KR102382145B1 - Gate valve - Google Patents

Abstract

The gate valve of the present invention includes a valve case, a valve body, a rotating shaft, a rotating shaft driving unit, a movable valve unit, a valve case biasing unit, a hydraulic driving unit, a hydraulic pressure generating unit, a driving unit, a power supply, and a first A non-energized actuation brake, a second non-excited actuation brake, and a brake operation release unit for releasing the operations of the first non-excited actuation brake and the second non-excited actuation brake are provided.

Description

gate valve {GATE VALVE}

BACKGROUND OF THE INVENTION Field of the Invention [0001] The present invention relates to gate valves, and more particularly to techniques well suited for use in pendulum valves having a normally closed mechanism.

In a vacuum device, a flow path between two spaces of different vacuum degrees, such as between a chamber and a pipe, between a pipe and a pipe, or between a pipe and a pump, etc., is divided and the two divided spaces are connected. The gate valve is being installed. As such a gate valve, various types of valves are known.

As such a valve, when the valve is closed, the valve body that closes the valve is rotated to block the flow path, and a hydraulically driven expansion/contraction actuator as a biasing part for pressing the valve body against the valve case opening. A pendulum-type gate valve having a

The present inventors have applied for such a gate valve (patent document 1).

Here, the rotation operation of the valve body for opening and closing the valve is performed by driving a motor or the like.

The generation of hydraulic pressure in the expansion/contraction actuator is handled by the motor supplied from the power supply.

In addition, the expansion-contraction drive in the expansion-contraction actuator of this example is a structure performed by the drive by hydraulic pressure and the spring back using a spring in the reverse direction, etc.

As a gate valve, in addition to high reliability in the operation of dividing into a large area, it has been required to enable a normally closed operation of closing the flow path when the power supply is lost.

This normal closing operation enables the operation of closing the flow path in a state in which a power source such as power supplied to drive the valve body or the like is not acting during the valve gate operation, and , which means keeping the flow path closed.

Japanese Patent No. 6358727 Publication

However, the normally closing operation|movement in a pendulum type gate valve is an emergency operation|movement, such as a power failure. Therefore, this emergency such as a power outage occurs when it is not expected.

For this reason, when an emergency such as a power outage occurs, there is a possibility that the flow path serving as the operation position of the valve body may be in a situation that interferes with the operation of the valve body.

For example, when performing a normal closing operation simultaneously with a power failure, there is a possibility that the valve body, which is a pendulum in closed rotation, may strongly collide with a foreign object or the like located in the flow path. In this case, there is a possibility that a fairly strong impact may occur to the valve body or parts such as the valve case.

Alternatively, if the valve body is suddenly rotated when performing the normal closing operation simultaneously with the power failure, there is a possibility that other structures in the chamber communicating with the flow path may be adversely affected.

In addition, the rotational operation of the valve body and the hydraulic operation to the seal position in the direction of the rotation axis of the valve body are sometimes performed by different biasing parts. In this case, in a normal closing operation|movement, after the closing operation|movement to the valve opening shielding position of a valve body is complete|finished, it is necessary to perform the closing operation|movement to the sealing position of a valve body.

When the sequence of the time (timing) for these closing and closing operations is disturbed, the valve may not be in a closed state, or malfunctions such as failure in the vicinity of the valve body may occur.

In addition, in order to realize the normally closed operation in consideration of safety, in the hydraulic drive part, in addition to the normal driving by the hydraulic pressure generated by the motor, the emergency operation by the springback in the case of an emergency power failure in addition to the normal power supply is performed. need to be compatible.

However, when springback is enabled at the time of a power failure, when an emergency operation by springback is performed with respect to a motor for generating hydraulic pressure that has lost power, there are the following problems.

First, the reverse flow of hydraulic pressure by the spring at the time of power failure simultaneously reverses the rotational shaft of the motor in the valve case biasing portion. Then, in the motor reversed in the state where the power supply is lost, a large amount of reverse energy is generated due to inertia.

Here, in the gate valve in which the gate operation with a large area is possible, it is necessary to also make comparatively large the force which presses and seals the valve body. Accordingly, a motor having an extremely large rated current is used to drive the valve body. For this reason, the reversal (kinetic energy expressed by the product of the reverse angular velocity and the moment of inertia) due to the inertia is extremely large. For this reason, the kinetic energy at the end of the springback is released as an impact load, and the cylinder in the hydraulic pressure generating unit overcontracts, resulting in generation of hydraulic pressure higher than expected.

In addition, there has been a demand to prevent the occurrence of inconvenience in the closing operation in an emergency.

In order to solve this problem, immediately after power loss, which is an emergency, the position of the valve body is maintained and, after checking the condition in the flow path, etc., the normally closed operation of the valve is possible even in the state of power loss, and the gate valve There has been a need to improve the certainty of the normal close operation in .

The present invention has been made in consideration of the above circumstances, and aims to achieve the following objects.

1. Maintaining the valve state in an emergency, and then enabling the normally closed operation.

2. To improve the operation certainty of the valve.

3. Aim for space saving, miniaturization, and light weight as a valve.

4. To reduce the effect of valve closing operation at the time of emergency shutoff.

5. To prevent the occurrence of malfunctions, etc. in devices related to gate valves.

The gate valve of the present invention is a gate valve capable of normally closing operation, comprising: a valve case having a hollow part, a first opening and a second opening which are provided to face each other between the hollow part and serve as a communicating flow path, and the flow path; a rotating shaft having an openable and blocking valve body, an axis extending in the flow direction while rotatably supporting the valve body between a retracted position and a valve opening blocking position in the hollow portion; A rotating shaft driving unit having a rotational driving motor capable of rotating and rotating the valve body; a valve case biasing part for moving and closing the movable valve part in the direction of the flow path; a hydraulic driving part for supplying and driving working hydraulic pressure to the valve case biasing part; and a hydraulic pressure generating part for generating hydraulic pressure from the hydraulic driving part; A hydraulic motor driving the hydraulic pressure generating unit and a driving unit having a hydraulic biasing member, a power supply to the rotating shaft driving unit and the driving unit, and a first non-excitation operation for regulating the operation of the rotating driving motor during shearing A brake, a second non-excitation operating brake for regulating the operation of the hydraulic motor during shearing, and a brake operation release unit for releasing the operation of the first non-excitation operating brake and the second non-excitation operating brake are provided. For this reason, the said subject was solved.

In the gate valve of the present invention, the brake operation release unit independently operates the first non-excitation brake for regulating the operation of the rotary drive motor and the second non-excitation brake for regulating the operation of the hydraulic motor. may be released.

In the gate valve of the present invention, the brake operation release unit cancels the operation of the first non-excitation brake that regulates the operation of the rotary drive motor, and then the second non-excitation that regulates the operation of the hydraulic motor You may release the operation of the excitation operated brake.

In the gate valve of this invention, the said brake operation canceling part may be connected to the release control part which can output a release instruction signal based on the information in the said flow path.

Moreover, in the gate valve of this invention, you may judge whether the said cancellation|release control part outputs a cancellation instruction signal based on the information in the said flow path.

In the gate valve of the present invention, the brake operation release unit releases the operation of the second non-excitation operation brake that regulates the operation of the hydraulic motor, and after enabling the hydraulic damper to operate, the operation of the rotation drive motor You may cancel the operation of the said 1st non-excitation operation brake which is regulated.

In the gate valve of this invention, the said brake operation release part may be manually operated.

The gate valve of the present invention is a gate valve capable of normally closing operation, comprising: a valve case having a hollow part, a first opening and a second opening which are provided to face each other between the hollow part and serve as a communicating flow path, and the flow path; a rotating shaft having an openable and blocking valve body, an axis extending in the flow direction while rotatably supporting the valve body between a retracted position and a valve opening blocking position in the hollow portion; A rotating shaft driving unit having a rotational driving motor capable of rotating and rotating the valve body; a valve case biasing part for moving and closing the movable valve part in the direction of the flow path; a hydraulic driving part for supplying and driving working hydraulic pressure to the valve case biasing part; and a hydraulic pressure generating part for generating hydraulic pressure from the hydraulic driving part; a driving unit having a hydraulic motor driving the hydraulic pressure generating unit and a hydraulic biasing member; a power supply to the rotating shaft driving unit and the driving unit; and a second non-energized brake for regulating the operation of the hydraulic motor at the time of operation, and a brake operation release unit for releasing the operations of the first non-excited brake and the second non-excited brake.

For this reason, in the closing operation of the gate valve, at the time of normal feeding, the rotating shaft is rotated by the rotation driving motor of the rotating shaft driving part and the valve body is rotationally driven, while the hydraulic motor and hydraulic pressure in the driving part of the hydraulic pressure generating part are driven. A valve case biasing part is driven by a biasing member, and a valve closing operation|movement is performed.

Further, in an emergency such as loss of power supply from the power source, the first non-excitation brake regulates the operation of the rotational drive motor, while the second non-excited brake regulates the operation of the hydraulic motor to develop the valve body state. can keep

In addition, in an emergency, the operation of the first non-excitation operation brake and the second non-excitation operation brake are canceled by the brake operation release unit, so that the operation of the rotation drive motor regulated by the first non-excitation operation brake and the second operation brake; It becomes possible to cancel the operation|movement of the hydraulic motor which was regulated by the non-excitation operation brake, and to perform a valve closing operation|movement.

For this reason, the positional state of the valve body is maintained for a predetermined time from loss of power supply, and after that, a valve closing operation|movement can be performed after a predetermined|prescribed condition is satisfied. For this reason, it becomes possible to confirm the situation in the flow path by maintaining the state of the valve body, and after that, it is possible to perform a closing operation of the gate valve and provide a gate valve capable of a safe and reliable normal closing operation. .

In the gate valve of the present invention, the brake operation release unit independently operates the first non-excitation brake for regulating the operation of the rotational drive motor and the second non-excitation brake for regulating the operation of the hydraulic motor. makes it possible to release

For this reason, after releasing the restriction|regulation of the operation|movement of a rotation drive motor, the restriction|regulation of the said 2nd non-excitation operation brake which regulates the operation|movement of a hydraulic motor can be cancelled|released. For this reason, the positional state of the valve body is maintained for a predetermined time from loss of power supply, and after that, a valve closing operation|movement can be performed after a predetermined|prescribed condition is satisfied.

At this time, after the valve body rotates, the closing operation can be performed.

In the gate valve of the present invention, the brake operation release unit releases the operation of the first non-excitation brake that regulates the operation of the rotational drive motor, and then the second non-excitation that regulates the operation of the hydraulic motor Release the excitation-actuated brake.

For this reason, after releasing the restriction|regulation of the operation|movement of a rotation drive motor, the operation|movement which cancel|releases the restriction|regulation of the said 2nd non-excitation operation brake which regulates the operation|movement of a hydraulic motor can be performed in order. For this reason, the positional state of the valve body is maintained for a predetermined time from loss of power supply, and after that, a valve closing operation|movement can be performed after a predetermined|prescribed condition is satisfied.

In the gate valve of the present invention, the brake operation release unit is connected to a release control unit capable of outputting a release instruction signal based on the information in the flow passage.

For this reason, the condition in the flow path is confirmed, the release control unit outputs a release instruction signal, and based on the release instruction signal, the brake operation release unit cancels the regulation of the operation of the rotary drive motor. After that, the operation of releasing the regulation of the second non-excitation operation brake that regulates the operation of the hydraulic motor can be sequentially performed. For this reason, after maintaining the positional state of the valve body for a predetermined time from loss of power supply, a valve closing operation can be performed after a predetermined condition is satisfied.

Here, in order to obtain information in the flow path, a sensor or the like may be provided and connected to the brake operation release unit.

Moreover, in the gate valve of this invention, the said release control part judges based on the information in the said flow path whether to output a release instruction signal.

For this reason, the condition in the flow path is confirmed, the release control unit outputs a release instruction signal, and based on the release instruction signal, the brake operation release unit cancels the regulation of the operation of the rotary drive motor. After that, the operation of releasing the regulation of the second non-excitation operation brake that regulates the operation of the hydraulic motor can be sequentially performed.

In the gate valve of the present invention, after the brake operation release unit releases the operation of the second non-excitation operation brake that regulates the operation of the hydraulic motor, and enables the hydraulic damper to operate, the operation of the rotation drive motor Release the operation of the first non-exciter-actuated brake that regulates.

For this reason, at the end of the rotational operation of the valve body, the hydraulic damper (switching valve, spool valve) for relieving the impact can be operated, and the closing operation for relieving the impact can be performed.

In the gate valve of this invention, the said brake operation release part is comprised so that manual operation is possible.

For this reason, an operator etc. confirm the situation in a flow path, and after that, the restriction|regulation of the operation|movement of a rotation drive motor is cancelled|released by manually implementing a brake operation release part. After that, the operation of releasing the regulation of the second non-excitation operation brake that regulates the operation of the hydraulic motor can be sequentially performed.

According to the gate valve of the present invention, it is possible to maintain the valve state in an emergency, and then perform the closing operation after the valve body rotates, and by performing the normal closing operation, the operation reliability of the valve is improved, , it becomes possible to achieve the effect that it is possible to reduce the influence of the valve closing operation at the time of emergency shutoff, and to prevent the occurrence of a failure or the like in the device related to the gate valve.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic sectional drawing along the flow path direction which shows the gate valve which concerns on 1st Embodiment of this invention, and is a figure which shows the case where the valve body is arrange|positioned at the retracted position (valve open position).
It is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve which concerns on 1st Embodiment of this invention.
It is a schematic sectional drawing along the flow path which shows the gate valve which concerns on 1st Embodiment of this invention, It is a figure which shows the case where the valve main body is arrange|positioned at the valve opening blocking position (sliding preparation position).
It is a schematic sectional drawing along the flow path which shows the gate valve which concerns on 1st Embodiment of this invention, and is a figure which shows the case where the valve body is arrange|positioned at the valve closing position.
[ Fig. 5] Fig. 5 is a flow chart showing the normally closed operation of the gate valve according to the first embodiment of the present invention.
Fig. 6 is a cross-sectional view in the direction of the rotation axis for explaining the rotation shaft driving unit in the gate valve according to the second embodiment of the present invention.
It is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve which concerns on 2nd Embodiment of this invention.
It is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve which concerns on 2nd Embodiment of this invention.
It is a schematic explanatory drawing which shows the valve case biasing part in the gate valve which concerns on 2nd Embodiment of this invention.
It is a schematic explanatory drawing which shows the valve case biasing part in the gate valve which concerns on 2nd Embodiment of this invention.
It is sectional drawing orthogonal to the flow path in the gate valve which concerns on 3rd Embodiment of this invention, and shows the retracted position of a valve body, and a valve opening blocking position.
12] It is sectional drawing along the flow path in the gate valve which concerns on 3rd Embodiment of this invention, and shows the valve opening blocking position of a valve body.
[ Fig. 13 ] It is an enlarged cross-sectional view taken along the flow path showing the edge of the valve body in Fig. 12 .
[ Fig. 14] Fig. 14 is a top view of the valve body in the gate valve according to the third embodiment of the present invention as seen from the direction orthogonal to the flow path.
[FIG. 15] It is an enlarged cross-sectional view along the flow path which shows the valve case biasing part, the valve frame biasing part, and the valve plate biasing part in FIG.
Fig. 16 is an enlarged cross-sectional view taken along the flow path showing the edge of the valve body in the gate valve according to the third embodiment of the present invention, and shows the valve closing state by the movable valve frame.
17] It is an enlarged cross-sectional view along the flow path which shows the valve case biasing part, the valve frame biasing part, and the valve plate biasing part in FIG.
Fig. 18 is an enlarged cross-sectional view taken along a flow path showing the edge of the valve body in the gate valve according to the third embodiment of the present invention, and shows the valve closed state in which the reverse pressure is canceled by the movable valve plate part.
[FIG. 19] It is an enlarged cross-sectional view along the flow path which shows the valve case bias part, a valve frame bias part, and a valve plate bias part in FIG.
It is a schematic sectional drawing along the flow path which shows the gate valve which concerns on 4th Embodiment of this invention, It is a figure which shows the case where the valve body is arrange|positioned at the valve opening blocking position (sliding preparation position).
It is a top view which shows the principal part of the gate valve which concerns on 4th Embodiment of this invention, It is a figure which shows the positional relationship between a spool valve and the rotation shaft of a valve body.
It is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve which concerns on 4th Embodiment of this invention.
[Fig. 23] Fig. 23 is a flowchart showing the normally closed operation of the gate valve according to the fourth embodiment of the present invention. It is a schematic diagram which shows the operation|movement of a spool valve, and is a figure which shows the valve open state in which the rod of a spool valve exists in a 2nd position.
It is a schematic diagram which shows the operation|movement of the gate valve in the gate valve which concerns on 5th Embodiment of this invention, and a spool valve, It is a figure which shows the valve open state in which the rod of a spool valve exists in a 2nd position.
It is a schematic diagram which shows the operation|movement of the gate valve in the gate valve which concerns on 5th Embodiment of this invention, and a spool valve, It is a figure which shows the valve closing state in which the rod of a spool valve exists in a 3rd position.
It is a schematic diagram which shows the operation|movement of the gate valve in the gate valve which concerns on 5th Embodiment of this invention, and a spool valve, It is a figure which shows the collision standby state in which the rod of a spool valve exists in a 1st position.
27 is a schematic diagram showing the operation of the gate valve and the spool valve in the gate valve according to the fifth embodiment of the present invention, the dumping state in which the rod of the spool valve starts moving so as to approach the second position from the first position It is a drawing showing
It is a schematic diagram which shows the operation|movement of the gate valve and spool valve in the gate valve which concerns on 5th Embodiment of this invention, It is a figure which shows the dumping state in which the rod of a spool valve moved so that it might approach a 2nd position further.
It is a schematic diagram which shows the operation|movement of the gate valve in the gate valve which concerns on 5th Embodiment of this invention, and a spool valve, It is a figure which shows the moment when the rod of a spool valve reached a 3rd position.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the valve open state in which the rod of a spool valve exists in a 2nd position.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the valve closing state in which the rod of a spool valve is in a 3rd position.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the collision standby state in which the rod of a spool valve exists in a 1st position.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the dumping state in which the rod of a spool valve started moving in the direction closer to the 2nd position than the 1st position. am.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the dumping state in which the rod of a spool valve moved so that it might approach a 2nd position further.
It is a schematic diagram which shows the operation|movement of the spool valve in the gate valve which concerns on 6th Embodiment of this invention, It is a figure which shows the moment when the rod of a spool valve reached a 3rd position.
Fig. 36 is a cross-sectional view in the rotational axis direction for explaining the rotational shaft driving unit in the gate valve according to the seventh embodiment of the present invention.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 1st Embodiment of this invention is demonstrated based on drawing.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic sectional drawing along the flow path direction which shows the gate valve in this embodiment, and is a figure which shows the case where the valve main body is arrange|positioned at the retracted position (valve opening position).

It is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve in this embodiment.

3 : is a schematic sectional drawing along the flow path which shows the gate valve in this embodiment, and is a figure which shows the case where the valve body is arrange|positioned at the valve opening blocking position (sliding preparation position).

4 : is a schematic sectional drawing along the flow path which shows the gate valve in this embodiment, and is a figure which shows the case where the valve main body is arrange|positioned at the valve closing position.

1 to 4, reference numeral 100 denotes a gate valve.

As shown in FIG. 1, the gate valve 100 which concerns on this embodiment is a pendulum type slide valve which can operate normally closed by a springback. As shown in FIGS. 1-4, the gate valve 100 which concerns on this embodiment has the valve case 10, the hollow part 11, the valve body 5, the rotating shaft 20, and the rotating shaft. A driving unit 200 and a hydraulic driving unit 700 (incompressible fluid driving unit) are provided.

The valve case 10 has a hollow portion 11 and a first opening 12a and a second opening 12b that are provided to face each other between the hollow portion 11 and serve as a communication passage H. .

The flow path H is set toward the first opening 12a from the second opening 12b.

The valve body 5 is disposed in the hollow portion 11 of the valve case 10 to open and block the flow path H.

The rotating shaft 20 has an axis line extending in the flow path H direction.

The rotating shaft 20 rotatably supports the valve body 5 between the retracted position in the hollow part 11 and the valve opening blocking position.

In the retracted position, the valve body 5 is retracted from the first opening 12a and is in an open state ( FIG. 1 ) in which the flow path H can be communicated. In the valve opening blocking position, the valve body 5 is set to a blocking possible state ( FIG. 3 ) in which the first opening 12a is blocked.

The gate valve 100 operates between the retracted position and the valve closed position (FIG. 4).

The rotating shaft driving unit 200 is capable of rotating the rotating shaft 20 .

The rotation shaft driving unit 200 is capable of reciprocally rotating the valve body 5 .

The rotation shaft driving unit 200 includes a rotation driving motor 220 .

The rotation drive motor 220 is connected to a power source 227 . The power supply 227 supplies electric power for rotationally driving the rotation shaft 20 to the rotation drive motor 220 .

The rotating shaft drive part 200 has a shear biasing device 230 which rotates the rotating shaft 20 so that the valve body 5 can be brought to the valve closing position at the time of shearing. .

The shear biasing device 230 may be formed of a spring ring type provided with a spring spring having a biasing force.

The shear biasing device 230 is configured to release the mainspring wound at the time of normal energization at the time of shearing.

The rotating shaft drive part 200 is provided with the non-excitation operation brake 221 (1st non-excitation operation brake) which regulates the operation|movement of the rotation drive motor 220 at the time of shearing.

The non-excitation operation brake 221 stops the rotation of the rotation shaft of the rotation drive motor 220 in a state where there is no power supply from the power source 227 .

The rotating shaft driving unit 200 has a brake operation release unit 225f for releasing the operation of the non-excitation brake 221 .

The brake operation release unit 225f cancels the operation when the non-excitation operation brake 221 regulates the operation of the rotation drive motor 220 . That is, it is possible to enable the rotation of the rotation driving motor 220 in a state where there is no power supply from the power source 227 .

In the rotation shaft driving unit 200 , the non-excitation operation brake 221 stops the rotation operation of the rotation driving motor 220 at the time of shearing.

After that, when the operation of the non-excitation brake 221 is released by the brake operation release unit 225f, the rotation shaft 20 is rotated by the shear bias device 230 and the valve body 5 is moved to the valve closing position. do.

The valve body 5 includes a neutral valve part 30 connected to the rotation shaft 20 , a valve frame part 63 connected to the neutral valve part 30 , and a movable valve part connected to the valve frame part 63 . 54) (movable valve plate part).

The neutral valve part 30 is fixed to the rotating shaft 20 .

The neutral valve part 30 maintains the central position in the flow path H direction in the hollow part 11 .

The valve frame part 63 is located around the movable valve part 54 . The valve frame part 63 is fixed to the neutral valve part 30 . The valve frame part 63 maintains the central position of the hollow part 11 together with the neutral valve part 30 in a retracted position, a valve opening blocking position, and a valve closing position.

The movable valve part 54 is made slidably in the flow path H direction with respect to the valve frame part 63. As shown in FIG.

The movable valve part 54 can change the position in the flow path H direction with respect to the valve frame part 63 in a valve opening blocking position and a valve closing position.

The movable valve portion 54 maintains the central position of the hollow portion 11 between the retracted position and the retracted position and the valve opening blocking position.

The movable valve part 54 is provided with the valve plate seal packing which closely_contact|adheres to the inner surface of the valve case 10 located around the 1st opening part 12a.

A valve case biasing part 70 (pressure-reducing cylinder) is embedded in the valve case 10 and provided. A plurality of valve case biasing portions 70 are disposed along the circumferential direction of the movable valve portion 54 .

