the driving device 80b.

Therefore, in the present embodiment, as in the first embodiment, high-speed valve control can be executed without increasing the capacities of devices such as the pump 91 and the accumulator 92, thereby improving plant efficiency. It is possible.

The hydraulic circuit device 90 of this embodiment has a simpler configuration than the other embodiments described above. Therefore, in this embodiment, the reliability of the hydraulic circuit device 90 can be improved.

<Fourth Embodiment>
[A] Hydraulic circuit device 90
4A and 4B are diagrams schematically showing a hydraulic circuit device 90 according to the fourth embodiment. 4A and 4B show the hydraulic circuit device 90 that operates the drive device 80b (see FIG. 6) of the intercept valve V30b.

Similar to FIG. 1A, FIG. 4A shows how the intercept valve V30b is normally opened and closed. Similarly to FIG. 1B, FIG. 4B shows a state in which the intercept valve V30b is made to open rapidly when an accident occurs in the power transmission system.

As shown in FIGS. 4A and 4B, the hydraulic circuit device 90 of this embodiment includes a pump 91, an accumulator 92, a servo valve 93 and a booster 94, as in the case of the first embodiment (see FIGS. 1A and 1B). and a switching valve V95 (first switching valve). Further, the hydraulic circuit device 90 of the present embodiment has a switching valve V42 (second switching valve) other than the switching valve V95 (first switching valve), and has an orifice R42. The hydraulic circuit device 90 of this embodiment includes portions that are arranged differently from those of the first embodiment. Except for this point and related points, this embodiment is the same as the above-described first embodiment. Therefore, descriptions of overlapping items will be omitted as appropriate.

[A-1] Pump 91
In the hydraulic circuit device 90 of this embodiment, the pump 91 is connected to the servo valve 93 via the oil passage L91. Here, the oil passage L91 is provided with a connection portion J91a. One end of the oil passage L911 is connected to the connection portion J91a. A connecting portion J911a is provided in the oil passage L911.

[A-2] Accumulator 92
The accumulator 92 has one end of an oil passage L92 connected to an oil supply/discharge port provided at the bottom. The other end of the oil passage L92 is connected to the connection portion J911a of the oil passage L911.

[A-3] Booster 94
The booster 94 has a primary side port P941 connected to one end of an oil passage L941. The secondary port P942 of the booster 94 is connected to the other end of the oil passage L942.

[A-4] Switching valve V95
As in the first embodiment, the switching valve V95 is a four-way solenoid valve, and includes a first switching valve port P951, a second switching valve port P952, a third switching valve port P953, and a fourth switching valve port P953. switching valve port P954.

As shown in FIG. 4A, when the intercept valve V30b is caused to perform the normal opening operation and the normal closing operation, the switching valve V95 is in the non-excited state, and the pump 91 is turned on as in the case of the first embodiment. The discharge port and the oil supply/discharge port of the accumulator 92 are configured to communicate with each other through a first switching valve port P951 and a second switching valve port P952.

Then, as shown in FIG. 4B, when the intercept valve V30b is to be rapidly opened, the switching valve V95 is changed from the non-excited state to the excited state, and the accumulator 92 is supplied with power as in the case of the first embodiment. The drain port and the primary side port P941 of the booster 94 are configured to communicate with each other through the second switching valve port P952 and the third switching valve port P953.

[A-5] Switching valve V42
The switching valve V42 is a three-way solenoid valve and includes a first valve port P421, a second valve port P422 and a third valve port P423. In the switching valve V42, the first valve port P421 is connected to one end of the oil passage L911. The second valve port P422 is connected to one end of the oil passage L942. One end of the third valve port P423 is connected to the oil passage L42. The other end of the oil passage L42 is connected to a connection portion J93a provided in the oil passage L93a.

As shown in FIG. 4A, when the intercept valve V30b performs normal opening and normal closing operations, the switching valve V42 is arranged between the oil supply/discharge port of the accumulator 92 and the secondary side port P942 of the booster 94. communicates between the first valve port P421 and the second valve port P422.

As shown in FIG. 4B, when the intercept valve V30b is rapidly opened, the switching valve V42 blocks the connection between the oil supply/discharge port of the accumulator 92 and the secondary side port P942 of the booster 94. and the first oil chamber C831a of the driving device 80b are communicated through the second valve port P422 and the third valve port P423.

[A-6] Orifice R42
The orifice R42 is installed in a portion of the oil passage L911 located closer to the switching valve V42 than the connection portion J911a.

[B] Operation [B-1] Normal Opening Operation A case where the intercept valve V30b is caused to perform a normal opening operation will be described with reference to FIG. 4A.