The valve case biasing part 70 has, as shown in FIGS. 1 and 2 , an expansion and contraction rod 72 (movable part), a biasing member 73 (pressure-reducing spring), and a fixed part 71 .

The movable part 72 (extensible rod) of the valve case biasing part 70 is made expandable and contractible toward the inside of the chamber Ch which consists of a vacuum atmosphere.

The valve case biasing part 70 is arranged so that it is possible to apply a force to the movable part 72 in the direction in which the biasing member 73 is spaced apart from the movable valve part 54 .

In the valve case biasing part 70 , as shown in FIG. 1 , the movable part 72 retracted by the biasing force of the biasing member 73 is separated from the movable valve part 54 , and is attached to the fixed part 71 . are housed

The valve case biasing part 70 is driven by the hydraulic pressure (incompressible fluid) supplied from the hydraulic driving part 700 .

The hydraulic drive unit 700 includes a hydraulic pressure generating unit 701 and a hydraulic pressure pipe 702 . The hydraulic pressure generating unit 701 generates hydraulic pressure for supplying hydraulic pressure to the fixing unit 71 . The hydraulic pressure pipe 702 is connected to the hydraulic pressure generating unit 701 and the fixing unit 71 of the valve case biasing unit 70 .

The hydraulic drive unit 700 is configured to perform a normally closed operation.

The hydraulic pressure generating unit 701 includes a hydraulic pressure biasing member 720 that generates hydraulic pressure to be supplied to the valve case biasing unit 70 by a biasing force.

The hydraulic pressure generating unit 701 supplies, to the valve case biasing unit 70 , the hydraulic pressure in the operating direction by the biasing force of the hydraulic biasing member 720 when the movable part 72 is retracted. The hydraulic pressure generating unit 701 is further configured to maintain the hydraulic pressure state and maintain the movable part 72 in the expanded/contracted state at the end of this operation. Moreover, the contact|abutting state of the movable part 72 to a target object, such as a pressing force, is controllable suitably.

The hydraulic drive unit 700 includes a drive unit 705 , as shown in FIG. 2 .

The driving unit 705 generates a driving force greater than the biasing force of the hydraulic biasing member 720 when the movable part 72 expands and contracts, and flows the hydraulic pressure from the valve case biasing unit 70 to the hydraulic pressure generating unit 701 . It has a hydraulic motor (705m) for driving the hydraulic pressure generating unit (701).

The drive part 705 is provided with the non-excitation operation brake 705b (2nd non-excitation operation brake) which regulates the operation|movement of the hydraulic motor 705m at the time of a front end.

The non-excitation brake 705b stops the rotation of the rotary shaft of the hydraulic motor 705m in a state where there is no power supply from the power source 707 .

The drive unit 705 has a brake operation release portion 705f that cancels the operation of the non-excitation operation brake 705b.

The brake operation release unit 705f cancels the operation of the non-excitation operation brake 705b while regulating the operation of the hydraulic motor 705m. That is, it is possible to enable the rotation of the rotary shaft of the hydraulic motor 705m in a state where there is no power supply from the power source 707 .

The driving unit 705 is connected to and controlled by a control unit (controller) 706 .

The driving unit 705 is connected to a power supply 707 , and electric power for driving the driving unit 705 is supplied.

The valve case biasing unit 70 generates a driving force greater than the biasing force of the biasing member 73 by the operating hydraulic pressure supplied from the hydraulic driving unit 700 to drive the movable unit 72 .

The valve case biasing part 70 is made to be spring-backed by the hydraulic drive part 700 .

Springback means that hydraulic oil flows from the hydraulic pressure generating unit 701 to the valve case biasing unit 70 by the biasing force of the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701, and the operating direction by the hydraulic motor 705m and driving the movable part 72 in the reverse direction.

In this embodiment, at the time of normal feeding, the valve case biasing part 70 is driven by the hydraulic pressure supplied by the hydraulic drive part 700, and by retracting the movable part 72, it is pressed against the movable valve part 54. turn off

Moreover, in the hydraulic drive system, the movable part 72 is extended by the biasing force of the hydraulic pressure biasing member 720 of the hydraulic pressure generating part 701 in the valve case biasing part 70, and the movable valve part 54 is pressed. (押壓).

This is called a springback by the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701 .

In the hydraulic drive unit 700 , the non-excitation brake 705b stops the rotational operation of the hydraulic motor 705m at the time of shearing.

Thereafter, the operation of the non-excitation operation brake 705b is released by the brake operation release unit 705f.

Then, hydraulic oil flows from the hydraulic pressure generating unit 701 to the valve case biasing unit 70 by the hydraulic biasing member 720 . For this reason, the movable part 72 is extended, and the movable valve part 54 is pressed.

In the valve case biasing portion 70 , the chamber Ch serving as the vacuum side on which the telescopic rod 72 extends is the hollow portion 11 communicating with the flow passage H.

The valve case biasing part 70 built in the valve case 10 is connected to a hydraulic drive part 700 installed on the atmospheric side and is driven by hydraulic pressure.

The hydraulic drive unit 700 simultaneously supplies and discharges an incompressible fluid (pressure oil) to the plurality of valve case biasing units 70 . That is, the hydraulic drive unit 700 simultaneously drives the plurality of valve case biasing units 70 .

The valve case biasing portion 70 applies a force to the movable valve portion 54 toward the first opening 12a in the flow path H direction in the valve opening blocking position and the valve closing position. The valve case biasing portion 70 has a function of enabling the valve plate seal packing to be closely attached to the inner surface of the valve case 10 positioned around the first opening 12a.

The valve case biasing part 70 presses the periphery of the movable valve part 54 in the valve opening blocking position in the flow path H direction. The valve case biasing part 70 closes (closes) the flow path H by the movable valve part 54 which has moved.

In addition, although not shown in the valve frame part 63 or the movable valve part 54, the central position of the hollow part 11 in the flow path H direction with the movable valve part 54 with respect to the valve frame part 63. A biasing portion (neutral biasing portion) for applying a force toward

Moreover, in the gate valve 100 which concerns on this embodiment, when the valve case biasing part 70 is not operating, the movable valve part 54 is the hollow part 11 inside the valve case 10. It has a mechanism to hold it in its central position. The flow path between the valve frame part 63 and the movable valve part 54 between the valve opening blocking position and the valve closing position by the biasing part (neutral bias part) of the valve case biasing part 70 and the valve frame part 63. The thickness dimension in (H) direction is adjustable.

When the rotating shaft 20 rotates in a direction intersecting the direction of the flow path H, the neutral valve part 30 fixed to the rotating shaft 20 also rotates integrally with this rotation. In addition, since the movable valve part 54 is slidable only in the thickness direction to the neutral valve part 30, the movable valve part 54 rotates integrally with the neutral valve part 30.

By rotating the neutral valve unit 30 by the rotation shaft driving unit 200, the flow path ( In the valve opening blocking position for blocking H), the movable valve portion 54 moves in pendulum motion.

In the present embodiment, the fixing portion 71 of the valve case biasing portion 70 is incorporated in the valve case 10 . The valve case biasing part 70 is arranged so that it is possible to apply a force to the movable part 72 in the direction in which the biasing member 73 is spaced apart from the movable valve part 54 .

In the valve case biasing part 70, as shown in FIGS. 1 and 3, the movable part 72 retracted by the biasing member 73 is spaced apart from the movable valve part 54, and the valve case ( 10) is accommodated in the fixed part 71 built-in.

Here, in the valve case biasing part 70 , hydraulic pressure is supplied from the hydraulic pressure driving part 700 by the hydraulic pressure biasing member 720 of the hydraulic pressure generating part 701 from the retracted storage state (spring back), and the movable part 72 ) is elongated.

At this time, the valve case biasing part 70 moves the movable valve part 54 toward the 1st opening part 12a by the movable part 72, and the movable valve part 54 is moved of the valve case 10. in contact with the inside. Moreover, the valve case biasing part 70 presses the movable valve part 54 against the inner surface of the valve case 10 to make it a closed state, and closes the flow path H (valve closing operation|movement).

From the extended state of the movable part 72 , the valve case biasing part 70 is activated by releasing the hydraulic pressure supplied from the hydraulic driving part 700 by the driving of the hydraulic motor 705m of the driving part 705 . ) degenerate the tip. At this time, the biasing part (neutral biasing part) separates the movable valve part 54 from the 1st opening part 12a.

For this reason, the movable valve part 54 is separated from the inner surface of the valve case 10 and is retracted. By making the movable valve part 54 into the central position of the hollow part 11 in the flow path H direction, the flow path H is opened (release operation|movement).

In this way, the valve closing operation and the valve releasing operation are made possible by the mechanical contact operation and the mechanical separation operation in the valve case biasing portion 70 . Here, the mechanical abutting operation in the valve case biasing portion 70 is an operation of bringing the movable valve portion 54 into contact with the inner surface of the valve case 10 . The mechanical separation operation in the valve case biasing portion 70 is an operation in which the movable valve portion 54 is separated from the inner surface of the valve case 10 by the biasing portion (neutral biasing portion).

After this release operation, the rotating shaft 20 is rotationally driven by the rotating shaft driving unit 200 (retraction operation), and the neutral valve unit 30 and the movable valve unit 54 also rotate integrally with this rotation.

The gate valve 100 performs the valve-opening operation|movement which makes the movable valve part 54 retract from a valve opening blocking position to a retraction position by this release operation|movement and a retraction operation|movement, and makes a valve open state. The rotating shaft driving unit 200 is configured to allow a normally closed operation.

The valve case biasing part 70 is driven by the hydraulic pressure supplied from the hydraulic driving part 700 .

The hydraulic drive unit 700 may further include a switching sensor 802 capable of switching the hydraulic pressure supply by detecting that the rotation of the rotary shaft 20 is at the valve closing position and the valve opening closing position.

The hydraulic drive unit 700 is configured such that a normally closed operation by springback is possible by the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701 .

The hydraulic driving unit 700 moves hydraulic oil from the valve case biasing unit 70 to the hydraulic pressure generating unit 701 by the hydraulic motor 705m of the driving unit 705 when the movable unit 72 is retracted.

The hydraulic driving unit 700 causes the hydraulic pressure generated by the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701 to flow back to the valve case biasing unit 70 when the movable unit 72 is extended.

The hydraulic drive unit 700 is capable of maintaining the hydraulic state in which the movable unit 72 is expanded and contracted upon completion of the operation.

The hydraulic drive unit 700 can appropriately control the contact state of the movable unit 72 with the movable valve unit 54 .

At the time of normal energization in this embodiment, in the gate valve 100, as shown in FIG. 1, the movable valve part 54 is a retracted position, and it consists of a state in which the flow path H expands and can distribute|circulate.

Moreover, while the movable valve part 54 closes rotation operation from the retracted position shown in FIG. 1 to the valve opening blocking position shown in FIG. 3 by the rotating shaft drive part 200, the flow path H is partially movable. It is covered by the valve part 54 . In this case, the first opening 12a and the second opening 12b communicate with each other through a part of the flow path H.

In addition, immediately after the movable valve part 54 reaches the valve opening blocking position shown in FIG. 3, although the flow path H is blocked by the movable valve part 54, it is not sealed. In this case, the 1st opening part 12a and the 2nd opening part 12b communicate through the space in the vicinity of the periphery of the movable valve part 54. As shown in FIG.

Moreover, when spring-backed by the hydraulic pressure biasing member 720 of the hydraulic pressure generating part 701, in the valve case biasing part 70, the movable part 72 is extended-drive.

For this reason, the movable valve part 54 performs the sealing operation|movement which changes the position in the flow path H direction. For this reason, the movable valve part 54 slides from the valve opening blocking position shown in FIG. 3 to the valve closing position shown in FIG. 4, and the flow path H is blocked.

Next, when the hydraulic motor 705m of the driving unit 705 in the hydraulic driving unit 700 is driven, the movable valve unit 54 is driven by degenerate driving of the movable unit 72 in the valve case biasing unit 70 . An opening operation of changing the position in the flow path H direction is performed. For this reason, the movable valve part 54 slides from the valve closing position shown in FIG. 4 to the valve opening blocking position shown in FIG. At this time, the flow path H is partially covered by the movable valve part 54, and the 1st opening part 12a and the 2nd opening part 12b communicate through a part of the flow path H.

In addition, immediately after the movable valve part 54 starts sealing releasing operation|movement (separation operation|movement) from the valve closing position shown in FIG. 4, sealing of the flow path H is canceled and the vicinity of the periphery of the movable valve part 54. Through the space of , the first opening 12a and the second opening 12b communicate. At the same time, although the flow path H is blocked by the movable valve part 54, it will be in the state which is not sealed.

In addition, during the open rotation operation of the movable valve unit 54 from the valve opening blocking position shown in FIG. 3 to the retracted position shown in FIG. 1 , the flow path H is partially covered by the movable valve unit 54 . . In this case, the first opening 12a and the second opening 12b communicate with each other through a part of the flow path H.

In addition, during the rotational operation of the movable valve part 54 , the valve case biasing part 70 maintains the retracted state of the movable part 72 , and the extension driving of the movable part 72 is not performed.

Next, operation of the gate valve 100 at the time of shearing is demonstrated.

5 : is a flowchart which shows the normally closing operation|movement in the gate valve in this embodiment.

When the gate valve 100 in this embodiment exists in the valve opening blocking position shown in FIG. 3 at the time of a front end, this valve opening blocking position state is maintained.

Here, when the valve main body 5 in the gate valve 100 is located between the valve opening blocking position shown in FIG. 3 to the retraction position shown in FIG. 1, let this state be a valve circulation state.

First, as operation|movement at the time of shearing in the gate valve 100 of this embodiment, in step S00 shown in FIG. 5, the case where it was a valve circulation state is considered.

As for the operation at the time of shearing in the gate valve 100 of this embodiment, a blackout generate|occur|produces in step S01 shown in FIG. In this step S01, the power supply from the power supply 227 to the rotation drive motor 220 is stopped. At the same time, in step S01, power supply from the power source 707 to the hydraulic motor 705m is stopped.

Then, in step S02 shown in FIG. 5, the non-excitation operation brake 221 and the non-excitation operation brake 705b act|operate.

For this reason, the operation|movement of the rotation drive motor 220 is regulated by the operation|movement of the non-excitation operation brake 221 in step S03a shown in FIG.

At the same time, the operation of the non-excitation operation brake 705b regulates the operation of the hydraulic motor 705m in step S03b shown in FIG. 5 .

For this reason, the state of the valve body 5 is maintained. That is, the valve body 5 is hold|maintained at several positions between the valve opening blocking position shown in FIG. 3 to the retracted position shown in FIG.

These steps S03a and S03b are emergency operations, and are performed simultaneously with step S02.

Next, in step S04 shown in FIG. 5, the situation in the flow path H is confirmed. Here, the status check in the flow path H confirms whether or not there is a problem with closing the flow path H (valve closing operation) with the gate valve 100 that has been stopped urgently.

Specifically, it is checked whether or not there is an obstacle obstructing the operation of the valve body 5 in the rotational operation range (rotational operation region) for moving the valve body 5 from the retracted position to the valve opening blocking position in pendulum motion. Check (check the presence of obstacles).

Alternatively, when the movable valve part 54 is pressed against the inner surface of the valve case 10 and the flow path H is closed (valve closing operation), the inner surface of the movable valve part 54 and the valve case 10 is performed. In between the steps, the presence or absence of an obstacle that obstructs the operation of the movable valve unit 54 is checked.

Moreover, when the flow path H is closed, the presence or absence of the obstacle which generate|occur|produces in the both sides of the valve body 5, ie, upstream and downstream in the flow path H, is confirmed.

In this embodiment, a worker can perform the status check in the flow path H in this step S04.

Next, in step S05 shown in FIG. 5, the brake operation release part 225f is actuated.

Then, in step S06 shown in FIG. 5 , the brake operation release unit 225f cancels the operation of the non-excitation operation brake 221 .

Due to this, the rotation of the rotation driving motor 220 is possible.

At the same time, by the operation of the brake operation release unit 225f, in step S07 shown in Fig. 5, the shear biasing device 230 operates.

For this reason, the shear biasing device 230 releases the mainspring wound at the time of normal energization.

By the biasing force of the spring, the shear biasing device 230 rotates the rotating shaft 20 so that the valve body 5 can be brought to the valve closing position even during shearing.

For this reason, in step S08 shown in FIG. 5, the valve body 5 is moved to a valve opening blocking position by pendulum motion.

After the valve body 5 is positioned at the valve opening blocking position, in step S10 shown in Fig. 5 , the brake operation release unit 705f is actuated. Then, in step S11 shown in FIG. 5, the brake operation canceling part 705f cancels the operation|movement of the non-excitation operation brake 705b.

For this reason, rotation of the hydraulic motor 705m becomes possible.

Then, in step S12 shown in FIG. 5, the hydraulic drive part 700 operates. Specifically, in step S13 , hydraulic oil flows from the hydraulic pressure generating unit 701 to the valve case biasing unit 70 by the biasing force of the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701 . For this reason, the movable part 72 is extended in the direction opposite to the operation direction by the hydraulic motor 705m.

Then, in step S14 shown in FIG. 5, the movable valve part 54 is pressed against the inner surface of the valve case 10 by the movable part 72, and the flow path H is closed (valve closing operation|movement).

As a result, the gate valve 100 of the present embodiment completes the springback operation in an emergency such as loss of power supply from the power sources 707 and 227 .

In the present embodiment, the operation release of the non-excitation operation brake 221 of the brake operation release unit 225f in step S06 and the operation release of the non-excitation operation brake 705b of the brake operation release unit 705f in step S11 are released. is done independently.

Incidentally, these steps S11 and S06 can also be performed manually by an operator.

That is, the operation release of the non-excitation operation brake 221 of the brake operation release unit 225f and the operation release of the non-excitation operation brake 705b of the brake operation release unit 705f can be manually operated.

Here, the status check in the flow path H in step S04 may be performed before the operation of the brake operation release unit 705f in step S10.

The gate valve 100 of the present embodiment can release the restriction on the operation of the hydraulic motor 705m after releasing the restriction on the operation of the rotation drive motor 220 . For this reason, the positional state of the valve body 5 is maintained for a predetermined time from the loss of power supply in step S01. Thereafter, it becomes possible to perform the valve closing operation after a predetermined condition is satisfied.

In addition, by confirming the situation in the flow path H in step S04, it is possible to prevent the occurrence of new inconvenience in an emergency.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 2nd Embodiment of this invention is demonstrated based on drawing.

6 is a cross-sectional view in the rotational axis direction for explaining the rotational shaft driving unit of the oil gate valve in the present embodiment.

What is different from the first embodiment described above with respect to this embodiment is the point regarding the rotating shaft drive part, the hydraulic pressure generating part, and the valve case biasing part. .

The rotary shaft drive unit 200 in this embodiment is configured to have a function equivalent to that of the rotary shaft drive unit 200 in the first embodiment described above.

The rotating shaft driving unit 200 for rotating the rotating shaft 20 is made of an electric actuator.

As shown in FIG. 6 , the rotary shaft drive unit 200 includes a planetary gear clutch 210 connected to the rotary shaft 20 , a rotary drive motor 220 connected to the planetary gear clutch 210 as a driving source, and a planetary gear clutch. It has a shear biasing device 230 connected to 210 , a rotation switching device 240 , and a return device.

The rotating shaft drive unit 200 sets the neutral valve body (valve body) 5 to the valve closing position at the time of shearing (when the supply of driving power is cut off).

The rotating shaft driving unit 200 is configured to sequentially operate the rotating operation of the rotating shaft 20 and the closing operation of the valve case biasing unit 70 .

The shear biasing device 230 has a spring ring type provided with a spring 231 having a biasing force.

The shear biasing device 230 is configured to release the mainspring 231 wound during normal energization at the time of shearing.

At this time, the front-end biasing device 230 rotates the rotating shaft 20 so that the neutral valve body 5 can be brought to the valve closing position by the biasing force of the spring 231 .

The rotation switching device 240 is configured to be capable of switching a state of connection to a drive source for rotationally driving the rotation shaft 20 at the time of energization and shearing.

Specifically, during normal energization (when driving power is supplied), the rotation shaft 20 is rotationally driven by the rotation drive motor 220 .

In addition, at the time of shearing which is not normal (when supply of drive electric power is interrupted|blocked), the rotating shaft 20 is rotationally driven by the shear biasing device 230.

The restoration device has a function of returning the shear biasing device 230 from which the biasing force is released at the time of shearing to the restored state in which the torque is stored at the shear recovery in which the energization is restored from the shearing state.

In addition, these shear biasing apparatus 230, the rotation switching apparatus 240, and the return apparatus may have a mutually common structure.

Specifically, it has a planetary gear clutch (planetary gear-type clutch) 210 as the rotating shaft drive part 200 .

The planetary gear clutch 210 includes a driving gear 211, a sun gear 212, a plurality of planetary gears 213, an inner tooth gear 214, a flange portion 215, and a casing ( 201).

The drive gear 211 rotates by driving the rotation drive motor 220 .

The drive gear 211 is rotatably mounted on the outer periphery of the rotating shaft 20 .

The sun gear 212 is integrally formed with the drive gear 211 . The sun gear 212 is rotatably mounted on the outer periphery of the rotation shaft 20 .

The planet gear 213 is located on the outer side in the radial direction of the rotation shaft 20 with respect to the sun gear 212 .

A plurality of planetary gears 213 are provided in the circumferential direction of the rotating shaft 20 .

The plurality of planetary gears 213 are all arranged to mesh with the sun gear 212 .

The inner tooth gear 214 is rotatably mounted on the outer periphery of the rotating shaft 20 .

The inner tooth gear 214 has inner peripheral teeth 214a facing the inner side of the radial direction of the rotation shaft 20 .

The inner tooth gear 214 is meshed with each planetary gear 213 by the inner main teeth 214a.

The inner tooth 214a of the inner tooth gear 214 is located on the outer side in the radial direction of the rotation shaft 20 with respect to each planetary gear 213 .

The flange part 215 is connected so that it may stick out in the outer peripheral direction of the rotating shaft 20. As shown in FIG.

The flange portion 215 rotates integrally with the rotating shaft 20 .

One end of the support shaft 213c passing through each planetary gear 213 is rotatably attached to the flange portion 215 .

The rotating shaft 20 serves as an output shaft of the planetary gear clutch 210 .

The sun gear 212 and the driving gear 211 are connected by the sleeve 211a through the rotation shaft 20 .

The outer periphery of the inner tooth gear 214, the outer tooth (214b) is installed.

The inner tooth gear 214 is connected so that the outer tooth (214b) and the inner relay (內中繼) gear 233 mesh with each other.

The internal relay gear 233 is rotatably mounted on the outer periphery of the mainspring shaft 231c.

The mainspring shaft 231c is disposed in a position parallel to the rotation shaft 20 .

The internal relay gear 233 is integrally formed with the external relay gear 234 coaxial with the mainspring shaft 231c.

The external relay gear 234 is rotatably mounted on the outer periphery of the mainspring shaft 231c.

In the external relay gear 234 , a small scale gear 243 meshes with each other.

The critical gear 243 is rotatably mounted on the outer periphery of the brake shaft 241c.

The brake shaft 241c is disposed at a position parallel to the rotation shaft 20 and the mainspring shaft 231c.

The large-scale gear 243 is integrally formed with the large-scale gear 244 coaxial with the brake shaft 241c.

As for the mass system gear 244, the mainspring gear 235 meshes with each other.

The mainspring gear 235 is integrally formed with the mainspring gear 236 coaxial with the mainspring shaft 231c.

The small mainspring gear 235 and the mainspring gear 236 rotate integrally with the mainspring shaft 231c.

A brake gear 245 meshes with the mainspring gear 236 .

The brake gear 245 rotates integrally with the brake shaft 241c.

A spring 231 is connected to the mainspring shaft 231c.

The mainspring shaft 231c is made drivable by the mainspring spring 231 with the biasing force released.

The winding shaft 231c is provided with a hoisting stop 231d so that the winding stops in a constant state when the spring 231 is wound up.

A sensor 250 for detecting that the mainspring 231 is sufficiently wound is provided on the mainspring shaft 231c.

The sensor 250 is connected to the excitation-actuated brake 241 so as to output a detection signal.

An excitation-actuated brake 241 is connected to the brake shaft 241c as a rotation switching device 240 that releases the wound spring 231 at the time of shearing.

The spring 231 is made of a torque storage unit.

The spring 231 rotates the rotating shaft 20 via a relay gear unit when the biasing force is released. For this reason, the rotating shaft drive part 200 is comprised so that the valve body 5 can be made into a valve closing position.

The excitation-operated brake 241 exerts a brake function with respect to the mainspring 231 when energized. For this reason, the rotation of the mainspring shaft 231c is stopped at the time of energization.

The excitation-actuated brake 241 releases the brake function with respect to the spring 231 at the time of shearing, and releases the biasing force of the mainspring 231 . For this reason, at the time of shearing, the mainspring shaft 231c is made rotatable.

A non-excitation brake 221 is connected to the rotation drive motor 220 .

The non-excitation operation brake 221 exerts a brake function at the time of shearing, and stops the rotation of the rotation drive motor 220 .

The non-excitation operation brake 221 releases the brake function when energized, and enables the rotational drive motor 220 to be rotationally driven. The non-excitation operation brake 221 is connected to the brake operation release part 225f.

In addition, the rotation drive motor 220 may be accompanied by the gear unit which adjusts a torque and rotation speed, and the motor unit for control other than the said structure.

Moreover, the stopper 21 which regulates a rotation position is provided in the rotation shaft 20. As shown in FIG.

The stopper 21 restricts the rotation shaft 20 so that rotation is possible between the valve closing position and the valve opening position.

A switching valve 704 for detecting that the neutral valve body 5 has reached the valve closing position is connected to the stopper 21 . When the switching valve 704 is turned on, as will be described later, the hydraulic pressure supplied from the connected hydraulic drive unit 700 decreases in the fixed portion 71, thereby extending the movable portion 72 of the valve case biasing portion 70. It can be driven in the closing direction.

When the rotary shaft drive unit 200 is energized normally (the driving power is supplied), the excitation-actuated brake 241 exerts a brake function and maintains this state.

In addition, the spring 231 is maintaining the wound state.

At the same time, during normal energization, the non-excitation operation brake 221 does not have a brake function. Accordingly, the driving force of the rotational drive motor 220 is capable of rotating the rotational shaft 20 via the planetary gear clutch 210 .

Specifically, in the rotating shaft driving unit 200 , the excitation-actuated brake 241 maintains a state in which the rotation of the brake shaft 241c is stopped.

In this state, the rotation of the brake gear 245 integral with the brake shaft 241c is maintained in a stopped state.

For this reason, the brake gear 245 and the mainspring gear 236 meshing with each other, the mainspring gear 236 and the mainspring gear 235 and the mainspring shaft 231c integrated with each other are all in a state in which rotation is stopped. keep

At the same time, the small-winding gear 235 and the large-scale gear 244 meshing with each other, the large-scale gear 244 and integral large-scale gear 243, the small-scale gear 243 and the external relay gear 234 meshing with each other ), the external relay gear 234 and the integral internal relay gear 233 maintain a state in which rotation is stopped.

In addition, in the same way, the inner gear 214 meshed with each other to the inner relay gear 233 and the outer tooth 214b, the rotation is maintained in a stopped state.

In this state, when the rotation drive motor 220 is driven, in the planetary gear clutch 210 , the drive gear 211 is rotationally driven.

Then, the sun gear 212 integral with the drive gear 211 rotates.

In addition, the planet gear 213 meshing with the sun gear 212 rotates.

At this time, the planetary gear 213 rotates around the axis of the support shaft 213c.

When the planetary gear 213 rotates, the rotation of the inner-tooth gear 214 is stopped. At this time, since the planetary gear 213 meshes with the inner tooth 214a and the inner tooth gear 214 with each other, the planet gear 213 rotates in the circumferential direction of the inner tooth gear 214 .

It follows the planetary gear 213 which moves in the circumferential direction of this inner-tooth gear 214, and the flange part 215 rotates.

For this reason, the rotating shaft 20 formed integrally with the flange part 215 rotates.

In addition, at the time of shearing (when the supply of driving power is cut off), in a state in which the brake operation release unit 225f is operated, the excitation-actuated brake 241 maintains a state in which the rotation of the brake shaft 241c is stopped. keep

In this state, the rotation of the brake gear 245 integral with the brake shaft 241c is maintained in a stopped state.

For this reason, the brake gear 245 and the mainspring gear 236 meshing with each other, the mainspring gear 236 and the mainspring gear 235 and the mainspring shaft 231c integrated with each other are all in a state in which rotation is stopped. keep

At the time of shearing (when the supply of driving power is cut off), in the state in which the operation of the brake operation release unit 225f is released, the non-excitation operation brake 221 functions as a brake in the rotation shaft driving unit 200 . . For this reason, it becomes a state in which the rotation drive motor 220 does not drive.

For this reason, the rotation of the drive gear 211 will be in the stopped state. At the same time, the rotation of the sun gear 212 formed integrally with the driving gear 211 is stopped.

In addition, at the time of shearing (when the supply of driving power is cut off), the brake function of the excitation-actuated brake 241 does not function in a state in which the operation of the brake operation release unit 225f is released.

For this reason, the brake shaft 241c will be in a rotatable state.

Then, the brake gear 245 formed integrally with the brake shaft 241c is in a rotatable state.

For this reason, the brake gear 245 and the mainspring gear 236 meshed with each other are in a rotatable state. In addition, the mainspring gear 236 and the small mainspring gear 235 and the mainspring shaft 231c integrated with each other are in a rotatable state.

Then, the biasing force of the wound spring 231 is released, and the mainspring shaft 231c rotates.

With the rotation of the mainspring shaft 231c, the mainspring gear 235 integrally formed with the mainspring shaft 231c rotates.

In accordance with the rotation of the small winding gear 235, the small winding gear 235 and the large-scale gear 244 meshed with each other, the large-scale gear 244 and the integral small-scale gear 243 all rotate.

In addition, the external relay gear 234 meshed with the critical gear 243, the external relay gear 234 and the integral internal relay gear 233 are all rotated.

For this reason, the inner-tooth gear 214 meshed with the internal relay gear 233 and the outer peripheral teeth 214b rotates.

By rotation of the inner tooth gear 214, the inner tooth gear 214 and the planetary gear 213 meshed with the inner main tooth 214a rotates about the axis of the support shaft 213c.

At this time, the rotation of the sun gear 212 is stopped. For this reason, the sun gear 212 and the planet gear 213 meshed with each other move in the circumferential direction of the sun gear 212 .

Following the planet gear 213 moving in the circumferential direction of this sun gear 212, the flange part 215 rotates.

For this reason, the rotating shaft 20 formed integrally with the flange part 215 rotates.

In this way, at the time of shearing, in the state in which the brake operation release unit 225f is operated in the rotating shaft driving unit 200, the wound spring 231 is released, and the rotating shaft 20 rotates to the valve closing position. .

Following the rotation of the rotation shaft 20, the stopper 21 integrally formed with the rotation shaft 20 rotates to the valve closing position.

When the rotation shaft 20 and the stopper 21 come to the valve closing position, the stopper 21 will contact|abut the switching valve 704 mentioned later. Then, the selector valve 704 mentioned later turns ON, and the movable part 72 of the valve case biasing part 70 is driven in the extending|stretching closing direction, and it becomes a valve closing state.

When returning from the shearing state, it is in the state which can energize.

For this reason, the non-excitation operation brake 221 is made in the state in which a brake function does not function.

Accordingly, the driving force of the rotational drive motor 220 is capable of rotating the rotational shaft 20 via the planetary gear clutch 210 .

At the time of shear recovery from the shear state to the normal energized state, in the rotary shaft drive unit 200, first, the brake operation release unit 225f is operated, and the excitation-actuated brake 241 has a brake function keep not doing

For this reason, the brake shaft 241c maintains the rotatable state.

Then, the brake gear 245 integrally formed with the brake shaft 241c maintains a rotatable state.

For this reason, the brake gear 245 and the mainspring gear 236 meshed with each other are in a rotatable state.

In addition, the mainspring gear 236 and the small mainspring gear 235 and the mainspring shaft 231c integrated with each other are in a rotatable state.

The mainspring gear 235 integrally formed with the mainspring shaft 231c is in a rotatable state.

The small winding gear 235 and the mass system gear 244 meshed with each other, the mass system gear 244 and the integral small system gear 243 are all in a rotatable state.

In addition, the external relay gear 234 meshed with the critical gear 243, the external relay gear 234 and the integral internal relay gear 233 are all in a rotatable state.

The inner tooth gear 214 meshing with each other to the inner relay gear 233 and the outer tooth 214b is in a rotatable state.

In this state, when the rotation drive motor 220 is driven, in the planetary gear clutch 210 , the drive gear 211 is rotationally driven.

Then, the sun gear 212 integral with the drive gear 211 rotates.

In addition, the planet gear 213 meshing with the sun gear 212 rotates.

At this time, the planetary gear 213 rotates around the axis of the support shaft 213c.

In this state, the flange portion 215 and the rotating shaft 20 do not rotate due to the weight of the valve body 5 . Accordingly, by the rotation of the driving gear 211 , the inner tooth gear 214 rotates through the sun gear 212 and the planetary gear 213 .

Then, the internal transmission gear 233 meshed with each other to the inner tooth gear 214 and the outer tooth 214b rotates.

As the internal relay gear 233 rotates, the internal relay gear 233 and the integral external relay gear 234 rotate.

In addition, the external gear 234 and the primary gear 243 meshing with each other, the primary gear 243 and the integrated mass system gear 244, the mass system gear 244 and the small winding gear 235 meshing with each other ), all rotate.

In accordance with the rotation of the mainspring gear 235, the mainspring shaft 231c integral with the mainspring gear 235 rotates.

When the mainspring shaft 231c rotates, the connected mainspring 231 is wound.

At the same time, as the mainspring gear 235 rotates, the mainspring gear 236 integrally with the mainspring gear 235 rotates. As the mainspring gear 236 rotates, the brake shaft 241c rotates.

When the spring 231 can be sufficiently wound and the state is sufficient to bring the neutral valve body 5 to the valve closed position at the time of shearing, this is detected by the sensor 250, and the excitation-operated brake 241 brakes function to function.

The rotation of the brake shaft 241c is stopped by the brake function of the excitation-operated brake 241 .

For this reason, the brake gear 245 integral with the brake shaft 241c, the mainspring gear 236 meshing with the brake gear 245, and the mainspring gear 236 and the mainspring shaft 231c integral with each other, In all cases, the rotation is stopped.

For this reason, the state in which the spring 231 is fully wound is maintained, and it becomes a standby state with respect to shear generation|occurrence|production.

Moreover, the rotation of the small winding gear 235 integrally with the large winding gear 236 is in the stopped state.

For this reason, the small winding gear 235 and the mass gear 244 meshing with each other, the mass gear 244 and the integral gear 243, the minor gear 243 and the external gear meshing with each other ( 234), the external relay gear 234 and the integral internal relay gear 233 are in a state in which rotation is stopped.

In addition, the inner-tooth gear 214 meshing with each other to the inner relay gear 233 and the outer peripheral teeth 214b is in a state in which rotation is stopped.

When the rotation drive motor 220 is driven in this state, the driving force of the rotation drive motor 220 is transmitted to the rotation shaft 20 and it becomes possible to rotate the neutral valve body 5 .

At the start of energization (at the time of shear recovery), the operation of winding the mainspring 231 by driving the rotational drive motor 220 without the excitation-actuated brake 241 functioning is a recovery device.

7 : is a schematic explanatory drawing which shows the hydraulic pressure generating part of the pressurized state in the hydraulic drive part of the gate valve in this embodiment.

It is a schematic explanatory drawing which shows the hydraulic pressure generating part of the hydraulic drive part pressure-reduced state of the gate valve in this embodiment.

The hydraulic drive unit 700 in the present embodiment has a configuration equivalent to that of the hydraulic drive unit 700 in the first embodiment described above.

The hydraulic pressure generating unit 701 includes a hydraulic cylinder 710 , a hydraulic pressure biasing member 720 , a cylinder driving unit 730 , and a casing 750 , as shown in FIGS. 7 to 8 .

The hydraulic cylinder 710 pressurizes and supplies pressure oil, which is an incompressible fluid, to the valve case biasing portion 70 . The hydraulic biasing member 720 applies a force to the hydraulic cylinder 710 and enables a springback operation.

The cylinder driving unit 730 may drive the hydraulic cylinder 710 against the hydraulic biasing member 720 . The casing 750 accommodates these hydraulic cylinders 710 , the hydraulic biasing member 720 , and the cylinder driving unit 730 .

The hydraulic cylinder 710 includes a user cylindrical cylinder body 711 and a piston 712 relatively movable in the axial direction inside the cylinder body 711 . The piston 712 has a hydraulic oil passage 713 penetrating the inside along its axis line, and the hydraulic oil passage 713 is connected to the hydraulic pressure pipe 702 . The hydraulic flow path 713 can flow in or outflow the hydraulic oil (driving fluid), which is an incompressible fluid, to the hydraulic pipe 702 .

In the piston 712 , a hydraulic oil passage 713 connected to the hydraulic pipe 702 passes through the casing 750 . The end 712a of the piston 712 is sealed with an O-ring and a sealing material. The end 712a of the piston 712 is installed and fixed to the casing 750 .

The end portion 712b opposite to the end portion 712a of the piston 712 is located in the cylinder body 711 in a coaxial state.

The end 711a of the cylinder body 711 is open. In the end 711a of the cylinder body 711, the end 712b of the piston 712 is inserted therein.

The cylinder body 711 is relatively movable in the axial direction with respect to the piston 712 . The cylinder body 711 is relatively movable in the axial direction with respect to the casing 750 .

The end 711b of the cylinder body 711 is blocked. A hydraulic space 714 is formed by an inner surface close to the end 711b of the cylinder body 711 and a cross section of the end 712b of the piston 712 . The hydraulic space 714 is filled with hydraulic oil (driving fluid), which is an incompressible fluid.

The volume of the hydraulic space 714 increases or decreases when the cylinder body 711 relatively moves in the axial direction with respect to the piston 712 . In accordance with the increase/decrease in the volume of the hydraulic space 714 , the hydraulic oil filled in the hydraulic space 714 flows in or flows out into the hydraulic pipe 702 through the hydraulic oil passage 713 .

At the end 711a of the cylinder body 711, a flange portion 711c is provided at an outer peripheral position.

The flange portion 711c is cast outward in the radial direction from the end portion 711a.

The end 721a of the inner spring 721 serving as the hydraulic biasing member 720 and the end 722a of the outer spring 722 are in contact with the surface of the flange portion 711c toward the end 711b.

A peripheral groove 711d is cast on the surface of the flange portion 711c facing the end portion 711b close to the outer peripheral surface of the cylinder body 711 .

The end 721a of the inner spring 721 serving as the hydraulic biasing member 720 is in contact with the circumferential groove 711d. The edge part 722a of the outer spring 722 is contact|abutted to the surface which faces the edge part 711b of the flange part 711c used as the outer peripheral position of the circumferential groove 711d.

The hydraulic biasing member 720 has an inner spring 721 and an outer spring 722 . The inner spring 721 and the outer spring 722 are formed of a coil spring. The inner spring 721 and the outer spring 722 are disposed coaxially with the cylinder body 711 and the piston 712 . The inner spring 721 has an inner diameter dimension that is slightly larger than the diameter dimension of the outer peripheral surface of the cylinder body 711 .

The outer spring 722 has an inner diameter dimension that is slightly larger than the outer diameter dimension of the inner spring 721 . The outer spring 722 has a larger wire diameter than the inner spring 721 . The outer spring 722 has a larger biasing force than the inner spring 721 .

The inner spring 721 and the outer spring 722 are capable of transmitting the biasing force in the expansion and contraction direction to the cylinder body 711 . A force is applied to both the inner spring 721 and the outer spring 722 to press the flange portion 711c of the cylinder body 711 toward the end portion 712a of the piston 712 .

The end 721b of the inner spring 721 and the end 722b of the outer spring 722 are in contact with the casing 750 . For this reason, the hydraulic biasing member 720 applies a force to the cylinder body 711 with respect to the casing 750.

In addition, the configuration of the hydraulic biasing member 720 is not limited as long as the hydraulic biasing member 720 can apply a force to the cylinder body 711 .

A bush 711e and Y-shaped packings 711f and 711g are provided on the inner peripheral surface of the cylinder body 711 at a position close to the end portion 711a. The inner peripheral surface of the cylinder body 711 and the outer peripheral surface of the piston 712 are slidably sealed. An end 731a of the drive shaft 731 of the cylinder drive unit 730 is coaxially connected to the end 711b of the cylinder body 711 .

The cylinder drive unit 730 includes a drive shaft 731 that relatively moves the cylinder body 711 in the axial direction with respect to the piston 712 and a drive transmission that drives the drive shaft 731 by a drive unit 705 such as a motor. have wealth

The drive shaft 731 is disposed in the casing 750 in a coaxial state with the cylinder body 711 and the piston 712 . The drive shaft 731 is made to be movable in the axial direction. The drive shaft 731 is relatively movable in the axial direction with respect to the piston 712 and the casing 750 .

A ball screw 731c is formed on the outer peripheral surface of the drive shaft 731 at a position close to the end 731a. The length of the ball screw 731c in the axial direction of the drive shaft 731 is the inner surface ( 732c) is set to maintain the screwed state.

On the radially outer side of the drive shaft 731, the screw drive gear 732 is coaxially arrange|positioned at the outer peripheral position of the ball screw 731c. The drive shaft 731 is supported with respect to the casing 750 by the screw drive gear 732 .

A rotation stop 731h, which will be described later, is provided to protrude in the radial direction at the end 731b opposite to the end 731a of the drive shaft 731 . The rotation stop 731h is located inside the sliding groove 757 provided in the casing 750, and regulates the movement direction so that the drive shaft 731 can move in the axial direction without rotating.

The screw drive gear 732 has a cylindrical shape. The screw drive gear 732 is rotatably supported with respect to the casing 750 . Ball bearings 732f and 732g are installed on the outer periphery of the screw drive gear 732 . The ball bearings 732f and 732g are rotatable coaxially with the drive shaft 731 with respect to the casing 750 and support the screw drive gear 732 .

In addition, the screw drive gear 732 does not move in the axial direction with respect to the casing 750 . An inner surface 732c is formed on the inner periphery of the screw drive gear 732 . The inner surface 732c is screwed with the ball screw 731c of the drive shaft 731 .

When the screw drive gear 732 rotates, a rotational force acts on the drive shaft 731 by the ball screw 731c screwed with the inner surface 732c. The rotation of the drive shaft 731 is regulated by the rotation stop 731h and the sliding groove 757 . Accordingly, the drive shaft 731 moves in the direction regulated by the sliding groove 757 , that is, in the axial direction of the drive shaft 731 .

An outer gear 732d is formed on the outer periphery of the screw drive gear 732 . The outer gear 732d is formed at a position sandwiched between the ball bearing 732f and the ball bearing 732g in the axial direction of the screw drive gear 732 . In the screw drive gear 732 , the outer gear 732d is positioned on the outermost side in the radial direction.

In addition, as for the screw drive gear 732, the inner screw drive gear 732a in which the inner surface 732c was formed, and the external screw drive gear 732b in which the outer gear 732d was formed may be connected integrally.

The outer gear 732d meshes with the drive gear 733d. The drive gear 733d has a rotation axis parallel to the axis line of the drive shaft 731 . The drive gear 733d is rotatably supported by the rotation shaft 734 parallel to the axis line of the drive shaft 731 . The rotation shaft 734 is supported by the casing 750 as a position spaced apart from the outside in the radial direction of the drive shaft 731 . The drive gear 733d is integrally formed with the coaxial drive gear 733e. The drive gear 733e has a larger diameter dimension than the drive gear 733d. The drive gear 733e rotates integrally with the drive gear 733d.

The drive gear 733e meshes with the drive gear 735 . The drive gear 735 has a rotation axis parallel to the axis line of the drive shaft 731 . The drive gear 735 is rotatably supported by a rotation shaft 736 parallel to the axis line of the drive shaft 731 . The rotation shaft 736 is supported by the casing 750 as a position further apart from the rotation shaft 734 at an outer position in the radial direction of the drive shaft 731 .

The drive gear 735 meshes with the drive gear 737 . The drive gear 737 has a rotation axis parallel to the axis line of the drive shaft 731 . The drive gear 737 is fixed to the rotation drive shaft 705a of the drive part 705, such as a motor, parallel to the axis line of the drive shaft 731. The rotational drive shaft 705a consists of a position further apart from the rotational shaft 736 at the outer position in the radial direction of the drive shaft 731. As shown in FIG. The rotational drive shaft 705a is rotatably mounted to the casing 750 in a penetrating state.

Screw drive gear 732, ball bearings 732f, 732g, inner surface 732c, outer gear 732d, drive gear 733d, drive gear 733e, rotary shaft 734, drive gear 735, rotary shaft 736 , the drive gear 737 constitutes a drive transmission unit (drive system of the hydraulic pressure generating unit 701 ).

The casing 750 includes a casing cylinder 751 , a casing lid 752 , a rear casing 753 , a ring 754 , and a lid portion 758 . The casing cylinder 751 is formed in a cylindrical shape. The casing lid 752 closes one end of the casing cylinder 751 .

The rear casing 753 closes the other end of the casing cylinder 751 . The ring 754 is provided between the casing cylinder 751 and the rear casing 753 . The lid part 758 closes the other end of the rear casing 753 .

The casing cylinder 751 has an internal shape extending coaxially with the cylinder body 711 , the piston 712 , and the drive shaft 731 . The interior of the casing cylinder 751 forms a storage space 755 .

Inside the storage space 755, a cylinder body 711, a piston 712, an inner spring 721 and an outer spring 722 serving as the hydraulic biasing member 720, and an end portion of the drive shaft 731 ( 751a) is accommodated. In the storage space 755 , an end position close to the piston 712 is opened, and is closed by the casing lid 752 .

A piston 712 is connected and fixed to the casing lid 752 . An end portion 712a of the piston 712 passes through the casing lid 752 . In the storage space 755 , an end position close to the drive shaft 731 is opened, and is blocked by the rear casing 753 . A drive shaft 731 passes through the rear casing 753 . In the storage space 755 , a ring 754 is provided at a position adjacent to the rear casing 753 .

The ring 754 is disposed on the periphery of the drive shaft 731 as coaxial with the drive shaft 731 . The inner periphery of the ring 754 and the outer periphery of the drive shaft 731 are spaced apart. The ring 754 has an inner diameter equal to the diameter of the inner periphery of the flange portion 711c, that is, the outer peripheral surface of the cylinder body 711 . In addition, the ring 754 has an outer diameter equal to the outer diameter dimension of the flange portion 711c.

The end 721b of the inner spring 721 serving as the hydraulic biasing member 720 and the end 722b of the outer spring 722 are in contact with the surface of the ring 754 facing the casing lid 752 . A circumferential groove 754d is cast on the surface of the ring 754 opposite to the casing lid 752 so as to correspond to the circumferential groove 711d. The end 721b of the inner spring 721 serving as the hydraulic biasing member 720 is in contact with the circumferential groove 754d. The end portion 722b of the outer spring 722 is in contact with the surface of the ring 754 serving as the outer peripheral position of the circumferential groove 754d toward the casing lid 752 .