In the present embodiment, when the intercept valve V30b is normally opened, the switching valve V42 connects the accumulator 92 and the secondary port P942 so that the switching valve V95 is switched off from the pump 91. The hydraulic oil that has passed through and the hydraulic oil that has flowed out from the accumulator 92 are supplied to the secondary side port P942.

Further, the switching valve V95 maintains a non-excited state to allow communication between the first switching valve port P951 and the second switching valve port P952. Therefore, the discharge port of the pump 91 and the oil supply/discharge port of the accumulator 92 communicate with each other via the switching valve V95.

Along with this, when the switching valve V95 is in the non-excited state, communication is established between the third switching valve port P953 and the fourth switching valve port P954. Therefore, the oil passage L941 is in a state of communication via the switching valve V95.

Hydraulic oil pressurized by the pump 91 is supplied to the servo valve 93 via the oil passage L91.

At this time, the hydraulic fluid pressurized by the pump 91 flows into the oil passage L911 from the connection portion J91a of the oil passage L91. Hydraulic oil that has flowed into the oil passage L911 passes between the first switching valve port P951 and the second switching valve port P952 of the switching valve V95 in the non-excited state. Hydraulic oil is then supplied to the oil supply/discharge port of the accumulator 92 . As a result, the accumulator 92 is filled with hydraulic oil.

In addition, the hydraulic fluid pressurized by the pump 91 flows to the switching valve V42 via the orifice R42 in the oil passage L911. The switching valve V42 communicates between the first valve port P421 and the second valve port P422 during normal opening operation. Therefore, the oil supply/discharge port of the accumulator 92 and the secondary port P942 of the booster 94 are in communication with each other via the switching valve V42. As a result, the hydraulic oil flows into the secondary side port P942 of the booster 94 via the oil passage L942.

As a result, in the booster 94, the hydraulic oil flows from the primary side port P941 into the oil passage L941, and the switching valve V95 in the non-excited state flows between the third switching valve port P953 and the fourth switching valve port P954. After passing through, it is discharged as drain oil.

[B-2] High-speed valve control (rapid opening operation)
Next, a case in which the intercept valve V30b is rapidly opened from a fully closed state to a fully opened state in order to perform high-speed valve control when an accident occurs in the power transmission system will be described with reference to FIG. 4B. .

When executing the rapid opening operation, the switching valve V95 is switched from the state in which the connection between the accumulator 92 and the primary side port P941 is shut off, as in the case of the first embodiment. Switch to a state in which between are communicated. As a result, hydraulic fluid is supplied from the accumulator 92 to the primary side port P941, and hydraulic fluid is supplied to the drive device 80b from the secondary side port P942.

Specifically, when performing the rapid opening operation, the switching valve V95 is changed from the non-excited state to the excited state. When the switching valve V95 is in an excited state, communication is established between the second switching valve port P952 and the third switching valve port P953. Therefore, the oil supply/discharge port of the accumulator 92 and the primary side port P941 of the booster 94 communicate with each other via the switching valve V95.

As a result, the hydraulic fluid that has flowed out of the accumulator 92 flows into the primary side port P941 of the booster 94 via the switching valve V95. As a result, in the booster 94, hydraulic fluid having a higher pressure than the hydraulic fluid supplied to the primary side port P941 is discharged from the secondary side port P942.

The hydraulic oil discharged from the booster 94 flows through the oil passage L942 and then to the switching valve V42. The switching valve V42 communicates between the second valve port P422 and the third valve port P423 when performing a rapid opening operation. Therefore, the secondary side port P942 of the booster 94 and the first oil chamber C831a of the drive device 80b are communicated through the switching valve V42. As a result, the hydraulic oil discharged from the secondary port P942 of the booster 94 directly flows into the first oil chamber C831a of the driving device 80b without passing through the servo valve 93. As a result, the intercept valve V30b is rapidly changed from the fully closed state to the fully opened state.

[C] Conclusion As described above, when the intercept valve V30b is to be rapidly opened in this embodiment, the switching valve V95 is connected to the primary side ports of the accumulator 92 and the booster 94, as in the first embodiment. The state in which the communication with P941 is cut off is switched to the state in which the communication between the accumulator 92 and the primary side port P941 of the booster 94 is connected. Thereby, hydraulic oil is supplied from the accumulator 92 to the primary side port P941 of the booster 94 . As a result, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary port P941 and hydraulic fluid discharged from the pump 91 is supplied from the secondary port P942 of the booster 94 to the driving device 80b.

Therefore, in the present embodiment, as in the first embodiment, high-speed valve control can be executed without increasing the capacities of devices such as the pump 91 and the accumulator 92, thereby improving plant efficiency. It is possible.

In this embodiment, when the intercept valve V30b is rapidly opened, the hydraulic oil discharged from the booster 94 is directly delivered to the drive device 80b without passing through the servo valve 93, as described above. supplied. Therefore, in the present embodiment, there is no influence of pressure loss or the like in the servo valve 93, so the rapid opening operation can be performed with higher reliability.

<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.

20: High pressure turbine, 30: Reheater, 31: Pressure detector, 40: Intermediate pressure turbine, 50: Low pressure turbine, 60: Condenser, 70: Generator, 71: Detector, 72: Detector, 80a : drive device, 80b: drive device, 81a: operating rod, 81b: operating rod, 82b: piston, 83b: cylinder, 90: hydraulic circuit device, 91: pump, 92: accumulator, 93: servo valve, 94: booster, 100: control device, 301a: valve body, 301b: valve body, 302a: valve stem, 302b: valve stem, 941: primary side cylinder, 942: secondary side cylinder, 943: primary side piston, 944: secondary side piston , 945: connecting rod, C831: internal space, C831a: first oil chamber, C831b: second oil chamber, C941: drive chamber, C941a: first drive chamber, C941b: second drive chamber, C942: pressure increase chamber, C942a: first pressure increasing chamber portion, C942b: second pressure increasing chamber portion, J91: connection portion, J911a: connection portion, J911b: connection portion, J91a: connection portion, J91b: connection portion, J91c: connection portion, J93a: Connection, J942a: Connection, J942b: Connection, L10: Main steam pipe, L20: Low temperature reheat steam pipe, L30: High temperature reheat steam pipe, L40: Crossover pipe, L42: Oil passage, L91: Oil passage, L911: Oil passage, L92: Oil passage, L93a: Oil passage, L93b: Oil passage, L941: Oil passage, L942: Oil passage, L942b: Oil passage, P421: First valve port, P422: Second P423: Third valve port P941: Primary side port P942: Secondary side port P951: First switching valve port P952: Second switching valve port P953: Third switching valve port, P954: fourth switching valve port, R23: orifice, R32: orifice, R42: orifice, S100: opening command signal, S31: detection signal, S71: detection signal, S72: detection signal, V10: main steam valve , V11: check valve (first check valve), V12: check valve (second check valve), V13: check valve (third check valve), V21: check valve (second 1 check valve), V23: check valve (second check valve), V30a: intermediate steam stop valve, V30b: intercept valve, V31: check valve (first check valve), V32: check valve Stop valve (second check valve), V42: switching valve (second switching valve), V95: switching valve (first switching valve)

Claims (4)