Between the casing cylinder 751 and the rear casing 753 , drive system support parts 751k and 753k extending toward the radially outer side of the drive shaft 731 from the storage space 755 are provided. The drive system support parts 751k and 753k are formed in a flange shape forming a part in the circumferential direction with respect to the casing cylinder 751 and the rear casing 753 .

The drive system support part 751k and the drive system support part 753k are in contact with each other. Between the drive system support part 751k and the drive system support part 753k, the screw drive gear 732, ball bearings 732f, 732g, the inner surface 732c, the outer surface 732d, the drive gear 733d, the drive gear ( 733e), the rotating shaft 734, the driving gear 735, the rotating shaft 736, and the driving gear 737 are sandwiched.

A screw drive gear 732 , ball bearings 732f and 732g , an outer gear 732d , a drive gear 733d , a drive gear 733e , and a rotation shaft are disposed on surfaces opposite to the drive system support part 751k and the drive system support part 753k . Concave and convex corresponding to 734 , the drive gear 735 , the rotation shaft 736 , and the drive gear 737 are formed.

The drive system support part 751k and the drive system support part 753k include a screw drive gear 732, ball bearings 732f and 732g, a drive gear 733d, a drive gear 733e, a rotation shaft 734, a drive gear 735, The rotating shaft 736 and the drive gear 737 are supported between the opposing surfaces.

Moreover, the rotation drive shaft 705a penetrates the drive system support part 751k. A drive unit 705 having a hydraulic motor 705m is attached to the drive system support unit 751k.

A ball bearing 732f is provided between the casing cylinder 751 and the screw drive gear 732 . The ball bearing 732f rotatably supports the screw drive gear 732 with respect to the casing cylinder 751 . A ball bearing 732g is installed between the rear casing 753 and the screw drive gear 732 . The ball bearing 732g rotatably supports the screw drive gear 732 with respect to the rear casing 753 .

In the rear casing 753 , a space 756 after which the end 731b of the drive shaft 731 is released is formed when the drive shaft 731 moves in the axial direction. The screw drive gear 732 is arrange|positioned at the position used as the boundary of the rear space 756 and the accommodation space 755. That is, at the position used as the boundary between the rear space 756 and the storage space 755, the drive shaft 731 is made to be movable in an axial direction, and is arrange|positioned.

In the rear space 756, a sliding groove 757 is formed so as to enlarge the diameter. The sliding groove 757 is located on the radially outer side of the drive shaft 731 . The sliding groove 757 regulates the rotation of the drive shaft 731 when the rotation stop 731h slides inside, and enables movement of the drive shaft 731 in the axial direction. The end of the rear space 756 is blocked by a lid portion 758 .

A detection switch 760 (detection means) capable of detecting that the drive shaft 731 has approached is provided at a position adjacent to the lid portion 758 of the rear space 756 . The detection switch 760 is connected to the control unit 706 . The detection switch 760 may be located in the sliding groove 757 .

A detection switch 761 (detection means) capable of detecting that the drive shaft 731 approaches the piston 712 is provided at a position adjacent to the screw drive gear 732 in the rear space 756 . The detection switch 761 is connected to the control unit 706 . The detection switch 761 may be located in the sliding groove 757 .

The detection switch 760 and the detection switch 761 detect the axial position of the drive shaft 731 . The detection switch 760 and the detection switch 761 can be of a contact type or a non-contact magnetic type.

For example, the detection switch 760 may be a limiter switch detectable when a part of the drive shaft 731 abuts, or a magnetic element provided on a part of the drive shaft 731 may be a detectable magnetic switch.

The detection switch 760 is, when the drive shaft 731 moves from the accommodation space 755 toward the rear space 756 , the drive shaft 731 reaches a position defined by the detection switch 760 in the axial direction. detect that In addition, when the driving shaft 731 moves from the rear space 756 toward the storage space 755 , the detection switch 761 is positioned at a position defined by the detection switch 761 in the axial direction. Detect what has been reached

Here, when the detection switch 760 outputs to the control unit 706 that the driving shaft 731 has reached a predetermined position in the axial direction, the control unit 706 receiving the signal causes the driving unit 705 to be driven. Outputs a stop signal. For this reason, the drive of the drive part 705 stops. Therefore, the movement position of the drive shaft 731 is regulated by the installed position of the detection switch 760 .

Here, the drive stop by the drive unit 705 may stop the drive of the hydraulic motor 705m by stopping the power supply from the power source 707 .

In addition, the drive stop by the drive part 705 may stop the rotation of the rotation drive shaft 705a of the hydraulic motor 705m by the non-excitation operation brake 705b.

Alternatively, when the detection switch 761 outputs to the control unit 706 that the driving shaft 731 has reached a predetermined position in the axial direction, the control unit 706 receiving the signal causes the driving unit 705 to be driven. Output the starting signal. For this reason, driving of the drive part 705 starts. Therefore, the movement position of the drive shaft 731 is regulated by the installed position of the detection switch 761 .

Here, when the drive unit 705 starts driving, the hydraulic motor 705m may be started by starting power supply from the power source 707 .

In addition, the drive start by the drive part 705 may cancel the rotation stop of the rotation drive shaft 705a of the hydraulic motor 705m by the non-excitation operation brake 705b.

In this way, the hydraulic pressure generating unit 701 can change the driving state in the driving unit 705 in response to the signal from the control unit 706 .

When the control unit 706 outputs a driving signal, the driving unit 705 drives. The rotation drive shaft 705a rotates by the drive of the drive part 705. As shown in FIG. By rotation of the rotational drive shaft 705a, the drive gear 737 attached to the rotational drive shaft 705a rotates. The rotation of the drive gear 737 is transmitted to the drive gear 735 meshing with each other. The rotation of the drive gear 735 is transmitted to the drive gear 733e meshing with each other.

The rotation of the drive gear 733e is transmitted to the drive gear 733d formed integrally. The rotation of the drive gear 733d is transmitted to the mutually meshed outer gear 732d, and the screw drive gear 732 rotates. The rotation of the outer gear 732d is transmitted to the inner surface 732c of the screw drive gear 732 formed integrally.

The rotation of the inner surface 732c of the screw drive gear 732 is transmitted to the ball screw 731c of the drive shaft 731 meshing with each other, and the drive shaft 731 rotates. Since the screw drive gear 732 is supported by the ball bearings 732f and 732g, even if it rotates, it does not move in the axial direction.

The drive shaft 731 is supported by the inner surface 732c, the rotation stop 731h is located inside the sliding groove 757, and the movement direction of the drive shaft 731 is regulated. For this reason, when the drive shaft 731 rotates, it moves in an axial direction. In this way, the rotational driving force of the driving unit 705 is transmitted to the driving shaft 731 by the driving transmission unit to move the driving shaft 731 in the axial direction.

When the drive shaft 731 moves in the axial direction, the cylinder body 711 connected integrally also moves in the axial direction in the same manner. At this time, since the piston 712 is being fixed to the casing lid 752, it does not move. For this reason, the cylinder body 711 and the piston 712 relatively move in the axial direction.

Here, as the cylinder body 711 and the piston 712 move relatively, the volume of the hydraulic space 714 inside the cylinder body 711 changes. According to a change in the volume of the hydraulic space 714 , the pressure oil (driving fluid), which is an incompressible fluid filled in the hydraulic space 714 , flows into or out of the hydraulic flow passage 713 .

An inner spring 721 and an outer spring 722 serving as the hydraulic pressure biasing member 720 in contact with the flange portion 711c apply a biasing force to the cylinder body 711 .

In the present embodiment, when the non-excitation brake 705b is not operated and the hydraulic motor 705m is not driven by the normal push, that is, the drive unit 705, the movable part 72 can be extended. . For this reason, in the hydraulic cylinder 710 , the biasing force from the hydraulic biasing member 720 is in the direction in which the inner spring 721 and the outer spring 722 extend. That is, the biasing force applied to the cylinder body 711 from the hydraulic biasing member 720 is in the direction in which the cylinder body 711 is spaced apart from the screw drive gear 732 .

Accordingly, the urging force of the hydraulic biasing member 720 is applied so that the volume of the hydraulic space 714 in the cylinder body 711 is decreased.

In addition, in this embodiment, when the non-excitation brake 705b is not act|operating in the normal push, ie, the drive part 705, and the hydraulic motor 705m is driven, the movable part 72 is made to be able to retract. . For this reason, in the hydraulic cylinder 710 , the direction in which the driving shaft 731 moves by the driving of the driving unit 705 is opposite to the biasing force of the hydraulic biasing member 720 . That is, by the driving of the driving unit 705 , the driving shaft 731 moves in a direction away from the piston 712 .

Accordingly, the drive shaft 731 moves so that the volume of the hydraulic space 714 in the cylinder body 711 is increased by the drive of the drive unit 705 .

When the non-excitation brake 705b is actuated in the driving unit 705 or the hydraulic motor 705m is driven to be stopped, the hydraulic pressure generating unit 701 is, as shown in FIG. 7 , of the hydraulic biasing member 720 . The volume of the hydraulic space 714 is reduced by the biasing force. Due to this, the volume of the hydraulic space 714 is pressurized. For this reason, the pressure oil (drive fluid) which is an incompressible fluid flows in with respect to the hydraulic pipe 702 through the hydraulic flow path 713 from the hydraulic space 714. At this time, hydraulic pressure acts on the valve case biasing portion 70 , and the tip portion 72a of the movable portion 72 extends.

In addition, in the case where the hydraulic pressure generating unit 701 drives the driving unit 705 , as shown in FIG. 8 , the volume of the hydraulic pressure space 714 is increased by the driving force of the driving unit 705 . For this reason, the volume of the hydraulic space 714 is pressure-reduced. Pressure oil (driving fluid), which is an incompressible fluid, flows into the hydraulic space 714 from the hydraulic pipe 702 through the hydraulic oil passage 713 . At this time, hydraulic pressure acts on the valve case biasing portion 70 , and the tip portion 72a of the movable portion 72 degenerates.

In addition, in the hydraulic pressure generating unit 701, even when the cylinder body 711 overruns so as to be close to the casing lid 752 for some reason, the flange portion 711c abuts against the casing lid 752, The movement of the cylinder body 711 is stopped. For this reason, the reduction of the hydraulic space 714 is limited to a predetermined range. Accordingly, the hydraulic pressure generating unit 701 may prevent excessive pressure oil (driving fluid) from flowing into the valve case biasing unit 70 .

9 : is axial direction sectional drawing for demonstrating the valve case biasing part in the gate valve in this embodiment. It is axial direction sectional drawing orthogonal to FIG. 9 for demonstrating the valve case biasing part in the hydraulic drive system in this embodiment, and a gate valve. Fig. 10 is an axial cross-sectional view showing an extended state in a valve case biasing part.

As shown in FIGS. 9-10, the valve case biasing part 70 which concerns on this embodiment includes the guide rod 771, the cylinder part 772, the expansion-contraction rod 72, the flange part 773, and a biasing member. (73) and a casing (774).

As for the valve case biasing part 70, as shown in FIGS. 9-10, from one end of a substantially cylindrical casing 774, the expansion and contraction rod 72 narrower than this casing 774 can extend and retract. is made up of The valve case biasing part 70 is connected to the hydraulic pressure generating part 701 via a hydraulic pressure pipe 702 .

The hydraulic pressure generating unit 701 is capable of supplying a positive pressure or a negative hydraulic pressure to the valve case biasing unit 70 when the expansion and contraction rod 72 is expanded and contracted, and maintains the hydraulic pressure state at the end of the operation. . In addition, the state in which the telescopic rod 72 is in contact with the target can be appropriately controlled.

As shown in FIGS. 9 to 10, the guide rod 771 has a substantially cylindrical shape and has a through hole 771c capable of supplying operating hydraulic pressure from the hydraulic drive unit 700 toward one end surface 771a in the axial direction. .

The guide rod 771 is erected from the lid part 774b of the casing 774 toward the inside of the casing 774 .

The guide rod 771 may be formed integrally with the lid part 774b. In the present embodiment, the guide rod 771 has a pipe-shaped outer guide rod 771g to a convex portion 774h protruding from the center position of the recess 774g provided in the lid portion 774b. are screwed together. For this reason, centering of the outer guide rod 771g with respect to the cover part 774b is performed. The through-hole 771c is continuously formed in the inside of the cover part 774b, the convex part 774h, and the outer guide rod 771g.

The cylinder part 772 consists of a user cylindrical shape with the other end opened. The cylinder part 772 consists of a guide rod 771 and coaxial shape. The cylinder part 772 is arrange|positioned so that the one end surface 771a of the guide rod 771 may be covered slidably. One end surface 771a of the guide rod 771 and the inner surface of the cylinder part 772 form a driving space 777 therein.

A through hole 771c communicates with the drive space 777 . A hydraulic pipe 702 is connected to the through hole 771c as shown in FIG. 9 . The drive space 777 is connected to a hydraulic pressure generating unit 701 via a hydraulic pressure pipe 702 .

Hydraulic oil is supplied to the driving space 777 from the hydraulic pressure generating unit 701 through the hydraulic pressure pipe 702 , and the driving space 777 is pressurized. Alternatively, hydraulic oil is returned to the hydraulic pressure generating unit 701 through the hydraulic pressure pipe 702 in the driving space 777 , and the driving space 777 is decompressed.

At one end 772a of the cylinder portion 772, an expansion rod 72 is provided at a position that becomes the upper surface in FIG. 9 . The telescopic rod 72 is formed in a cylindrical shape extending outward in the axial direction of the cylinder portion 772 . The telescopic rod 72 is formed coaxially with the cylindrical cylinder part 772 . The telescopic rod 72 is coaxial with the circumferential guide rod 771 .

The expansion and contraction rod 72 is formed integrally with the cylinder part 772, and is made movable so that it can expand and contract in the axial direction in addition to sliding of the cylinder part 772 with respect to the guide rod 771. The diameter dimension of the telescopic rod 72 is set smaller than the diameter dimension of the cylinder part 772 .

The diameter dimension of the telescopic rod 72 is set smaller than the diameter dimension of the guide rod 771 . The expansion and contraction rod 72 may be formed integrally with the cylinder part 772 . In the telescopic rod 72 of the present embodiment, the elastic rod 72 is screwed to a convex portion 772h protruding at the axial center position of the cylinder portion 772 . For this reason, centering of the telescopic rod 72 with respect to the lid part 774b is performed.

On the other end 772b of the cylinder portion 772, a flange portion 773 is cast at an outer peripheral position.

The flange portion 773 extends radially outward from the other end 772b of the cylinder portion 772 . The flange portion 773 has a predetermined thickness.

The flange portion 773 is formed integrally with the cylinder portion 772 .

On the flange portion 773 , the other end of the biasing member 73 abuts against a pressing surface 773a close to the expansion rod 72 .

The biasing member 73 has a spiral shape and applies a force to the flange portion 773 in the direction of retraction of the expansion and contraction rod 72 .

The biasing member 73 is located on the outer periphery of the cylinder portion 772 coaxially with the cylinder portion 772 . One end of the biasing member 73 abuts against the casing 774 .

The casing 774 has a cylindrical cylindrical portion 774c, a lid portion 774b that closes the other end of the cylindrical portion 774c, and a vacuum side that blocks a through hole 774m provided at one end of the cylindrical portion 774c. It has a lid part 774a.

At the central position of the lid part 774b, a guide rod 771 is installed toward the inside of the casing 774 . The vacuum side lid part 774a has a through hole 775 through which the expansion and contraction rod 72 penetrates in the center of the vacuum side lid part 774a, and is in contact with the vacuum side. The other end of the cylindrical part 774c is fitted to the recessed part 774g provided in the lid part 774b.

A buffer space 776 is formed inside the cylindrical part 774c, the lid part 774b, and the vacuum side lid part 774a.

The cylinder part 772 and the biasing member 73 are accommodated in the buffer space 776 . In the buffer space 776 , the cylinder portion 772 is capable of reciprocating movement. The buffer space 776 is a space for buffering before leaking to the outside (chamber) Ch serving as the vacuum side when the operating hydraulic pressure leaks from the drive space 777 .

A step 774d is formed on the inner surface of the cylindrical portion 774c serving as the buffer space 776 . As for the inner surface of the cylindrical part 774c, the position adjacent to the lid part 774b is enlarged compared with the position adjacent to the vacuum side lid part 774a.

As for the step 774d, the outer edge portion of the pressing surface 773a of the flange portion 773 abuts. The step 774d is a regulating portion that regulates the position of the cylinder portion 772 when it is elongated in the movement range (moving region).

The outer peripheral surface of the flange part 773 was not in contact with the inner surface of the cylindrical part 774c used as the buffer space 776. As shown in FIG. The flange part 773 used as the cylinder part 772 outer end part 772b abuts against the recessed part 774g provided in the lid part 774b. The recessed portion 774g serves as a regulating portion for regulating the position of the cylinder portion 772 in the retracting direction within the movement range.

The cylindrical part 774c and the vacuum side lid part 774a are connected and fixed. A step 774e is formed at a position adjacent to the vacuum side lid 774a of the cylindrical portion 774c. The position closer to the vacuum side lid portion 774a than the step 774e of the cylindrical portion 774c is further reduced in diameter to form an atmospheric-side buffer space 778 having the same inner diameter as the outer dimension of the cylinder portion 772 . is becoming

One end of the biasing member 73 is in contact with the step 774e.

The outer peripheral surface (sliding surface) 772m of the cylinder part 772 is in contact with the inner peripheral surface of the atmospheric|atmosphere side buffer space 778 slidably. In the atmospheric side buffer space 778, as shown in FIG. 9, 778 s of through-holes communicating with the outside are formed in the radial direction of the cylindrical part 774c. The atmospheric side buffer space 778 communicates with the atmospheric side by 778 s of through-holes.

The through hole 775 has a smaller diameter than the atmospheric side buffer space 778 . The through hole 775 has a diameter dimension substantially equal to the outer diameter of the expansion and contraction rod 72 .

The casing 774 and the guide rod 771 constitute the fixed part 71 .

The valve case biasing portion 70 is provided with a sealing member as a multi-stage seal structure so that oil, which is a working fluid, does not leak into the chamber Ch on the vacuum side during hydraulic driving. Specifically, from the driving space 777 inside the cylinder portion 772 to which hydraulic pressure is supplied to the inside or the outside of the chamber Ch on the vacuum side of the expansion rod 72, the four-stage sealing member 77a1 ~77e) is installed.

Two stages of sealing members 77a1 to 77e are provided on the sliding surface 771f of the outer periphery of the guide rod 771 that slides with the inner surface of the cylinder portion 772 .

In the sliding surface 771f of the outer periphery of the guide rod 771, an O-ring (sealing member) 77a1 and a wear ring (sealing member) 77a2 are cast in the same groove so that they can be sealed from the drive space 777 to the outside. is becoming

The wear ring (sealing member) 77a2 is cast on the radially outer side of the O-ring (sealing member) 77a1.

The wear ring (sealing member) 77a2 is in contact with the inner surface of the cylinder portion 772 , and slides with the sliding surface 772f of the inner periphery of the cylinder portion 772 .

In addition, on the sliding surface 771f of the outer periphery of the guide rod 771, at a position spaced apart from the driving space 777 from the wear ring (sealing member) 77a2, so that the sliding surface 771f and the sliding surface 771f are flush with each other. A wear ring (sealing member) 77b is cast.

The O-ring (sealing member) 77a1, the wear ring (sealing member) 77a2, and the wear ring (sealing member) 77b form a first-stage sealing member. The wear ring (sealing member) 77b is a backup ring.

Further, on the sliding surface 771f of the outer periphery of the guide rod 771, at a position spaced apart from the driving space 777 from the wear ring (sealing member) 77b, so that it is flush with the sliding surface 771f The Y packing 77c1 (sealing member) and the sealing 77c2 (sealing member) are cast in the same groove.

Both the Y packing 77c1 and the sealing 77c2 are in contact with the inner surface of the cylinder portion 772 . The Y packing 77c1 and the sealing 77c2 slide with the sliding surface 772f of the inner periphery of the cylinder part 772 .

The sealing 77c2 is arrange|positioned at the position spaced apart from the drive space 777 rather than the Y packing 77c1.

Further, on the sliding surface 771f of the outer periphery of the guide rod 771, a wear ring (sealing member) 77d at a position spaced apart from the driving space 777 rather than the sealing 77c2 so as to be flush with the sliding surface 771f This is being argued.

The Y packing 77c1, the sealing ring 77c2, and the wear ring (sealing member) 77d form a second-stage sealing member. The wear ring (sealing member) 77d is a backup ring.

A Y packing (sealing member) 77e is provided on the inner peripheral surface of the through hole 774m in a through hole 774m provided in a position close to the vacuum side lid portion 774a in the cylindrical portion 774c of the casing 774. It is stated

The Y packing (sealing member) 77e slides with the sliding surface 772m of the outer periphery used as the position adjacent to the one end surface 771a of the cylinder part 772. The Y packing (sealing member) 77e consists of a third-stage sealing member.

In the through hole 775 in the vacuum side lid portion 774a of the casing 774 , an O-ring (sealing member) 77f is cast on the inner peripheral surface of the through hole 775 .

The O-ring (sealing member) 77f slides with the outer peripheral surface (sliding surface) 72m of the telescopic rod 72 . The Y packing (sealing member) 77e consists of a 4th stage sealing member.

In addition to the sealing members 77a1 to 77e, an O-ring (sealing member) 77p is disposed at a screwing position between the convex portion 774h of the casing 774 and the outer guide rod 771g.

An O-ring (sealing member) 77q is disposed between the cylindrical portion 774c of the casing 774 and the recess 774g provided in the lid portion 774b.

An O-ring (sealing member) 77r is disposed around the through-hole 775 in the vacuum-side lid portion 774a for sealing with the chamber Ch serving as the vacuum side.

In the valve case biasing portion 70 in the present embodiment, the sealing members 77a1 to 77r can be selected from the following materials.

The wear ring (sealing member) 77a2 is made of a fluorinated resin. The wear ring (sealing member) 77b is made of HNBR (hydrogenated nitrile rubber). The Y packing 77c1 is made of HNBR (hydrogenated nitrile rubber). The sealing 77c2 is made of a fluorinated resin. The wear ring (sealing member) 77d is made of a fluorinated resin. The Y packing (sealing member) 77e is made of HNBR (hydrogenated nitrile rubber). The O-ring (sealing member) 77f is made of HNBR (hydrogenated nitrile rubber). The O-ring (sealing member) 77p, the O-ring (sealing member) 77q, and the O-ring (sealing member) 77r are all made of HNBR (hydrogenated nitrile rubber).

Moreover, the expansion-contraction rod 72 consists of stainless steel. The guide rod 771 is made of stainless steel. The cylinder part 772 is made of stainless steel. The cylindrical part 774c, the lid part 774b, and the vacuum side lid part 774a of the casing 774 are all made of aluminum. In addition, the material in such a structure can be suitably changed according to the use of the valve case biasing part 70. As shown in FIG.

In addition, a position close to the sliding surface 771f of the outer periphery of the guide rod 771 made of stainless steel, the sliding surface 772f of the inner periphery of the cylinder part 772, and the one end surface 771a of the cylinder part 772. Surface treatment such as chrome plating is performed on both the sliding surface 772m on the outer periphery and the sliding surface on the outer periphery of the elastic rod 72 .

In the valve case biasing portion 70 in the present embodiment, in the normal pull, that is, in a non-operating state, the expansion rod 72 is degenerate. In this state, the force is applied by the biasing member 73 to the flange portion 773 in the direction of retraction of the elastic rod 72 .