A hydraulic circuit device for operating a drive device for driving a steam valve,
a pump for discharging hydraulic oil;
an accumulator internally storing hydraulic oil;
By supplying hydraulic fluid to the primary side port, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary side port and hydraulic fluid discharged by the pump is delivered from the secondary side port. a booster with
a switching valve configured to switch between a state in which the accumulator and the primary side port are blocked and a state in which the accumulator and the primary side port are in communication;
a servo valve that supplies hydraulic oil discharged from the pump to the drive device;
a first check valve interposed between the pump and the servo valve and configured to allow hydraulic oil to flow from the pump side to the servo valve side;
a second check valve interposed between the accumulator and the secondary port and configured to allow hydraulic fluid to flow from the accumulator to the secondary port;
a third check valve interposed between the secondary side port and the servo valve and configured to allow hydraulic oil to flow from the secondary side port side to the servo valve side;
has
When performing a quick opening operation that closes the steam valve more rapidly than when performing a normal opening operation for the steam valve, the switching valve is isolated between the accumulator and the primary port. Hydraulic fluid is supplied from the accumulator to the primary port and hydraulic fluid is supplied from the secondary port to the drive device by switching from the state to the state in which the accumulator and the primary port are in communication. is configured to
When executing the opening operation, the hydraulic oil discharged from the pump is supplied to the driving device via the servo valve, and the pump and the accumulator are communicated through the switching valve. the hydraulic fluid that has flowed from the pump through the switching valve and the hydraulic fluid that has flowed out of the accumulator are supplied to the secondary port through the second check valve,
When executing the rapid opening operation, the hydraulic oil discharged from the secondary port does not flow into the pump and the accumulator through the first check valve and the second check valve, configured to be supplied to the drive device via the third check valve and the servo valve ;
Hydraulic circuit device. A hydraulic circuit device for operating a drive device for driving a steam valve,
a pump for discharging hydraulic oil;
an accumulator internally storing hydraulic oil;
By supplying hydraulic fluid to the primary side port, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary side port and hydraulic fluid discharged by the pump is delivered from the secondary side port. a booster with
a switching valve configured to switch between a state in which the accumulator and the primary side port are blocked and a state in which the accumulator and the primary side port are in communication;
a servo valve that supplies hydraulic oil discharged from the pump to the drive device;
a first check valve interposed between the pump and the servo valve and configured to allow hydraulic oil to flow from the pump side to the servo valve side;
a second check valve interposed between the secondary side port and the servo valve and configured to allow hydraulic oil to flow from the secondary side port side to the servo valve side;
an orifice interposed between the secondary port and the servo valve and provided to bypass the second check valve;
has
When performing a quick opening operation that closes the steam valve more rapidly than when performing a normal opening operation for the steam valve, the switching valve is isolated between the accumulator and the primary port. Hydraulic fluid is supplied from the accumulator to the primary port and hydraulic fluid is supplied from the secondary port to the drive device by switching from the state to the state in which the accumulator and the primary port are in communication. is configured to
When executing the opening operation, the hydraulic fluid discharged from the pump is supplied to the driving device via the servo valve, and the pump and the accumulator are communicated through the switching valve. the hydraulic oil discharged from the pump is supplied to the secondary port through the first check valve and the orifice in sequence without passing through the switching valve,
When executing the rapid opening operation, the hydraulic oil discharged from the secondary side port does not flow into the pump through the first check valve, but passes through the second check valve. configured to be supplied to the driving device;
Hydraulic circuit device. A hydraulic circuit device for operating a drive device for driving a steam valve,
a pump for discharging hydraulic oil;
an accumulator internally storing hydraulic oil;
By supplying hydraulic fluid to the primary side port, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary side port and hydraulic fluid discharged by the pump is delivered from the secondary side port. a booster with
a switching valve configured to switch between a state in which the accumulator and the primary side port are blocked and a state in which the accumulator and the primary side port are in communication;
a servo valve that supplies hydraulic oil discharged from the pump to the drive device;
a first check valve interposed between the pump and the servo valve and configured to allow hydraulic oil to flow from the pump side to the servo valve side;
a second check valve interposed between the secondary side port and the servo valve and configured to allow hydraulic oil to flow from the secondary side port side to the servo valve side;
an orifice interposed between the secondary port and the servo valve and provided to bypass the second check valve;
has
When performing a quick opening operation that closes the steam valve more rapidly than when performing a normal opening operation for the steam valve, the switching valve is isolated between the accumulator and the primary port. Hydraulic fluid is supplied from the accumulator to the primary port and hydraulic fluid is supplied from the secondary port to the drive device by switching from the state to the state in which the accumulator and the primary port are in communication. is configured to
When executing the opening operation, the hydraulic fluid discharged from the pump is supplied to the driving device via the servo valve, and the hydraulic fluid discharged from the pump and the hydraulic fluid flowing out from the accumulator is supplied to the secondary port via the orifice without passing through the switching valve,
When executing the rapid opening operation, the hydraulic oil discharged from the secondary side port does not flow into the pump and the accumulator through the first check valve, and the second check valve is opened. configured to be supplied to the drive device via
Hydraulic circuit device. A hydraulic circuit device for operating a drive device for driving a steam valve,
a pump for discharging hydraulic oil;
an accumulator internally storing hydraulic oil;
By supplying hydraulic fluid to the primary side port, hydraulic fluid having a higher pressure than hydraulic fluid supplied to the primary side port and hydraulic fluid discharged by the pump is delivered from the secondary side port. a booster with
a first switching valve configured to switch between a state in which the accumulator and the primary side port are blocked and a state in which the accumulator and the primary side port are in communication;
a second switching valve that switches between a state in which the accumulator and the secondary port are communicated and a state in which the drive device and the secondary port are communicated;
a servo valve that supplies hydraulic oil discharged from the pump to the drive device;
has
When performing a rapid opening operation for closing the steam valve more rapidly than when performing a normal opening operation for the steam valve, the first switching valve blocks communication between the accumulator and the primary side port. Hydraulic oil is supplied from the accumulator to the primary port, and hydraulic oil is supplied from the secondary port to the drive device by switching from the closed state to the state in which the accumulator and the primary port are in communication. is configured to supply to
When executing the opening operation, the hydraulic fluid discharged from the pump is supplied to the driving device via the servo valve, and the second switching valve is connected to the accumulator and the secondary port. supply hydraulic fluid from the pump via the first switching valve and hydraulic fluid flowing out from the accumulator to the secondary port,
When executing the rapid opening operation, the second switching valve maintains communication between the drive device and the secondary port so that the hydraulic fluid discharged from the secondary port is is configured to be directly supplied to the drive device without going through the servo valve,
Hydraulic circuit device.

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