Next, the hydraulic oil supplied from the hydraulic pressure generating unit 701 by the driving of the driving unit 705 in the hydraulic driving unit 700 flows into the driving space 777 through the hydraulic pressure pipe 702 . Then, the driving space 777 is pressed, generating a driving force greater than the biasing force of the biasing member 73 , and the cylinder part 772 moves toward the through hole 775 . At this time, the cylinder part 772 moves inside the buffer space 776 .

The outer edge portion of the pressing surface 773a of the flange portion 773 abuts against the step 774d, and the movement of the cylinder portion 772 is completed. For this reason, as shown in FIG. 10, the expansion-contraction rod 72 expands, and the expansion-contraction rod 72 advances (protrudes) toward the chamber Ch used as a vacuum side. The stretched telescopic rod 72 presses the object. In this state, by maintaining the hydraulic pressure supplied from the hydraulic pressure generating unit 701 to the driving space 777 , the expanded state of the telescopic rod 72 can be maintained.

In order for the expansion and contraction rod 72 to change from an extended state to a retracted state, the hydraulic pressure supplied from the hydraulic pressure generating part 701 to the drive space 777 is pressure-reduced. Alternatively, the hydraulic oil is returned from the driving space 777 to the hydraulic pressure generating unit 701 through the hydraulic pipe 702 . Then, the cylinder part 772 moves toward the lid part 774b by the biasing force which acts on the flange part 773 from the biasing member 73. As shown in FIG. For this reason, as shown in FIG. 9, the expansion-contraction rod 72 will be in the degenerate state.

In addition, in the valve case biasing part 70 of this embodiment, when oil leaks between the drive space 777 and the hydraulic space 714 through the hydraulic pipe 702, this can be detected. Specifically, when the flow rate accommodated in the drive space 777 is reduced, the volume of the hydraulic space 714 is reduced by the biasing force of the hydraulic biasing member 720 . For this reason, the reciprocating motion range of the drive shaft 731 in an axial direction moves in the direction adjoining the piston 712 from the assumed position.

Therefore, compared to the assumed position, the detection signal is output from the detection switch 761 at an earlier stage in the axial movement of the drive shaft 731 . For this reason, it is detectable that the flow volume accommodated in the drive space 777 has decreased.

In this embodiment, the same effects as those of the above-described embodiment can be obtained.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 3rd Embodiment of this invention is demonstrated based on drawing.

In this embodiment, the difference from the first and second embodiments described above relates to the pendulum valve body of the gate valve, and the corresponding components other than the above are assigned the same reference numerals and description thereof is omitted.

11 : is sectional drawing orthogonal to the flow path which shows the gate valve in this embodiment.

12 : is sectional drawing along the flow path which shows the gate valve in this embodiment.

Fig. 13 is an enlarged cross-sectional view taken along a flow path showing the periphery of the gate valve in the present embodiment.

11 to 13 , reference numeral 100 denotes a gate valve.

As shown in FIG. 11, FIG. 12, the gate valve 100 which concerns on this embodiment has the valve case 10, the hollow part 11, the valve body 5, the rotating shaft 20, and a rotating shaft. A driving unit 200 , a valve case biasing part 70 , a valve plate biasing part 80 (holding spring), a valve frame biasing part 90 , and a hydraulic driving part 700 are provided.

The first opening 12a and the second opening 12b have substantially the same outline. The first opening 12a has a circular outline. The second opening 12b has a circular outline.

In the hollow part 11 , the valve body 5 is arranged.

The valve body 5 is made so that a 1st space and a 2nd space can be interrupted|blocked in a valve closing position.

The rotating shaft 20 has an axis line extending substantially parallel to the flow path H direction. The rotating shaft 20 passes through the valve case 10 . The rotating shaft 20 can be rotationally driven by the rotating shaft driving unit 200 .

The valve body 5 is fixed to the rotation shaft 20 via a connecting member (not shown). Alternatively, the valve body 5 may be directly connected to the rotation shaft 20 via a connecting member (not shown).

The rotating shaft 20 functions as a position switching unit of the valve body 5 .

14 : is the top view seen from the direction orthogonal to the flow path which shows the valve body of the gate valve in this embodiment.

The valve body 5 can block the 1st opening part 12a and/or the 2nd opening part 12b.

The valve body 5 operates between the valve closing position, the valve opening blocking position, and the valve opening position (retracted position).

The valve body 5 is rotatable between the retracted position and the valve opening blocking position.

In the valve closed position, the valve body 5 is in a closed state ( FIGS. 16 to 19 ) with respect to the first opening 12a and/or the second opening 12b.

In the valve open position (retracted position), the valve body 5 is in an open state retracted from the first opening 12a and/or the second opening 12b (shown by broken lines in FIG. 11 ).

The valve body 5 is comprised by the neutral valve part 30 and the movable valve part 40. As shown in FIG.

The neutral valve part 30 extends in a direction orthogonal to the axis line of the rotation shaft 20 . The neutral valve unit 30 is disposed so as to be included in a plane parallel to the direction orthogonal to the axis of the rotation shaft 20 .

The neutral valve part 30 has the circular part 30a and the rotating part 30b, as shown to FIGS. 11-13.

The circular portion 30a has a ring shape that is slightly larger than the outline of the first opening 12a and/or the second opening 12b. The movable valve part 40 is arrange|positioned at the position used as the radial inner side of the circular part 30a. The inner periphery of the circular portion 30a is arranged so as to substantially overlap the first opening 12a and/or the second opening 12b when viewed in the flow path H direction.

The rotating part 30b is located between the rotating shaft 20 and the circular part 30a. The rotating part 30b rotates the circular part 30a with rotation of the rotating shaft 20. As shown in FIG. The rotating part 30b is formed in the flat plate shape extended so that a diameter may expand toward the circular part 30a from the rotating shaft 20. As shown in FIG. The rotating part 30b may consist of the arm shape in which the arm of several lines extended from the rotating shaft 20 toward the circular part 30a.

Although the rotation shaft 20 and the neutral valve part 30 rotate with respect to the valve case 10, the position does not change in the flow path H direction.

The circular part 30a and the rotating part 30b may consist integrally.

In this case, a through hole for fitting the movable valve part 40 is formed in the flat plate-shaped neutral valve part 30 to form a circular part 30a. A portion of the circular portion 30a in the circumferential direction and a portion extending outward in the radial direction constitute the rotating portion 30b.

It is formed so that the thickness dimension of the flow path H direction of the circular part 30a may become substantially equal to the thickness dimension of the flow path H direction of the rotation part 30b. A circular flange part 30c is cast on the radially inner side of the neutral valve part 30 in the circular part 30a.

It is formed so that the thickness dimension of the flow path H direction of the circular flange part 30c may become smaller than the thickness dimension of the flow path H direction of the circular part 30a. The circular flange portion 30c is cast at a position adjacent to the first opening portion 12a in the flow path H direction on the inner peripheral surface of the circular portion 30a.

In the flow path H direction, the outer frame plate 60e of the movable valve frame part 60 mentioned later is located in the position closer to the 2nd opening part 12b rather than the circular flange part 30c. The circular flange part 30c is connected to the outer frame plate 60e of the movable valve frame part 60 mentioned later. The circular flange part 30c and the outer frame plate 60e are located in the radial direction outer side of the outer peripheral crank part 60c.

The width dimension used in the radial direction of the neutral valve part 30 in the circular flange part 30c is set substantially equal to the width dimension used as the radial direction of the movable valve frame part 60 in the outer peripheral crank part 60c. The circular part 30a and the circular flange part 30c are cast in the position used as the radial direction outer side of the movable valve frame part 60 with respect to the outer peripheral crank part 60c.

In addition, the circular part 30a and the rotating part 30b may be formed so that the thickness dimension of the flow path H direction may become the same.

The movable valve part 40 consists of a substantially disk shape.

The movable valve part 40 is connected so that the position of the flow path H direction with respect to the neutral valve part 30 is changeable. That is, the movable valve part 40 is connected in such a way that only the thickness direction is slidable with respect to the neutral valve part 30 .

The movable valve part 40 consists of two parts mutually movable in the flow path H direction. The movable valve part 40 is provided with the movable valve frame part 60 (slide valve frame) and the movable valve board part 50 (counter board).

The movable valve frame portion 60 has a substantially ring shape substantially concentric with the circular portion 30a. The movable valve frame part 60 is located radially inside in the circular part 30a. The movable valve frame part 60 is fitted to the circular part 30a.

The movable valve frame part 60 is made to be slidable in the flow path H direction with respect to the neutral valve part 30. As shown in FIG. The movable valve frame unit 60 is configured to be movable in the flow path H direction with respect to the neutral valve unit 30 . The movable valve frame part 60 is made to be movable with respect to the neutral valve part 30 between the position which a pendulum operation|movement is possible, and the position which can contact the 1st opening part 12a.

The movable valve frame part 60 has the outer peripheral crank part 60c, the inner frame plate 60d, and the outer frame plate 60e.

As for the movable valve frame part 60, the inner frame plate 60d, the outer periphery crank part 60c, and the outer frame plate 60e are connected, and the ring-shaped cross-sectional shape in a radial direction becomes a substantially Z-shape.

The outer peripheral crank portion 60c is formed in a ring shape or a cylindrical shape having a contour slightly larger than that of the first opening portion 12a and/or the second opening portion 12b. The outer periphery crank portion 60c is formed around the outer periphery of the movable valve frame portion 60 . The outer peripheral crank part 60c has the thickness dimension in the flow path H direction substantially the same as the thickness dimension of the neutral valve part 30 in the flow path H direction.

The outer peripheral crank portion 60c has a sliding surface 60b.

The sliding surface 60b is a cylindrical surface having an axis line parallel to the flow path H direction. The sliding surface 60b is provided on the entire length in the circumferential direction from the inner peripheral surface of the outer peripheral crank portion 60c. The sliding surface 60b is slidably mutually slidable with the sliding surface 50b of the inner peripheral crank part 50c of the movable valve plate part 50 mentioned later, and is located in the opposite state.

The inner peripheral crank part 50c is fitted to the outer peripheral crank part 60c.

The inner frame plate 60d is cast in a position to be radially inner side of the movable valve frame part 60 in the outer peripheral crank part 60c. The inner frame plate 60d is cast at an end portion adjacent to the first opening portion 12a in the flow path H direction of the outer peripheral crank portion 60c. The inner frame plate 60d is formed in a flange shape parallel to the valve plate 50d.

The inner frame plate 60d has a thickness dimension in the flow path H direction smaller than the thickness dimension of the outer peripheral crank portion 60c in the flow path H direction. At a position closer to the second opening portion 12b in the flow path H direction than the inner frame plate 60d, an inner peripheral crank portion 50c to be described later is located. The width dimension used in the radial direction of the movable valve frame part 60 in the inner frame plate 60d is set to be substantially the same as the width dimension used as the radial direction of the movable valve frame part 60 in the inner peripheral crank part 50c.

The outer frame plate 60e is cast at a position outside the movable valve frame portion 60 in the outer peripheral crank portion 60c in the radial direction. The outer frame plate 60e is cast at an end portion adjacent to the second opening portion 12b in the flow path H direction of the outer peripheral crank portion 60c. The outer frame plate 60e is cast on the outer side in the radial direction of the movable valve frame portion 60 in the outer peripheral crank portion 60c.

The outer frame plate 60e is made of a protrusion whose dimension in the flow path H direction is smaller than that of the outer peripheral crank portion 60c.

The circular flange part 30c is located in the position closer to the 1st opening part 12a in the flow path H direction than the outer frame plate 60e. A plurality of valve frame biasing portions 90 are disposed on the outer frame plate 60e, as will be described later. In the outer frame plate 60e, a plurality of biasing hole 68 in which the valve frame biasing part 90 is incorporated is disposed.

Between the movable valve frame part 60 and the neutral valve part 30, the valve frame biasing part 90 (auxiliary spring) is arrange|positioned.

The movable valve frame part 60 is connected with the neutral valve part 30 by the valve frame biasing part 90 so that the position in the flow path H direction is changeable. The movable valve frame part 60 and the circular part 30a are made of a concentric double annular ring.

The movable valve frame part (60) is provided with a valve frame seal packing (61) on a surface facing (abutting) the valve case inner surface (10A). The valve frame seal packing 61 is arrange|positioned at the boundary position of the outer peripheral crank part 60c used as a circle, and the inner frame plate 60d. The valve frame seal packing 61 is provided in the end face opposite to the 1st opening part 12a of the outer peripheral crank part 60c.

The valve frame seal packing 61 is formed in a ring shape corresponding to the shape of the 1st opening part 12a.

The valve frame seal packing 61 consists of a seal part which consists of an O-ring etc., for example. The valve frame seal packing 61 can be closely attached to the valve case inner surface 10A located around the first opening 12a.

The valve frame seal packing (61) is arranged concentrically to the movable valve frame part (60).

The valve frame seal packing 61 is provided in the position adjacent to the outermost periphery in the outer peripheral crank part 60c. The valve frame seal packing 61 is in contact with the valve case inner surface 10A serving as the periphery of the first opening 12a when the valve is closed, and is pressed by the movable valve frame portion 60 and the valve case inner surface 10A. . For this reason, it will be in the state into which the 1st space and the 2nd space were divided.

The movable valve plate part 50 consists of a plate body which has a circular outline substantially concentric with the circular part 30a.

The movable valve plate part 50 is fitted in the radial direction of the outer peripheral crank part 60c in the movable valve frame part 60. As shown in FIG. The movable valve frame part 60 is arrange|positioned so that the periphery of the movable valve board part 50 may be enclosed in the position used as the radial direction outer side of the movable valve plate part 50. As shown in FIG.

The inner peripheral crank part 50c of the movable valve plate part 50 and the movable valve frame part 60 consist of a concentric double annular ring. The movable valve plate part 50 is made to be slidable in the flow path H direction with respect to the movable valve frame part 60. As shown in FIG. The movable valve plate part 50 is made to be movable in the flow path H direction with respect to the movable valve frame part 60 .

Here, the movable valve plate part 50 is made to be movable between the following three positions.

The first position is a position in which the movable valve plate part 50 can perform pendulum operation in the same manner with respect to the movable valve frame part 60 and the neutral valve part 30 which are in a position where pendulum operation is possible.

The second position is the same position as the movable valve plate portion 50 with respect to the movable valve frame portion 60 in the first position when the movable valve frame portion 60 is in a position capable of contacting the first opening portion 12a. .

The 3rd position is a position where the movable valve plate part 50 can contact the 2nd opening part 12b with respect to the movable valve frame part 60 in a 2nd position.

The movable valve plate part 50 has the inner peripheral crank part 50c and the valve plate 50d.

As for the movable valve plate part 50, the inner peripheral crank part 50c is cast in the peripheral position of the surface opposing the 1st opening part 12a in the valve plate 50d, and the cross-sectional shape passing through a diameter is substantially U-shaped. is in shape. The valve plate 50d is provided so as to seal the radially inner side of the inner peripheral crank portion 50c. The valve plate 50d has a flat plate shape disposed in a direction substantially perpendicular to the flow path H direction.

The inner peripheral crank portion 50c is formed in a ring shape or a cylindrical shape having an axial dimension shorter than a radial dimension. The inner periphery crank portion 50c is formed on the entire periphery at the outer periphery of the movable valve plate portion 50 . The inner peripheral crank portion 50c has an outer peripheral contour slightly larger than that of the first opening portion 12a and/or the second opening portion 12b. The inner peripheral crank portion 50c has an inner peripheral contour slightly smaller than that of the first opening portion 12a and/or the second opening portion 12b.

The inner peripheral crank part 50c has a smaller thickness dimension than the outer peripheral crank part 60c, ie, the dimension in the flow path H direction. The inner peripheral crank part 50c has a larger thickness dimension than the valve plate 50d, ie, the dimension in the flow path H direction.

The inner peripheral crank portion 50c has a sliding surface 50b. The sliding surface 50b is a cylindrical surface having an axis line parallel to the flow path H direction. The sliding surface 50b is provided on the entire length in the circumferential direction from the outer peripheral surface of the inner peripheral crank portion 50c. The inner peripheral crank part 50c and the outer peripheral crank part 60c are fitted in the state in which the sliding surface 50b and the sliding surface 60b contacted. The sliding surface 50b and the sliding surface 60b of the movable valve frame part 60 are mutually slidable, and are located in the opposite state.

In the inner peripheral crank part 50c, the bias hole 58 in which the valve plate bias part 80 is accommodated and the circumferential groove 59 are arrange|positioned alternately in the circumferential direction of the movable valve plate part 50. As shown in FIG. A plurality of valve plate biasing portions 80 are provided at equal intervals spaced apart from each other in the circumferential direction of the movable valve plate portion 50 . Three or more locations are preferable for the location where the some valve plate biasing part 80 is provided.

In this embodiment, when viewed from the center O of the valve plate 50d as the arrangement of the valve plate biasing portions 80 spaced apart from each other, the four valve plate biasing portions 80 are spaced apart at the same angular position (90 degrees). A configuration example arranged so as to be described is shown.

When viewed from the center O of the valve plate 50d, the angular position of the valve plate biasing portion 80 overlaps the angular position of the valve case biasing portion 70 and the valve frame biasing portion 90 .

The bias hole 58 is provided at equal intervals in the circumferential direction of the inner circumferential crank part 50c, corresponding to the arrangement of the valve plate bias part 80 as described above.

The circumferential groove 59 is cast in the circumferential direction of the inner circumferential crank portion 50c so as to tie between the adjacent sub-fine hole 58 .

The bias hole 58 and the circumferential groove 59 have openings on the surface opposite to the first opening 12a of the inner peripheral crank portion 50c in the flow path H direction.

In the inner peripheral crank portion 50c, an inner peripheral wall 59a, an outer peripheral wall 59b, and an inner peripheral wall 59a which are erected in the flow path H direction between the peripheral grooves 59 by a peripheral groove 59 ) and the bottom portion 59c between the outer peripheral wall 59b is formed.

The inner peripheral wall 59a and the outer peripheral wall 59b extend in the flow path H direction. The bottom portion 59c extends in a direction orthogonal to the direction of the flow path H substantially parallel to the valve plate 50d. The inner peripheral wall 59a is cast inside the peripheral groove 59 in the radial direction of the movable valve plate part 50 .

The circumferential groove 59 is provided with a curved portion 59d that curves and connects between the surface (bottom surface) of the bottom portion 59c and the surface (side surface) of the inner peripheral wall 59a. The circumferential groove 59 is provided with a curved portion 59e that curves and connects between the surface (bottom surface) of the bottom portion 59c and the surface (side surface) of the outer peripheral wall 59b.

The bottom 59c of the circumferential groove 59 is positioned closer to the first opening 12a in the flow path H direction than the bottom 58c of the bias hole 58 . The bottom portion 59c of the circumferential groove 59 is thicker than the bottom portion 58c of the bias hole 58 .

The bias hole 58 makes it possible to accommodate the valve plate bias part 80, which will be described later, and is formed in a substantially cylindrical shape.

The bottom portion 58c of the sub-fine hole 58 has a planar shape. A curved portion having the same radius of curvature as the curved portions 59d and 59e may not be provided.

A valve plate 50d is connected to the inner peripheral wall 59a in the radial direction inside the movable valve plate part 50 .

In the movable valve plate portion (50), the inner peripheral wall (59a) of the inner peripheral crank portion (50c) and the peripheral portion of the valve plate (50d) have an opening in the peripheral groove (59) rather than the bottom part (59c) of the peripheral groove (59). connected at a location close to

Further, on the radially inner side of the inner circumferential wall 59a, in the thickness direction of the movable valve plate portion 50 serving as the flow path H direction, closer to the first opening 12a than the central position of the inner circumferential crank portion 50c It is preferable that the valve plate 50d be connected to the position.

Incidentally, as a position where the inner peripheral wall 59a and the valve plate 50d are connected, in the flow path H direction, from an end position of the inner peripheral wall 59a which is a position close to the first opening 12a, the inner peripheral crank portion (50c) can be appropriately set up to the center position.

The inner circumferential wall 59a is a position at which the inner circumferential wall 59a and the valve plate 50d are connected, in the flow path H direction, closer to the first opening 12a than the central position of the inner circumferential crank portion 50c. It can be set to a position close to the end of

A sliding surface 50b is cast on the outer peripheral wall 59b on the radially outer side of the movable valve plate portion 50 . On the outer peripheral wall 59b, the sliding seal packing 52 (sliding seal member) which consists of an O-ring etc. as a plate sliding seal part is arrange|positioned on the radial direction outer side of the movable valve plate part 50. As shown in FIG. The groove 52m for accommodating the sliding seal packing 52 is cast in the outer peripheral wall 59b.

The sliding seal packing 52 is provided at a position closer to the opening of the circumferential groove 59 than the outer circumferential groove 56 , that is, at a position closer to the end of the outer circumferential wall 59b in the flow path H direction.

The groove 52m is provided in a position closer to the opening of the peripheral groove 59 than the peripheral groove 56, that is, in a position closer to the end of the outer peripheral wall 59b in the flow path H direction. The groove 52m is arrange|positioned at the position adjacent to the 1st opening part 12a of the outer peripheral wall 59b in the thickness direction of the movable valve plate part 50 used as the flow path H direction.

The protrusion in which the groove|channel 51m was provided is cast in the position used as the radial direction outer side of the movable valve plate part 50 by the outer peripheral wall 59b. The protrusion provided with the groove 51m is located adjacent to the 2nd opening part 12b of the outer peripheral wall 59b in the thickness direction of the movable valve plate part 50 used as the flow path H direction.

The groove 51m is located outside the outer peripheral wall 59b in the radial direction of the movable valve plate part 50 .

The groove 51m accommodates a counter cushion 51 (seal member), which will be described later. The groove 51m is provided in the cross section used as the position adjacent to the 2nd opening part 12b in the protrusion.

In the radial direction of the movable valve plate part 50, the outer peripheral groove 56 is provided in the outer peripheral surface of the outer peripheral wall 59b.

The outer circumferential groove 56 is located between the groove 52m and the groove 51m in the flow path H direction. The outer circumferential groove 56 is disposed so as not to contact the sliding seal packing 52 .

The sliding seal packing 52 is arrange|positioned between the inner peripheral crank part 50c and the outer peripheral crank part 60c. By the sliding seal packing 52, the sealing state of the sliding surface 50b and sliding surface 60b at the time of sliding is maintained.

The sliding surface 50b, the sliding seal packing 52, and the sliding surface 60b constitute a plate sliding seal part.

The movable valve plate portion 50 and the movable valve frame portion 60 are connected by a valve plate biasing portion 80 .

The movable valve plate portion 50 and the movable valve frame portion 60 can slide relative to each other in the reciprocating directions indicated by reference numerals B1 and B2 in FIG. 12 . The reciprocating directions B1 and B2 are directions perpendicular to the surfaces of the movable valve plate part 50 and the movable valve frame part 60 . The reciprocating directions B1 and B2 are the flow path H directions parallel to the axial direction of the rotation shaft 20 .

A counter cushion 51 is cast on the movable valve plate portion 50 on a surface facing (abutting) the valve case inner surface 10B.

The counter cushion 51 is formed in a ring shape corresponding to the shape of the second opening portion 12b. The counter cushion 51 is an elastic body. The counter cushion 51 can be closely attached to the valve case inner surface 10B, which becomes the periphery of the second opening portion 12b when the valve is closed.

The counter cushion 51 consists of a seal part made of an O-ring or the like.

The counter cushion 51 is provided in the end face of the inner peripheral crank part 50c opposite to the 2nd opening part 12b. The counter cushion 51 is provided at the outermost periphery position in the inner periphery crank part 50c.

The counter cushion 51 is in contact with the valve case inner surface 10B serving as the periphery of the second opening portion 12b when the valve is closed, and is pressed by the movable valve plate portion 50 and the valve case inner surface 10B.

For this reason, it will be in the state into which the 1st space and the 2nd space were divided.

The counter cushion 51 elastically deforms when the movable valve plate part 50 and the valve case inner surface 10B collide. The counter cushion 51 relieves the impact when the movable valve plate part 50 collides with the valve case inner surface 10B. For this reason, it becomes possible to prevent generation|occurrence|production of a garbage.

The counter cushion 51, the sliding seal packing 52, and the valve frame seal packing 61 are arrange|positioned on the substantially same cylindrical surface. The counter cushion 51, the sliding seal packing 52, and the valve frame seal packing 61 are arrange|positioned so that they may overlap with each other when seen from the flow path H direction. For this reason, a back pressure cancellation rate of about 100% can be obtained.

An air bleed hole 53 is provided in the movable valve plate portion 50 .

The air bleed hole 53 communicates with the inside of the outer circumferential groove 56 and the surface opposite to the second opening 12b of the inner crank portion 50c at a position closer to the center O than the counter cushion 51 . do.

When the movable valve plate part 50 and the valve case inner surface 10B collide, the sealed space is formed by the movable valve plate part 50, the valve case inner surface 10B, and the counter cushion 51. As shown in FIG. The air evacuation hole 53 removes gas from this sealed space.

The valve plate biasing part 80 is incorporated in the biasing part hole 58 of the movable valve plate part 50 .

The valve plate biasing part 80 is a region where the movable valve frame part 60 and the movable valve plate part 50 overlap, that is, the inner frame plate 60d of the movable valve frame part 60 and the movable valve when viewed from the flow path H direction. It is disposed on the inner peripheral crank portion 50c of the plate portion 50 .

A plurality of valve plate biasing portions 80 are provided at equal intervals spaced apart from each other in the circumferential direction of the movable valve plate portion 50 . As for the location where the valve plate biasing part 80 is provided, three or more locations are preferable. Two of the valve plate biasing parts 80 are arrange|positioned as a set (set). A set of valve plate biasing parts 80 are respectively arrange|positioned at the position used as both ends of the diameter passing through the center O of the movable valve plate part 50.

The plurality of valve plate biasing portions 80 are provided in a circumferential direction of the movable valve plate portion 50 to be spaced apart from each other for every set (set).

As a specific arrangement of the plurality of valve plate biasing parts 80, as shown in FIG. 14, when viewed from the center O of the valve plate 50d, the four valve plate biasing parts 80 are at the same angular position (90°). ) can represent the configuration arranged in

The valve plate biasing part 80 induces (regulates) the movement of the movable valve plate part 50 in the flow path H direction. The valve plate biasing part 80 can change the thickness dimension used as the flow path H direction between the movable valve frame part 60 and the movable valve plate part 50. The valve plate biasing part 80 interlocks the movable valve plate part 50 in the reciprocating directions B1 and B2 in which the movable valve frame part 60 moves.

It is an enlarged sectional view along the flow path which shows the valve case biasing part of the gate valve in this embodiment, a valve frame biasing part, and a valve plate biasing part.

The valve plate biasing part 80 connects the inner frame plate 60d of the movable valve frame part 60 and the inner peripheral crank part 50c of the movable valve board part 50 .

The valve plate biasing portion 80 includes a plate guide pin 81 , a coil spring 82 , a pressure receiving portion 83 , a lid portion 58f , and a regulating cylinder ( 85).

The plate guide pin 81 is constituted by a rod-shaped body having a substantially uniform thickness. The plate guide pin 81 is formed in a bolt shape. The plate guide pin 81 penetrates the inside of the valve plate bias part 80 . The plate guide pins 81 are erected in the flow path H direction. The base part 81b of the plate guide pin 81 is fixed to the inner frame plate 60d of the movable valve frame part 60. As shown in FIG. The base part 81b of the plate guide pin 81 penetrates the inner frame plate 60d. The long axis portion of the plate guide pin 81 is erected from the inner frame plate 60d toward the bias hole 58 .

The plate guide pin 81 is disposed coaxially with the bias hole 58 of the inner peripheral crank portion 50c. The tip 81a of the plate guide pin 81 is located inside the bias hole 58 . At the tip 81a of the plate guide pin 81 , a pressure receiving part 83 having a diameter larger than that of the long axis of the plate guide pin 81 is provided.

The pressure receiving portion 83 is disposed at a position such that it can abut against the bottom portion 58c of the bias hole 58 or does not abut against the bottom portion 58c. The pressure receiving part 83 is cast in a flange shape on the tip 81a of the plate guide pin 81 . The pressure receiving portion 83 protrudes from the plate guide pin 81 radially outward.

On the long axis of the plate guide pin 81 , a regulating cylinder 85 is slidably positioned on the outer side in the radial direction.

The regulating cylinder 85 has a cylindrical shape coaxial with the long axis of the plate guide pin 81 . The regulating cylinder 85 regulates the sliding position and sliding direction of the plate guide pin 81 . One end of the regulating cylinder 85 is connected to a lid portion 58f that closes the bias hole 58 . The axial dimension of the control cylinder 85 is smaller than the axial dimension of the plate guide pin 81 . A bush 85a in contact with the plate guide pin 81 is disposed inside the regulating cylinder 85 in the radial direction.

The lid portion 58f is disposed so as to block the opening of the bias hole 58 . The lid portion 58f is fixed at the opening position of the bias hole 58 . A hole 58g is provided in the lid portion 58f as a through hole.

The hole 58g is coaxial with the regulating cylinder 85 and has the same diameter. A plate guide pin 81 is fitted to the hole 58g and the regulating cylinder 85 .

At a position close to the lid portion 58f of the inner frame plate 60d, further, a fixed lid 58f1 is provided so as to be in contact with the lid portion 58f. The fixed lid 58f1 reinforces the fixing of the lid portion 58f to the opening of the bias hole 58 . A through hole larger than the hole 58g is concentrically provided in the fixed lid 58f1.

The coil spring 82 (holding spring) is made of, for example, an elastic member such as a screw-type spring. The coil spring 82 is arranged to have a bias axis parallel to the axis line of the bias hole 58 . The coil spring 82 is incorporated in the bias hole 58 of the movable valve plate portion 50 . The coil spring 82 is made of a double helix, and has an inner coil spring 82a and an outer coil spring 82b having different diameter dimensions.

Both the inner coil spring 82a and the outer coil spring 82b are disposed coaxially with the plate guide pin 81 .

Although the coil spring 82 was provided double and reinforced the biasing force, it can also be set as single fold.

The coil spring 82 has one end in contact with the lid portion 58f and the other end in contact with the pressure receiving portion 83 . A force is applied to the coil spring 82 so as to press the lid portion 58f and the pressure receiving portion 83 .

In the lid portion 58f and the fixed lid 58f1, the air that communicates with the bottom portion 58c vicinity and the space at a position closer to the inner frame plate 60d than the lid portion 58f inside the bias hole 58 An extraction hole 85b is provided.

In the base part 81b and the inner frame plate 60d of the plate guide pin 81, the space which becomes a position closer to the inner frame plate 60d than the lid part 58f, and the valve case inner surface 10A rather than the inner frame plate 60d ) is provided with an air bleed hole (85c) for communicating the hollow portion (11) adjacent to.

A sealing member 85d such as an O-ring may be cast at a position closer to the lid portion 58f than the bush 85a of the regulating cylinder 85 .

When the plate guide pin 81 and the regulating cylinder 85 slide in the axial direction to each other, the axial angle between the plate guide pin 81 and the regulating cylinder 85 does not change, and the plate guide pin 81 and The position in the flow path H direction with the regulating cylinder 85 changes. For this reason, the inner frame plate 60d fixed to the base part 81b of the plate guide pin 81, and the lid part 58f to which the one end of the regulating cylinder 85 was fixed mutually move in the flow path H direction. do. For this reason, the position regulation of the movable valve frame part 60 and the movable valve plate part 50 is guide|induced.

The coil spring 82 presses the lid part 58f and the pressure receiving part 83 in the mutually spaced direction.

Since the pressure receiving part 83, the tip 81a of the plate guide pin 81, the base part 81b of the plate guide pin 81, and the inner frame plate 60d are mutually fixed, the mutual positional relationship changes. I never do that. For this reason, the coil spring 82 always applies force to the lid part 58f and the pressure receiving part 83 in the direction in which the lid part 58f and the inner frame plate 60d adjoin in the flow path H direction. .

Here, when it moves in the flow path H direction so that the inner frame plate 60d and the lid part 58f may be spaced apart, the distance between the lid part 58f and the pressure receiving part 83 decreases. For this reason, the coil spring 82 contracts. Also in this case, since the pressure receiving part 83, the tip 81a of the plate guide pin 81, the base part 81b of the plate guide pin 81, and the inner frame plate 60d are mutually fixed, the positional relationship does not change

For this reason, the contracted coil spring 82 exerts more force on the lid part 58f and the pressure receiving part 83 in the direction in which the lid part 58f and the inner frame plate 60d adjoin in the flow path H direction. apply For this reason, the movable valve plate part 50 and the movable valve frame part 60 mutually move in the direction in which the diameter-expanded pressure receiving part 83 of the lid part 58f and the plate guide pin 81 is spaced apart.

In the valve plate biasing part 80, when the movable valve plate part 50 and the movable valve frame part 60 slide to each other, the plate guide pin 81 penetrating the hole 58g, the regulating cylinder 85 ( It moves in the axial direction of the plate guide pin 81 with respect to the lid part 58f and the regulating cylinder 85 in a state regulated by the axial direction by the bush 85a). Then, the coil spring 82 contracts in the axial direction of the plate guide pin 81 . By the contracted coil spring 82 , a force is applied to the lid portion 58f occupying the bias hole 58 in a direction adjacent to the inner frame plate 60d of the movable valve frame portion 60 .

For this reason, the movable valve plate part 50 and the movable valve frame part 60 receive the biasing force of the valve plate biasing part 80 in the direction in which the thickness dimension of the flow path H direction reduces.

By the valve plate biasing part 80, when the movable valve plate part 50 and the movable valve frame part 60 mutually slide, a sliding direction can be regulated so that it may not shift|deviate from reciprocating direction B1, B2.

Moreover, even when the movable valve board part 50 and the movable valve frame part 60 slide, the attitude|position of the movable valve board part 50 and the movable valve frame part 60 does not change, but a parallel movement can be performed.

The valve plate biasing part 80 and the valve frame biasing part 90 are provided so as to have a biasing force capable of applying a force in the direction of the flow path H which is opposite to each other.

The valve frame biasing portion 90 is a circular flange portion 30c of the neutral valve portion 30 and an outer frame plate serving as a position regulating portion of the movable valve frame portion 60 overlapping the circular flange portion 30c when viewed from the flow path (H) direction. (60e) is placed in between. The valve frame biasing part 90 applies a force to the neutral valve part 30 toward the central position of the movable valve frame part 60 in the flow path H direction.

The valve frame biasing part 90 is incorporated in the biasing part hole 68 of the outer frame plate 60e. The valve frame biasing portion 90 is a region where the neutral valve portion 30 and the movable valve frame portion 60 overlap, that is, the circular flange portion 30c of the neutral valve portion 30 and movable when viewed from the flow path H direction. It is disposed on the outer frame plate 60e of the valve frame unit 60 .

A plurality of valve frame biasing portions 90 are provided at equal intervals spaced apart from each other in the circumferential direction of the circular flange portion 30c. Three or more places are good corresponding to the valve plate biasing part 80 in the location where the valve frame biasing part 90 is provided. Two of the valve frame biasing parts 90 are arrange|positioned as a set (set). A set of valve frame biasing portions 90 are respectively arranged at positions serving as both ends of a diameter passing through the center O of the movable valve frame portion 60 .

The plurality of valve frame biasing portions 90 are provided to be spaced apart from each other in the circumferential direction of the movable valve frame portion 60 for each set (set). As a specific arrangement of the plurality of valve frame biasing portions 90, in Fig. 14, when viewed from the center O of the movable valve frame portion 60, the four valve frame biasing portions 90 are at the same angular position (90°). It can represent a deployed configuration.

When viewed from the center O of the valve plate 50d, the angular position of the valve frame biasing portion 90 in the circumferential direction of the circular flange portion 30c is the valve plate portion in the circumferential direction of the movable valve board portion 50. It is configured to overlap the angular position of the detail 80 . The valve frame biasing part 90 and the valve plate biasing part 80 are arranged on the same straight line passing through the center O of the valve plate 50d. The valve frame biasing part 90 is arrange|positioned at the position spaced apart from the center O of the valve plate 50d rather than the valve plate biasing part 80 on the straight line passing through the center O.

The valve frame biasing part 90 induces (regulates) the movement of the neutral valve part 30 and the movable valve frame part 60 in the flow path H direction. As for the valve frame biasing part 90, the thickness dimension used as the flow path H direction of the neutral valve part 30 and the movable valve frame part 60 can be changed. The valve frame biasing portion 90 reciprocates the movable valve frame portion 60 in the reciprocating directions B1 and B2 with respect to the circular flange portion 30c.

The valve frame biasing portion 90 connects the circular flange portion 30c of the neutral valve portion 30 and the outer frame plate 60e of the movable valve frame portion 60 . The bias hole 68 is provided in the outer frame plate 60e of the movable valve frame part 60 . The sub-hole 68 is formed in a cylindrical shape having an axial line in the flow path H direction. The bias hole 68 is provided so as to penetrate the outer frame plate 60e of the movable valve frame portion 60 .

In the bias hole 68 , the opening on the surface of the outer frame plate 60e opposite to the second opening 12b is blocked by the pressure receiving part 93 as will be described later. In the sub-hole 68 , in the flow path H direction, the opening at a position close to the first opening 12a is not blocked. That is, the bias hole 68 opens in the same direction as the bias hole 58 of the movable valve plate part 50 . The bias hole 68 is provided in a position close to the outer peripheral crank portion 60c close to the radially inner side in the radial direction of the movable valve frame portion 60 to the outer frame plate 60e.

The valve frame biasing part 90 has a rim guide pin 91 , a rim coil spring 92 , and a regulating cylinder 95 .

The edge guide pin 91 is constituted by a rod-shaped body having a substantially uniform thickness. The rim guide pin 91 penetrates the inside of the valve frame bias part 90 . The edge guide pins 91 are erected in the flow path H direction. The frame guide pin 91 is fixed to the outer frame plate 60e of the movable valve frame part 60 . The edge guide pin 91 is arranged coaxially with the sub-hole 68 of the outer frame plate 60e. The base portion 91b of the frame guide pin 91 is provided with a pressure receiving portion 93 whose diameter is larger than that of the long axis of the frame guide pin 91 .

The pressure receiving portion 93 is fixed at a position opposite to the second opening 12b in the flow path H direction in the bias hole 68 . The pressure receiving portion 93 blocks the opening directed to the second opening 12b in the flow path H direction in the bias hole 68 . The pressure receiving portion 93 forms the bottom of the bias hole 68 . That is, the base portion 91b of the edge guide pin 91 forms the bottom of the bias hole 68 as the pressure receiving portion 93 . The pressure receiving portion 93 may be screw-engaged to the opening of the biasing portion hole 68 . In this case, the edge guide pin 91 may be formed in a bolt shape.

The pressure receiving part 93 is exposed on the surface of the movable valve frame part 60 opposite to the valve case biasing part 70 mentioned later. The base portion 91b of the frame guide pin 91 is fixed to the outer frame plate 60e of the movable valve frame portion 60 .

The long axis part of the frame guide pin 91 is erected toward the circular flange part 30c from the bias part hole 68 of the outer frame plate 60e. The circular flange portion 30c is provided with a recessed portion 30cm on the surface opposite to the first opening 12a.

A through hole 30g passing through the circular flange portion 30c in the flow path H direction is provided at the central position of the recess 30cm.

A position close to the tip 91a of the edge guide pin 91 penetrates through the through hole 30g so as to be slidable.

Therefore, the front-end|tip 91a of the edge guide pin 91 penetrates the circular flange part 30c. The tip 91a of the edge guide pin 91 can be located in the recessed portion 30cm provided in the circular flange portion 30c. The axial length of the tip 91a of the edge guide pin 91 is set so as not to be closer to the valve case inner surface 10A than the valve frame seal packing 61 in the flow path H direction.

A neutral spacer 94 is provided around the tip 91a of the edge guide pin 91 .

The neutral spacer 94 is attached to the tip 91a position of the edge guide pin 91 by a C-ring 94a. The neutral spacer 94, the C-ring 94a can be located inside the recess 30cm.

A control cylinder 95 slidable with respect to the edge guide pin 91 is located radially outside the long shaft portion located in the center of the edge guide pin 91 in the axial direction.

The regulating cylinder 95 has a cylindrical shape coaxial with the long axis of the edge guide pin 91 . The regulating cylinder 95 regulates the sliding position and sliding direction of the edge guide pin 91 . The axial dimension of the regulating cylinder 95 is smaller than the axial dimension of the edge guide pin 91 . A bush 95a in contact with the edge guide pin 91 is disposed inside the regulating cylinder 95 in the radial direction.

At one end of the regulating cylinder 95, a flange portion 95f is cast.

The flange part 95f is fixedly connected to the position used as the back surface of the recessed part 30cm in the circular flange part 30c. The regulating cylinder 95 is fixed to the surface opposite to the outer frame plate 60e in the circular flange part 30c by the flange part 95f.

The flange portion 95f and the regulating cylinder 95 have a through hole 95g extending in the flow path H direction. The through hole 95g communicates with the flange portion 95f and the regulating cylinder 95 . The through-hole 95g consists of a position coaxial with the through-hole 30g. Similar to the through hole 30g, a position close to the tip 91a of the edge guide pin 91 penetrates through the through hole 95g so as to be slidable.

The frame coil spring 92 constitutes the valve frame biasing portion 90 as an auxiliary spring. The edge coil spring 92 is housed inside the bias hole 68 . The edge coil spring 92 is arranged in a coaxial state at a position to be around the edge guide pin 91 .

The edge coil spring 92 is made of, for example, an elastic member such as a spring, and is arranged to have a biasing axis parallel to the axis of the biasing part hole 68 .

One end of the edge coil spring 92 is in contact with the pressure receiving portion 93 that is around the base portion 91b in the edge guide pin 91 . The other end of the frame coil spring 92 is in contact with a flange portion 95f surrounding the through hole 95g. The rim coil spring 92 applies a force to the periphery of the base portion 91b of the rim guide pin 91 and the flange portion 95f around the through hole 95g in the direction opposite to the flow path H direction, respectively. add

The edging coil spring 92 can also strengthen the biasing force as a structure which consists of a double coil spring, for example.

In the valve frame biasing portion 90 , when the movable valve frame portion 60 moves with respect to the neutral valve portion 30 , the axial direction of the through hole 95g of the regulating cylinder 95 fixed to the circular flange portion 30c is , the edge guide pin 91 moves in the axial direction. At this time, the edge guide pin 91 slides with respect to the bush 95a. Then, the tip 91a of the edge guide pin 91 protrudes from the recess 30cm toward the valve case inner surface 10A.

For this reason, the flange part 95f of the regulating cylinder 95 and the pressure receiving part 93 which is the bottom part of the biasing part hole 68 adjoin in the flow path H direction. At this time, the edge coil spring 92 contracts. By the biasing force of the contracted edge coil spring 92, the pressure receiving portion 93 and the flange portion 95f are pressed in a direction to be spaced apart from each other.

That is, the pressure receiving part 93 of the bottom part of the bias hole 68 and the flange part 95f of the back surface of the circular flange part 30c are position-moved so that it may be spaced apart from each other in the flow path H direction. For this reason, the movable valve frame part 60 is moved with respect to the neutral valve part 30 .

Thus, by the valve frame biasing part 90, the thickness dimension in the flow path H direction of the neutral valve part 30 and the movable valve frame part 60 becomes changeable. The valve frame biasing part 90 moves the movable valve frame part 60 to the reciprocating directions B1 and B2 with respect to the neutral valve part 30 which does not positionally move in the flow path H direction.

At this time, in the valve frame biasing portion 90 , the axial direction of the rim guide pin of the regulating cylinder 95 does not incline. When the movable valve frame part 60 is positionally moved in the flow path (H) direction with respect to the neutral valve part 30 by the valve frame biasing part 90, the moving direction of the movable valve frame part 60 is the reciprocating direction B1. , B2) is regulated so as not to deviate from it. Therefore, the movable valve frame part 60 moves in parallel with respect to the neutral valve part 30 without changing.

At the same time, it is possible to restrict the movable valve frame unit 60 from moving out of the flow path (H) direction with respect to the neutral valve unit 30 . Specifically, the movable valve frame part 60 fitted to the circular part 30a can be prevented from moving in the circumferential direction. For this reason, in the pendulum operation of the valve body 5, the holding state of the movable valve frame part 60 with respect to the neutral valve part 30 can be stabilized, and the operation stability of the gate valve 100 can be improved.

In addition, even when the movable valve frame part 60 moves in the flow path (H) direction with respect to the neutral valve part 30, as the edge guide pin 91 and the plate guide pin 81 are parallel, the valve plate bias part By (80), the movable valve plate part 50 follows and moves in the reciprocating direction (B1, B2). Incidentally, an exception is made when the differential pressure in the flow path H direction is applied to the valve plate 50d.

Here, with respect to the positional movement of the movable valve frame part 60 in the flow path H direction, the neutral valve part 30 and the movable valve plate part ( When 50) and the movable valve frame part 60 slide with each other, this sliding direction can be regulated so as not to deviate from the reciprocating directions B1 and B2. In addition, even when the neutral valve part 30, the movable valve plate part 50, and the movable valve frame part 60 slide, the neutral valve part 30, the movable valve plate part 50, and the movable valve frame part 60 mutually The posture does not change, and relatively parallel movement can be performed.

A plurality of valve case biasing portions 70 are incorporated in the valve case 10 .

The valve case biasing portion 70 constitutes a lifting mechanism that presses the movable valve frame portion 60 in a direction toward the seal surface. The valve case biasing part 70 is a position where it is possible to apply a force to the movable valve frame part 60 in a direction close to the first opening part 12a with respect to the flow path H direction, that is, the second opening part 12b. placed in the surrounding position.

The valve case biasing part 70 is composed of the valve case biasing part 70 in the first to second embodiments.

In the valve case biasing part 70 in the present embodiment, the expansion and contraction rod 72 is made to be extensible from the fixing part 71 along the flow path H direction to the direction adjacent to the first opening part 12a.

The valve case biasing portion 70 is provided with a multi-stage seal structure so that oil, which is a working fluid, does not leak into the hollow portion 11 serving as the vacuum side during hydraulic driving.

A ring-shaped sealing member (O-ring) 77f is provided around the telescopic rod 72 , for example, at a position close to the movable valve frame part 60 . The elastic rod 72 is made expandable and contractible in the state which sealed the boundary between the fixed part 71 and the hollow part 11 used as a vacuum side.

The valve case biasing part 70 has a function of moving the movable valve frame part 60 toward the 1st opening part 12a. The valve case biasing part 70 makes the movable valve frame part 60 abut against the valve case inner surface 10A, presses the movable valve frame part 60 against the valve case inner surface 10A, and closes the flow path H. (valve closing action).

The valve case biasing portion 70 is disposed in the valve case 10 as a position that can be pushed without changing the posture of the movable valve frame portion 60 . Specifically, the valve case biasing portion 70 is arranged so that the axis of the expansion and contraction rod 72 coincides with the axis of the frame guide pin 91 of the valve frame biasing portion 90 .

The position where the tip portion 72a of the telescopic rod 72 presses the valve frame biasing portion 90 is arranged so as to become the base portion 91b of the frame guide pin 91 . That is, the position where the tip portion 72a of the telescopic rod 72 presses the valve frame biasing portion 90 is arranged so as to become the pressure receiving portion 93 of the frame guide pin 91 .

The plurality of valve case biasing portions 70 are provided to be spaced apart from each other along the periphery of the second opening portion 12b. A plurality of valve case biasing portions 70 are provided at equal intervals spaced apart from each other in the circumferential direction of the outline of the second opening portion 12b.

Three or more places are good corresponding to the valve frame biasing part 90 in the location where the valve case biasing part 70 is provided. Two of the valve case biasing parts 70 are arrange|positioned as a set (set). A set of valve case biasing portions 70 are respectively disposed at positions outside the radial direction of both ends in a diameter (straight line) passing through the center O of the second opening portion 12b. A set of valve case biasing parts 70 are arranged at positions that are both ends of a diameter passing through the center O of the movable valve frame part 60 , similarly to the valve frame biasing part 90 .

The plurality of valve case biasing portions 70 are provided to be spaced apart from each other in the circumferential direction of the outline of the second opening portion 12b for each set (set). As a specific arrangement of the plurality of valve case biasing parts 70, in Fig. 14, when viewed from the center O of the second opening 12b, the four valve case biasing parts 70 are positioned at the same angular position (90°). It can represent a deployed configuration.

The angular position of the valve case biasing part 70 in the circumferential direction of the circular flange part 30c when viewed from the center O of the second opening part 12b is the valve plate in the circumferential direction of the movable valve plate part 50 . It is configured to overlap the angular position of the biasing portion 80 and the valve frame biasing portion 90 .

The valve case biasing part 70, the valve frame biasing part 90, and the valve plate biasing part 80 are arranged on the same straight line passing through the center O of the valve plate 50d. The valve case biasing part 70 is spaced apart from the center O of the valve plate 50d from the valve plate biasing part 80 on a straight line passing through the center O, similarly to the valve frame biasing part 90 . placed in one position.

When the valve case biasing portion 70 is changed from the flow path communication state ( FIGS. 13 and 15 ) in the valve opening blocking position to the valve closed state ( FIGS. 16 to 19 ), the expansion and contraction rod is operated by hydraulic pressure. (72) is stretched.

At this time, the valve case biasing portion 70 applies a force to the movable valve frame portion 60 in contact with the tip portion 72a. For this reason, the movable valve frame part 60 moves toward the 1st opening part 12a in the flow path H direction. The valve frame seal packing 61 is in close contact with the valve case inner surface 10A around the first opening 12a.

In the plurality of valve case biasing parts 70 , all of the expansion operations of the expansion and contraction rod 72 are operable almost simultaneously.

Here, the front-end|tip part 72a of the telescopic rod 72 abuts against the pressure receiving part 93 at the position which extended the axis line of the telescopic rod 72. As shown in FIG. Since the pressure receiving portion 93 is fixed to the bottom position of the bias hole 68, the pressing force of the expansion rod 72 is applied through the pressure receiving portion 93 and the outer frame plate 60e to the outer crank portion ( 60c).

At this time, the position regulation with respect to the neutral valve part 30 of the movable valve frame part 60 is performed by the edge guide pin 91 and the regulating cylinder 95. As shown in FIG. Since the axis of the frame guide pin 91 coincides with the axis of the expansion rod 72 , the movable valve frame unit 60 moves in the flow path H direction with respect to the neutral valve unit 30 in the direction of movement. With respect to , the pressing force in this moving direction acts in the same position and direction.

Hereinafter, the operation of the gate valve 100 according to the present embodiment will be described in detail.

First, in the gate valve 100 according to the present embodiment, the valve body 5 is in the retracted position made of the hollow part 11 in which the flow path H is not provided, as shown by the broken line in FIG. 11 . think. At this time, the movable valve part 40 was not in contact with either of the valve case inner surface 10A and the valve case inner surface 10B.

In this state, the rotation shaft driving unit 200 rotates the rotation shaft 20 in the direction indicated by the reference symbol R01 (the direction intersecting the direction of the flow path H). Then, the neutral valve part 30 and the movable valve part 40 rotationally move in pendulum motion along the direction R01. By this rotation, the valve body 5 moves from the retracted position to the valve opening blocking position which consists of a position opposing the 1st opening part 12a as shown by the solid line in FIG.

With the valve body 5 in the valve opening blocking position, the valve case biasing portion 70 extends the expansion rod 72 in a direction adjacent to the first opening 12a in the flow path H direction. do. The expansion and contraction rod 72 abuts against the movable valve frame part 60 and presses the movable valve frame part 60 . The movable valve frame part 60 moves in the direction adjacent to the 1st opening part 12a.

By means of the valve case biasing portion 70, the movable valve frame portion 60 abuts against the valve case inner surface 10A. At this time, the valve frame seal packing 61 is in close contact with the valve case inner surface 10A located around the 1st opening part 12a. For this reason, as shown in FIGS. 16-19, the flow path H is closed (valve closing operation|movement).

Conversely, in the state in which the flow path H is closed, the valve case biasing portion 70 degenerates the expansion and contraction rod 72 . For this reason, the biasing force from the expansion-contraction rod 72 to the movable valve frame part 60 reduces. Then, the movable valve frame part 60 is divided from the inner surface of the valve case 10 by the biasing force of the valve frame biasing part 90 . The sealed state of the movable valve frame part 60 and the valve case inner surface 10A is cancelled|released.

For this reason, as shown to FIGS. 12-15, the flow path H is opened (release operation|movement).

The valve closing operation and release operation in the movable valve part 40 are performed by a mechanical abutting operation by the valve case biasing part 70 and a mechanical separation operation by the valve frame biasing part 90 .

After the release operation, the rotation shaft driving unit 200 rotates the rotation shaft 20 in the direction indicated by the reference symbol R02. Then, the movable valve part 40 moves from a valve opening blocking position to a retraction position (retraction operation).

The valve opening operation which makes the movable valve part 40 into a valve-open state is performed by this release operation|movement and a retraction operation|movement.

In a series of operations (valve closing operation, releasing operation, retracting operation), the valve plate biasing part 80 makes the movable valve frame part 60 and the movable valve plate part 50 interlock|cooperate.

[Valve body retractable position (FREE) state]

12 to 14, the movable valve part 40 (the movable valve frame part 60, the movable valve plate part 50) in the valve opening blocking position is either valve case inner surface 10A, 10B of the valve case 10. ), which is not in contact with This state is called a state in which the valve body is FREE.

In a state in which the valve body is FREE, the expansion and contraction rod 72 of the valve case biasing portion 70 is in a retracted state. At this time, the expansion and contraction rod 72 does not protrude from the valve case inner surface 10B, but is buried in a position closer to the fixing part 71 than the valve case inner surface 10A. That is, the valve case biasing portion 70 is not in contact with the valve body 5 . In addition, the edge guide pin 91 did not protrude from the recessed part 30cm.

Fig. 16 is an enlarged cross-sectional view taken along a flow path showing the periphery of the gate valve in the present embodiment. It is an enlarged cross-sectional view along the flow path which shows the valve case biasing part of the gate valve in this embodiment, a valve frame biasing part, and a valve plate biasing part.

Next, the valve case biasing part 70 is driven from the state in which the valve body is FREE.

Then, the front-end|tip part 72a of the expansion-contraction rod 72 abuts against the lower surface 60sb of the movable valve frame part 60, as shown by arrow F1 in FIG. 16, FIG. At this time, the distal end portion 72a of the telescopic rod 72 abuts against the pressure receiving portion 93 .

For this reason, the movable valve frame part 60 moves toward 10 A of valve case inner surfaces. Moreover, the state in which the movable valve frame part 60 moves and the valve frame seal packing 61 contact|connects the valve case inner surface 10A is a valve closing position state (valve closed state). Moreover, the edge guide pin 91 protrudes from the recessed part 30cm.

At this time, the movable valve plate part 50 moves in the same direction as the movable valve frame part 60 by the valve plate biasing part 80 . At the same time, the movable valve plate part 50 and the movable valve frame part 60 maintain a sliding seal state through the sliding seal packing 52 .

In a state in which the valve body is free, the valve case biasing part 70 brings the movable valve frame part 60 into contact with the valve case inner surface 10A of the valve case 10 to close the flow path H (valve closing operation) .

[The valve body is in the variable closing position (static pressure or no differential pressure)]

16 and 17 show a state in which the flow path H is closed by the valve closing operation described above.

This state is called the valve closed state of no static pressure/differential pressure. The valve closed state without positive pressure/differential pressure is a state in which the valve body 5 is in contact with one inner surface of the valve case 10 and is not in contact with the other inner surface.

That is, in the closed state of the valve without positive pressure/differential pressure, the movable valve frame portion 60 of the valve body 5 is in contact with the valve case inner surface 10A around the first opening portion 12a. At the same time, the valve body 5 is not in contact with the valve case inner surface 10B positioned around the second opening 12b.

In the valve closed state without positive pressure/differential pressure, in the valve case biasing portion 70 , the expansion and contraction rod 72 is held in a state in which it is distracted in the direction toward the movable valve frame portion 60 . That is, the state in which the front end portion 72a is in contact with the lower surface 60sb of the movable valve frame portion 60 is maintained. Moreover, the valve frame seal packing 61 maintains the state in contact with the valve case inner surface 10A around the 1st opening part 12a of the valve case 10. In addition, the edge guide pin 91 maintains a state protruding from the recess (30 cm).

[Valve closed with the valve body in the reverse pressure position]

Fig. 18 is an enlarged cross-sectional view taken along a flow path showing the periphery of the gate valve in the present embodiment. 19 is an enlarged cross-sectional view along a flow path showing a valve case biasing part, a valve frame biasing part, and a valve plate biasing part of the gate valve in this embodiment.

18 and 19 show a state in which the flow path H is closed in a back pressure state.

This state is called the valve closing state of a back pressure. The reverse pressure valve closed state is a state in which the valve body 5 is in contact with both valve case inner surfaces 10A and 10B in the flow path H direction. That is, in the valve closed state of the reverse pressure, the movable valve frame portion 60 of the valve body 5 maintains a state in which the valve case inner surface 10A around the first opening portion 12a is in contact with the valve body 5 . The movable valve plate part 50 is also in contact with the valve case inner surface 10B located around the 2nd opening part 12b. Here, the back pressure means that a pressure is added to the valve body in the direction from the closed valve state to the valve open state.

When the valve body 5 receives back pressure with the expansion rod 72 extended, the movable valve plate part 50 is reciprocated with respect to the movable valve frame part 60 by the valve plate biasing part 80 . It moves while sliding to (B2) (FIG. 18, FIG. 19). Between the movable valve frame part 60 and the movable valve board part 50, the sealing state is maintained through the sliding seal packing 52. As shown in FIG.

For this reason, the movable valve plate part 50 collides with the valve case inner surface 10B around the 2nd opening part 12b. At this time, the counter cushion 51 relieves the impact caused by the collision in the movable valve plate part 50 . A mechanism for receiving the force received by the valve body 5 from the valve case inner surface 10B (the body on the back side) of the valve case 10 is a counterpressure canceling mechanism.

Also, from the valve closed state of the reverse pressure, the positive pressure/differential pressure is set to no. In this state, by the biasing force of the frame coil spring 92 of the valve frame biasing part 90, the movable valve frame part 60 is separated from the inner surface of the valve case 10, and the movable valve frame part 60 is retracted. This opens the flow path H (release operation).

In the gate valve 100 of this embodiment, when the neutral valve part 30, the movable valve board part 50, and the movable valve frame part 60 mutually slide, it becomes possible to perform mutual position regulation correctly, respectively. That is, it becomes possible to perform position regulation in the neutral valve part 30 and the movable valve frame part 60 accurately. At the same time, it becomes possible to precisely regulate the positions of the movable valve frame portion 60 and the movable valve plate portion 50 .

In particular, the sliding direction of the neutral valve part 30, the movable valve plate part 50, and the movable valve frame part 60 can be regulated so that all may not shift|deviate from reciprocating direction B1, B2.

Moreover, also when the neutral valve part 30, the movable valve board part 50, and the movable valve frame part 60 slide, the neutral valve part 30, the movable valve board part 50, and the movable valve frame part 60 ) and each other's postures do not change, and relatively parallel movements can be performed.

In addition, even when the valve body 5 pendulum operates, the posture of the neutral valve part 30, the movable valve plate part 50, and the movable valve frame part 60 does not change, and an integral positional relationship with each other is maintained. The pendulum operation can be performed while holding it.

In the gate valve 100 of this embodiment, when the expansion and contraction rod 72 presses the movable valve frame part 60, the position regulation of the movable valve frame part 60 with respect to the neutral valve part 30 is a frame guide pin ( 91) and the regulating tube 95.

Since the valve case biasing part 70, the valve plate biasing part 80, and the valve frame biasing part 90 are configured as described above, the movable valve frame part 60 is a flow path to the neutral valve part 30 ( In the movement in the direction H), with respect to the movement direction, the pressing force in the movement direction acts in the same position and direction.

Therefore, in the movement of the movable valve frame part 60 with respect to the neutral valve part 30 by the valve case biasing part 70, the posture of the movable valve frame part 60 with respect to the neutral valve part 30 can be very stable. there is.

At the same time, when the movable valve frame part 60 pressed by the expansion rod 72 moves in the flow path H direction with respect to the neutral valve part 30, the moving direction of this movable valve frame part 60 and the expansion and contraction rod 72 The direction of action of the pressing force of Moreover, with respect to the moving direction of the movable valve frame part 60, the pressing force from the expansion-contraction rod 72 acts on the movable valve frame part 60 at the position which becomes the same straight line.

For this reason, it can suppress that a moment will generate|occur|produce in the movable valve frame part 60. As shown in FIG. Accordingly, it is possible to suppress the occurrence of deformation in the movable valve frame portion 60 .

Thereby, it becomes possible to improve the sealability in the movable valve frame part 60, and to improve the operational reliability of the movable valve frame part 60. As shown in FIG.

In this embodiment, although the valve case biasing part 70, the valve plate biasing part 80, and the valve frame biasing part 90 were set as the structure provided in two sets, 4 each, it is good also as a structure other than it. Specifically, it is also possible to set it as the other number of installation groups according to the diameter of the gate valve 100, such as 3 sets of 6 each, or 4 sets of 8 each.

In addition, the valve case biasing part 70, the valve frame biasing part 90, and the valve plate biasing part 80 may be respectively arranged with different numbers. Also in this case, it is preferable that the valve case biasing part 70 and the valve frame biasing part 90 have the same number of pairs.

In this embodiment, the same effect as each above-mentioned embodiment can be resident.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 4th Embodiment of this invention is demonstrated based on drawing.

What is different from the first to third embodiments described above with respect to this embodiment is that the gate valve release control unit and the switching valve (spool valve) are related, and corresponding components other than the above are assigned the same reference numerals and A description is omitted.

20 : is a schematic sectional drawing along the flow path which shows the gate valve in this embodiment, and is a figure which shows the case where the valve main body is arrange|positioned at the valve opening blocking position.

It is a top view which shows the principal part of the gate valve in this embodiment, and is a figure which shows the positional relationship between a spool valve and the rotation shaft of a valve body.

22 : is a schematic explanatory drawing which shows the hydraulic drive part in the gate valve in this embodiment.

23 : is a flowchart which shows the normally closing operation|movement in the gate valve in this embodiment.

In the gate valve 100 of this embodiment, the brake operation release part 225f and the non-excitation operation brake 705b are connected to the release control part 101. As shown in FIG.

The release control unit 101 can output a release instruction signal to the brake operation release unit 225f and the non-excitation operation brake 705b based on the information in the flow path H. A sensor for acquiring information in the flow path H may be connected to the release control unit 101 .

A UPS device (UPS; Uninterruptible Power Supply) 102 is connected to the release control unit 101 . The release control unit 101 is operable by supplying power from the UPS device 102 even at the time of the previous stage.

In the gate valve 100 of this embodiment, the cancellation control part 101 confirms the situation in the flow path H, and outputs the cancellation instruction|indication signal.

Based on the release instruction signal output by the release control unit 101, the brake operation release unit 705f cancels the regulation of the non-excitation operation brake 705b. After that, based on the release instruction signal output by the release control unit 101 , the brake operation release unit 225f cancels the operation of the non-excitation operation brake 221 . Perform these operations in order.

At this time, the switching valve 800 (spool valve) can be made operable by the release of the operation restriction of the hydraulic motor 705m by the brake operation release part 705f.

The switching valve 800 is configured as a hydraulic damper that relieves an impact at the end of the closing operation of the valve body 5 .

The switching valve 800 is installed in the hydraulic pressure pipe 702 of the hydraulic drive unit 700 and can switch hydraulic pressure supply.

In the gate valve 100 of this embodiment, the kicker 25 which rotates in accordance with the rotation of the valve body 5 is provided integrally with the rotation shaft 20. As shown in FIG. The kicker 25 is disposed at an external position of the valve case 10 , that is, at a position used as an atmospheric atmosphere. The kicker 25 enables the switching valve 800 to switch the closing position detection operation, as will be described later. The kicker 25 may be regarded as a colliding object that performs a collision operation.

The switching valve 800 is provided in the hydraulic pressure pipe 702, detects that rotation of the rotary shaft 20 becomes the valve closing position and the valve opening closing position, and can switch hydraulic pressure supply.

23 : is a flowchart which shows the normally closing operation|movement in the gate valve in this embodiment.

Here, when the valve main body 5 in the gate valve 100 is located between the valve opening blocking position to a retracted position, let this state be a valve circulation state.

As operation|movement at the time of shearing in the gate valve 100 of this embodiment, first, in step S00 shown in FIG. 23, the case where it was a valve circulation state is considered.

In operation at the time of shearing in the gate valve 100 of this embodiment, a blackout generate|occur|produces in step S01 shown in FIG. In this step S01, the power supply from the power supply 227 to the rotation drive motor 220 is stopped. At the same time, in step S01, power supply from the power source 707 to the hydraulic motor 705m is stopped.

Then, in step S02 shown in FIG. 23, the non-excitation operation brake 221 and the non-excitation operation brake 705b act|operate.

For this reason, the operation|movement of the rotation drive motor 220 is regulated in step S03a shown in FIG. 23 by the operation|movement of the non-excitation operation brake 221.

At the same time, in step S03b shown in Fig. 23, the operation of the hydraulic motor 705m is regulated by the operation of the non-excitation brake 705b.

For this reason, let the state of the valve body 5 be maintained. That is, the valve body 5 is hold|maintained at several positions between a valve opening blocking position and a retracted position.

These steps S03a and S03b are emergency operations, and are performed simultaneously with step S02.

Next, in step S20 shown in FIG. 23, the situation in the flow path H is confirmed. Here, the status check in the flow path H means whether or not there is a problem with closing the flow path H (valve closing operation) with the gate valve 100 that has been stopped urgently.

Specifically, the presence or absence of an obstacle that obstructs the operation of the valve body 5 is checked in the rotational operation range for moving the valve body 5 from the retracted position to the valve opening blocking position by pendulum motion.

Alternatively, when the movable valve portion 54 is pressed against the inner surface of the valve case 10 to close the flow path H (valve closing operation), the movable valve portion 54 and the inner surface of the valve case 10 are In the meantime, the presence or absence of an obstacle to the operation of the movable valve unit 54 is checked.

Moreover, when the flow path H is closed, the presence or absence of the obstacle which generate|occur|produces in the both sides of the valve body 5, ie, upstream and downstream in the flow path H, is confirmed.

In the present embodiment, the status confirmation in the flow path H in this step S20 can be performed by the release control unit 101 by an output of a sensor provided inside the flow path H or the like.

According to the presence or absence of any obstacle to the valve closing operation in step S21, in the next step S21, the release control unit 101 determines whether or not the output of the release instruction signal is possible.

Next, in step S21 shown in FIG. 23, the cancellation control part 101 outputs the cancellation instruction signal.

Based on the release instruction signal output by the release control unit 101, the brake operation release unit 705f operates.

Then, in step S22 shown in FIG. 23, the brake operation release part 705f cancels the operation|movement of the non-excitation operation brake 705b.

For this reason, rotation of the hydraulic motor 705m becomes possible.

Then, in step S23 shown in FIG. 23, the hydraulic drive part 700 operates.

Specifically, in step S24 , the hydraulic pressure from the hydraulic pressure generating unit 701 toward the valve case biasing unit 70 is generated by the biasing force of the hydraulic pressure biasing member 720 of the hydraulic pressure generating unit 701 . For this reason, the operating hydraulic pressure reaches (inflows) to the switching valve 800 provided in the hydraulic pipe 702.

Then, in step S25 shown in FIG. 23, as mentioned later, the switching valve 800 will be in the state which shows an impact relief function. For this reason, it becomes a state which shows the function as a hydraulic damper which relieves the impact by the collision operation|movement of the kicker 25.

Next, in step S26 shown in FIG. 23, the cancellation control part 101 outputs the cancellation instruction|indication signal. Based on the release instruction signal output by the release control unit 101, the brake operation release unit 225f is actuated. Then, in step S27 shown in FIG. 23 , the brake operation release unit 225f cancels the operation of the non-excitation operation brake 221 .

Due to this, the rotation of the rotation driving motor 220 is possible.

At the same time, by the operation of the brake operation release unit 225f, in step S28 shown in FIG. 23, the shear biasing device 230 operates.

For this reason, the shear biasing device 230 releases the mainspring wound during normal energization.

Due to the biasing force of the spring, the front-end biasing device 230 rotates the rotating shaft 20 toward the valve closing position even during shearing.

In conjunction with the rotation of the rotating shaft 20 , the kicker 25 rotates integrally.

Then, in step S29 shown in FIG. 23 , the kicker 25 collides with the switching valve 800 . At this time, the shock relief is performed by the function as a hydraulic damper of the switching valve 800 .

Simultaneously, in step S30 shown in FIG. 23, the valve body 5 reaches the valve opening blocking position.

Then, the hydraulic pressure supply is replaced by the switching function of the switching valve 800 .

For this reason, hydraulic oil flows from the hydraulic pressure generating part 701 toward the valve case biasing part 70 by the biasing force of the hydraulic pressure biasing member 720 of the hydraulic pressure generating part 701. For this reason, the movable part 72 is extended in the direction opposite to the operation direction by the hydraulic motor 705m.

Then, in step S31 shown in FIG. 23, the movable valve part 54 is pressed against the inner surface of the valve case 10 by the movable part 72, and the flow path H is closed (valve closing operation).

As a result, the gate valve 100 of the present embodiment completes the springback operation in an emergency such as loss of power supply from the power sources 707 and 227 .

Here, step S21, step S25, step S26, and step S29 are performed in this order. For this reason, it becomes possible to show the shock alleviation function and the switching function as a hydraulic damper with respect to the switching valve 800. As shown in FIG.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 5th Embodiment of this invention is demonstrated based on drawing.

What is different from the fourth embodiment described above with respect to this embodiment is the point regarding the switching valve (spool valve), and the corresponding components other than that are assigned the same reference numerals and the description thereof is omitted.

24-29 is a schematic diagram which shows the operation|movement of the gate valve and spool valve in this embodiment.

Fig. 24 is a view showing the valve open state in which the rod of the spool valve is in the second position. Fig. 25 is a view showing the valve closed state in which the rod of the spool valve is in the third position. Fig. 26 is a view showing a collision standby state in which the rod of the spool valve is in the first position.

27 : is a figure which shows the dumping state which started moving so that the rod of a spool valve may approach a 2nd position rather than a 1st position. Fig. 28 is a view showing a dumping state in which the rod of the spool valve has moved so as to further approach the second position. Fig. 29 is a diagram showing a moment when the rod of the spool valve reaches the third position.

The switching valve 800 has a spool flow path 801 that enables the flow of hydraulic pressure between the hydraulic cylinder 710 (main cylinder) and the valve case biasing portion 70 .

The switching valve 800 is made so that opening/closing of the spool flow path 801 can be switched when the movable valve part 54 exists in a valve opening blocking position and a valve closing position.

The spool flow path 801 is connected to a main cylinder port 702a communicating with the hydraulic cylinder 710 and a pressure reducing cylinder port 702b communicating with the valve case biasing portion 70 .

The switching valve 800 has a rod (switching sensor) 802 .

One end of the rod 802 can be abutted against the kicker 25 . The kicker 25 rotates integrally with the valve body 5 according to the rotation of the rotating shaft 20 .

The rod 802 is made reciprocally movable in the axial direction.

A dumping chamber 803 is formed at a position adjacent to the other end of the rod 802 .

The dumping chamber 803 is connected to a main cylinder port 702a communicating with the hydraulic cylinder 710 .

The rod 802 has a biasing member 804 (spool spring) that applies a force in a direction from one end to the other.

The biasing member 804 is configured to release bias on the rod 802 according to a movement distance (axial position) of the rod 802 in a direction from one end to the other, as will be described later.

The rod 802 is movable in a direction in which the volume of the dumping chamber 803 is reduced by the kicker 25 which is abutted or collided.

The rod 802 is movable within a predetermined range in a direction in which the volume of the dumping chamber 803 is reduced by the biasing force of the biasing member 804 .

The rod 802 is movable in the direction in which the volume of the dumping chamber 803 increases by the hydraulic pressure supplied to the dumping chamber 803 from the main cylinder port 702a.

The switching valve 800 is provided with a dumping check valve 805 which enables the dumping chamber 803 and the main cylinder port 702a to communicate.

The dumping check valve 805 shuts off from the dumping chamber 803 toward the main cylinder port 702a and enables communication from the main cylinder port 702a toward the dumping chamber 803 .

The selector valve 800 is provided with a check valve 806 (spool check valve) in parallel with the spool flow passage 801 .

The check valve 806 shuts off from the main cylinder port 702a toward the pressure-reducing cylinder port 702b and enables communication from the pressure-reducing cylinder port 702b toward the main cylinder port 702a.

The dumping chamber 803 is provided with an orifice portion 807 capable of communicating with the main cylinder port 702a. The orifice portion 807 is provided in parallel with the dumping check valve 805 .

The orifice portion 807 has a variable communication state with the main cylinder port 702a, that is, a variable flow rate, depending on a movement distance (axial position) of the rod 802 from one end to the other end. there is.

In addition, the orifice part 807 may be provided at a plurality of locations in the axial direction of the rod 802 as positions exposed to the dumping chamber 803 in response to the movement of the rod 802 .

As will be described later, in the switching valve 800 , the spool flow path 801 can be opened in only a portion of the rod 802 according to a movement distance (axial position) in the direction from one end to the other end.

As will be described later, the orifice portion 807 of the selector valve 800 is the main cylinder port 702a according to the movement distance (axial position) of the rod 802 in the direction from one end to the other end, as will be described later. ) and can communicate with

Next, operation|movement of the switching valve 800 in this embodiment is demonstrated.

The selector valve 800 in this embodiment consists of a 3-position valve which has three positions. The three positions correspond to the expansion and contraction state of the rod 802 in the axial direction, respectively.

As shown in FIG. 26, the 1st position consists of a position where the rod 802 extends only the maximum distance which can move toward the end which is the end which the kicker 25 abuts or collides in the axial direction.

The 3rd position consists of a position in which only the maximum distance which the rod 802 can move toward the other end in the axial direction is degenerate, as shown in FIG.25, FIG.29.

Incidentally, in Figs. 25 and 29 , the degenerate rod 802 as the third position is not shown.

The 2nd position consists of a position between a 1st position and a 3rd position in the axial direction of the rod 802, as shown in FIG. The second position is such that the rod 802 is proximate to the third position in the axial direction.

Next, with respect to each position of these rods 802, the operation/action performed by the rod 802 with each configuration will be described.

The spool flow path 801 is opened only when the rod 802 is positioned at the third position, that is, the main cylinder port 702a and the pressure-reducing cylinder port 702b are in communication. The spool flow path 801 is closed when the rod 802 moves in a direction closer to the second position than the third position, that is, the main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. do it with

In addition, the spool flow path 801 is closed when the rod 802 is in several positions from the second position to the first position, that is, the main cylinder port 702a and the pressure-reducing cylinder port 702b are closed. put it in a blocked state.

The opening and closing of the spool flow path 801 can be switched when the rod 802 moves between the third position and the first position.

The dumping chamber 803 has a minimum volume when the rod 802 is positioned in the third position. The dumping chamber 803 has a maximum volume when the rod 802 is positioned in the first position. Further, the volume of the dumping chamber 803 changes proportionally or correspondingly according to a change in the distance at which the rod 802 is located between the third position and the first position.

The biasing force of the biasing member 804 is maximized when the rod 802 is positioned at the first position. The biasing member 804 applies a force between the first position and the second position of the rod 802 in a direction in which the rod 802 is degenerate.

The biasing member 804 is set so that the biasing force is not applied to the rod 802 when the rod 802 is positioned in the second position. The biasing member 804 is set so that the rod 802 is positioned between the second position and the third position so that no biasing force is applied to the rod 802 .

The dumping check valve 805 resides in a rectifying action, regardless of the angular position of the rod 802 .

The check valve 806 resides in a rectifying action, regardless of the respective position of the rod 802 .

The orifice part 807 relieves the hydraulic pressure flowing out from the dumping chamber 803 when the rod 802 is positioned between the first position and the second position. In particular, the orifice portion 807 is set so that when the rod 802 moves from the first position to the second position, the degree of relaxation of the hydraulic pressure flowing out from the dumping chamber 803 is increased.

Further, in the orifice portion 807 , when the rod 802 is positioned between the second position and the third position, hydraulic pressure flowing out from the dumping chamber 803 through the orifice portion 807 is blocked.

The kicker 25 may abut or collide with an end of the rod 802 when the rod 802 is positioned between the first position and the second position.

The kicker 25 may press down on the end of the rod 802 as the rod 802 moves from the first position to the second position.

The kicker 25 may press down on the end of the rod 802 as the rod 802 moves from the second position to the third position. The movement of the rod 802 from the second position to the third position is by pressing the kicker 25 .

The kicker 25 may contact an end of the rod 802 as the rod 802 moves from the third position to the second position. Movement of the rod 802 from the third position to the second position is initiated by releasing the depression from the kicker 25 .

In addition, since the kicker 25 rotates integrally with the rotating shaft 20, the valve body 5, and the valve frame part 63, the illustration is abbreviate|omitted in FIGS.

In the gate valve 100 of the present embodiment, the hydraulic motor 705m of the driving unit 705 of the cylinder driving unit 730 is energized (powered), and the normal valve opening/closing operation is controllable, and the cylinder driving unit due to power failure or the like. In a state in which power is not supplied to the hydraulic motor 705m of the driving unit 705 of the 730, a different operation is performed.

In addition, the spool flow path 801 of the switching valve 800 is made so that the spool flow path 801 can be opened only when the movable valve part 54 is in a valve opening blocking position and a valve closing position in any power supply state and a non-power supply state.

First, in a normal power supply state, the selector valve 800 operates between the second position and the third position.

Specifically, the hydraulic motor 705m of the drive unit 705 is energized, and, on the other hand, as for the switching valve 800 in the valve open state, the rod 802 is located at the second position.

That is, in the retracted position of the movable valve part 54, the flow path H is expanded and made to flow.

In this state, as shown in FIG. 24, the rod 802 is located in the 2nd position.

Moreover, the flow path H is partially covered by the movable valve part 54 while the movable valve part 54 closes rotation operation|movement from a retracted position to a valve opening blocking position. In this case, the first opening 12a and the second opening 12b communicate with each other through a part of the flow path H.

In this state, the rod 802 is in the second position.

In addition, immediately after the movable valve part 54 reaches the valve opening blocking position, although the flow path H is blocked by the movable valve part 54, it is not sealed. In this case, the 1st opening part 12a and the 2nd opening part 12b communicate through the space in the vicinity of the periphery of the movable valve part 54. As shown in FIG.

In this state, the rod 802 is immediately moved from the second position to the third position.

Further, by driving the valve case biasing portion 70, the movable valve portion 54 performs a sealing operation to change the position in the flow path H direction, and the movable valve portion 54 moves from the valve opening blocking position, The valve slides to the closed position, and the flow path (H) is blocked.

In this state, as shown in FIG. 25, the rod 802 is located in the 3rd position.

Next, the opening operation|movement which the movable valve part 54 changes the position in the flow path H direction, and the movable valve part 54 slides from a valve closing position to a valve opening blocking position. At this time, the flow path H is partially covered by the movable valve part 54, and the 1st opening part 12a and the 2nd opening part 12b communicate through a part of the flow path H.

In this state, the rod 802 is in the third position.

In addition, immediately after the movable valve part 54 starts the closing operation|movement from the valve opening blocking position, sealing of the flow path H is cancelled|released, and through the space of the vicinity of the periphery of the movable valve part 54, the 1st The opening 12a and the second opening 12b communicate with each other. At the same time, although the flow path H is blocked by the movable valve part 54, it will be in the state which is not sealed.

In this state, the rod 802 moves from the third position to the second position.

In addition, the flow path H is partially covered by the movable valve part 54 while the movable valve part 54 rotates openly from a valve opening blocking position to a retracted position. In this case, the first opening 12a and the second opening 12b communicate with each other through a part of the flow path H.

In this state, as shown in FIG. 24, the rod 802 is located in the 2nd position.

Next, in the non-powered state, such as when an emergency such as a power outage occurs, the selector valve 800 moves from the second position to the first position, from the first position to the third position, and further from the second position to the third position. It operates between positions.

In the gate valve 100 in this embodiment, it is a structure in which a normally closed operation|movement is possible.

Therefore, when the gate valve 100 is in the closed state and the hydraulic motor 705m of the drive unit 705 is energized, a power failure or the like occurs and the power supply is turned off, the switching valve 800 In , as shown in FIG. 25 , the rod 802 is located at the third position. At this time, the rod 802 does not move from the 3rd position.

On the other hand, when the gate valve 100 is in an open state and the hydraulic motor 705m of the drive unit 705 is energized, when a power failure or the like occurs and becomes a non-powered state, from the viewpoint of safety , the switching valve 800 operates to enable a normally closed operation.

Specifically, first, the hydraulic motor 705m of the drive unit 705 is energized, and on the other hand, as for the switching valve 800 in the valve open state, the rod 802 is located in the second position.

That is, in the state where the movable valve part 54 is a retracted position, and the flow path H is expanded and can distribute|circulate, the rod 802 is located in a 2nd position.

Next, for example, when a power outage occurs and the power supply to the hydraulic motor 705m of the drive unit 705 is lost, at that moment, in the valve open state and the selector valve 800 , the rod 802 is It maintains the state located in the second position.

That is, in the state in which the movable valve part 54 is a retracted position, and the flow path H develops and can distribute|circulate, as shown in FIG. 24, the rod 802 is located in a 2nd position.

Then, immediately after a power outage occurs and power supply to the hydraulic motor 705m of the drive unit 705 is lost, the movable valve unit 54 performs a closed rotation operation from the retracted position in the open valve state to the valve opening blocking position. . At that time, when the kicker 25 linked to the valve body 5 collides at the end of the closing operation, the rod 802 of the selector valve 800 is removed in order to enable a shock mitigation function as a hydraulic damper. Extend from 2nd position to 1st position.

That is, as shown in FIG. 26 , before the movable valve unit 54 closes from the retracted position, the rod 802 extends to the first position and enters a waiting state waiting for the kicker 25 to collide.

In the selector valve 800, when the rod 802 is in the first position, the shock relief state starts.

At the time of shock relief, the movable valve part 54, which operates to close from the retracted position to the valve opening blocking position, matches one end of the rod 802 at which the kicker 25 is located in the first position at the end of the closed rotation operation. and moves from the first position to the second position.

That is, as shown in FIG. 27, FIG. 28, while the movable valve part 54 closes rotation operation from a retracted position, the rod 802 moves from a 1st position to a 2nd position. Previously, the orifice portion 807 can communicate with the main cylinder port 702a from the dumping chamber 803, and on the other hand, the flow rate is variable.

Incidentally, the flow rate in the orifice portion 807 from the dumping chamber 803 to the main cylinder port 702a is set to decrease as the rod 802 moves from the first position to the second position.

In the switching valve 800 , when the rod 802 that has moved from the first position reaches the second position, the shock relief state ends.

At the end of the shock relief, at the end of the closing rotation operation of the movable valve unit 54 , the kicker 25 presses one end of the rod 802 that has reached the second position, and the rod 802 moves from the second position to the third position. move to position

That is, as shown in FIG. 29, at the moment when the movable valve part 54 reached|attained the valve opening blocking position, the rod 802 will reach|attain a 3rd position at the same time.

When the rod 802 reaches the third position, at the same time, the blocked spool flow path 801 is opened.

Accordingly, after the movable valve portion 54 reaches the valve opening blocking position, the spool flow passage 801 is opened. When the spool flow path 801 is opened, the main cylinder port 702a and the pressure-reducing cylinder port 702b communicate.

For this reason, the valve case biasing part 70 and the hydraulic cylinder 710 communicate with each other. Then, hydraulic pressure is supplied from the hydraulic cylinder 710 to the valve case sub-part 70 . For this reason, the valve case biasing part 70 operates, the movable valve part 54 moves from a valve opening blocking position to a valve closing position, and a valve closing operation is complete|finished.

Next, the operation including the shock alleviation action of the switching valve 800 in the present embodiment will be described.

First, the valve open state in which the hydraulic motor 705m of the drive part 705 is energized as a starting state is demonstrated.

In this state, as shown in FIG. 24, the movable valve part 54 exists in a retracted position.

As for the switching valve 800, the rod 802 is located in the 2nd position. The spool flow path 801 is clogged. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked.

The biasing member 804 is not applying a force to the rod 802 .

The volume of the dumping chamber 803 is reduced, and the dumping chamber 803 does not communicate with the orifice portion 807 .

As for the valve case biasing part 70 , the distal end of the movable part 72 is retracted by the biasing member 73 .

As for the hydraulic cylinder 710, the hydraulic motor 705m of the drive part 705 resists the biasing force of the hydraulic biasing member 720 (main spring), and the cylinder volume is increasing.

Communication is made possible from the valve case biasing part 70 to the hydraulic cylinder 710 by a check valve 806 .

Therefore, in the valve case biasing portion 70 urged by the biasing member 73 , a differential pressure higher than that of the hydraulic cylinder 710 and prescribed by the check valve 806 is generated.

The inside of the dumping chamber 803 is brought into a state of dynamic pressure with the hydraulic cylinder 710 by the dumping check valve 805 .

Next, for example, a case in which a power outage occurs and power supply to the hydraulic motor 705m of the drive unit 705 is lost will be described.

In this state, initially, the movable valve part 54 exists in the retracted position in step S00 shown in FIG.

After a power failure occurs in step S01 shown in FIG. 23 , in steps S02 to S21 shown in FIG. 23 , the operation of the rotary drive motor 220 is regulated and the operation of the hydraulic motor 705m is released.

Next, in step S23 shown in FIG. 23 , in the hydraulic cylinder 710 , the cylinder volume starts to be reduced by the biasing force of the hydraulic biasing member 720 . For this reason, in step S24 shown in FIG. 23, the pressure of the hydraulic cylinder 710 is raised by the biasing force of the hydraulic biasing member 720. As shown in FIG.

Since the inside of the dumping chamber 803 is in dynamic pressure with the hydraulic cylinder 710 by the dumping check valve 805, the pressure in the dumping chamber 803 rises.

When the pressure in the dumping chamber 803 rises, the rod 802 is pressed and moved, resists the biasing force of the biasing member 804, and the volume of the dumping chamber 803 expands. Thereby, the rod 802 extends from the 2nd position shown in FIG. 24 to the 1st position shown in FIG.

As for the switching valve 800, the rod 802 is located in the 1st position.

For this reason, in step S25 shown in FIG. 23, the rod 802 extended to the 1st position is in a waiting state waiting for the collision of the kicker 25. As shown in FIG.

The spool flow path 801 maintains a closed state. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked.

The biasing member 804 applies a force to the rod 802 .

The volume of the dumping chamber 803 is enlarged, and the dumping chamber 803 communicates with the orifice part 807 .

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In this state, in step S26 to step S28 shown in FIG. 23 , the operation of the rotation drive motor 220 is released and the rotation shaft 20 is rotated by the front-end biasing device 230 .

For this reason, the movable valve part 54 starts a closing rotation operation|movement toward a valve opening blocking position from a retracted position.

In this state, the rotational operation of the rotating shaft 20 is not controlled by the rotating shaft driving unit 200 . For this reason, the closing rotation operation|movement from the retracted position of the movable valve part 54 toward the valve opening blocking position is performed extremely rapidly.

In step S29 shown in FIG. 23 , by this closing operation, the kicker 25 abuts or collides with the end of the rod 802 positioned at the first position as shown in FIG. 27 . Continuing, the kicker 25 moves the rod 802 from the first position to the second position by pressing the end of the rod 802 .

In this state, by the operation of the rod 802 colliding with the kicker 25, the volume of the dumping chamber 803 is about to be momentarily reduced. At this time, the dumping chamber 803 instantaneously becomes high pressure. Here, the rising pressure of the dumping chamber 803 is relieved by the orifice portion 807 communicating with the dumping chamber 803 .

At this time, the high pressure is released from the dumping chamber 803 to the hydraulic cylinder 710 through the orifice portion 807 .

In the hydraulic cylinder 710 , pressure fluctuations are absorbed by the deformation of the hydraulic biasing member 720 .

The rising pressure of the dumping chamber 803, which has become a high pressure momentarily, is blocked by the dumping check valve 805 toward the main cylinder port 702a. For this reason, transmission of the high-pressure impact to the main cylinder port 702a and the part which communicates with the main cylinder port 702a is prevented.

The spool flow path 801 maintains a closed state. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. The biasing member 804 applies a force to the rod 802 .

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In addition, by the closing operation, rotation operation is continued from the retracted position of the movable valve part 54 toward the valve opening blocking position, and the movable valve part 54 approaches the valve opening blocking position.

In this state, the kicker 25 moves the rod 802 toward the second position by pressing it in a state in contact with the end of the rod 802 , and as shown in FIG. 28 , the rod 802 moves to the second position. close to position

Here, by the operation of the rod 802 pressed by the kicker 25, the volume of the dumping chamber 803 is continuously reduced. At this time, the dumping chamber 803 maintains a high-pressure state as it gradually lowers. Here, the pressure in the dumping chamber 803 is continuously relieved by the orifice portion 807 communicating with the dumping chamber 803 .

At this time, the high pressure is released from the dumping chamber 803 to the hydraulic cylinder 710 through the orifice portion 807 .

In the hydraulic cylinder 710 , pressure fluctuations are absorbed by the deformation of the hydraulic biasing member 720 .

The pressure in the dumping chamber 803 that has become high pressure is shut off toward the main cylinder port 702a by the dumping check valve 805 . For this reason, transmission of high pressure to the main cylinder port 702a and the part communicating with the main cylinder port 702a is prevented.

The spool flow path 801 maintains a closed state. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. The biasing member 804 applies a force to the rod 802 .

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In addition, by the closed rotation operation, the kicker 25 is pressed firmly in a state in contact with the end of the rod 802, so that the rod 802 reaches the second position.

In this state, the orifice portion 807 is blocked by the movement of the rod 802 , and the dumping chamber 803 is blocked from the hydraulic cylinder 710 .

For this reason, pressure relief is complete|finished. At this time, pressure fluctuations are absorbed by the deformation of the hydraulic biasing member 720 in the hydraulic cylinder 710 , and the pressure in the dumping chamber 803 is sufficiently lowered.

The spool flow path 801 maintains a closed state. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. The biasing member 804 cancels the state to which the force of the rod 802 is applied.

From the hydraulic cylinder 710 toward the valve case biasing portion 70 , it is blocked by the check valve 806 .

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

Moreover, by the closing operation|movement, as shown in FIG. 29, the movable valve part 54 arrives at the valve opening blocking position.

In this state, the kicker 25 is pressed firmly against the end of the rod 802 so that the rod 802 passes through the second position to reach the third position.

Here, the rod 802 reaches the third position at the same time as the moment when the movable valve portion 54 reaches the valve opening blocking position.

When the rod 802 reaches the third position, the spool flow path 801 first enters the communication state by the movement of the rod 802 .

The main cylinder port 702a and the pressure-reducing cylinder port 702b communicate with each other.

The biasing member 804 is not applying a force to the rod 802 .

From the hydraulic cylinder 710 toward the valve case biasing portion 70 , it is blocked by the check valve 806 , but communicates with the spool flow passage 801 .

For this reason, the pressure of the valve case biasing part 70 rises.

Accordingly, the valve case biasing part 70 generates a driving force greater than the biasing force of the biasing member 73 , and the distal end of the movable part 72 is extended.

At this time, it is pressed against the distal end of the movable part 72, and the movable valve part 54 performs a sealing operation in which the position in the flow path H direction is changed. For this reason, in step S31 shown in FIG. 23, the movable valve part 54 slides from a valve opening blocking position to a valve closing position, and the flow path H is clogged.

For this reason, the valve closing operation as the normal closing operation in an emergency such as a power failure is completed.

In the present embodiment, the gate valve 100 includes the release control unit 101 , the brake operation release unit 705f , the brake operation release unit 225f , the non-excitation operation brake 705b , the non-excitation operation brake 221 , By having the switching valve 800, it becomes possible to realize a normally closed operation that simultaneously exhibits incompressible fluid supply switching and shock relief.

The rod 802 is made movable between the second position and the third position by the state of being pressed by the rod 802 of the kicker 25 .

For this reason, the spool flow path 801 communicates with the spool flow path 801 unless the rod 802 pressed by the kicker 25 is in the third position in either a non-powered state such as a power failure or a normal power supply controllable state. doesn't happen

That is, when the valve body 5 is in a position other than the valve opening blocking position and the valve closing position, the rod 802 is located between the first position and the second position. At this time, the spool flow path 801 is blocked, and the movable valve unit 54 does not close.

Accordingly, the hydraulic pressure is not supplied from the hydraulic cylinder 710 to the valve case biasing portion 70 unless the rod 802 pressed by the kicker 25 is in the third position.

That is, unless the rod 802 pressed by the kicker 25 is in the third position, the valve case biasing unit 70 does not perform a closing operation with respect to the movable valve unit 54 .

Due to this, the valve case biasing portion 70 does not apply a force to the movable valve portion 54 when the valve body 5 is in other than the valve opening blocking position and the valve closing position.

Even when the gate valve 100 is in a normal power supply or no power supply state, only when the valve body 5 is in the valve opening blocking position and the valve closing position, the switching valve 800 applies hydraulic pressure to the valve case bias 70 . supply can be made available.

For this reason, it is possible to maintain the interlock function for regulating the normally closing operation of the springback with respect to the movable valve part 54 in both a non-power supply state such as a power failure, and a normal power supply controllable state.

For this reason, it can prevent that the gate valve 100 does not become a valve closing state by an inappropriate closing operation|movement. In addition, it is possible to prevent the gate valve 100 from being damaged or inconvenient due to an improper closing operation.

In addition, in the switching valve 800 of the gate valve 100 in this embodiment, when the rod 802 is located between a 1st position and a 2nd position, the dumping formed in the other end of the rod 802 . The impact can be alleviated by the seal 803 .

For this reason, the 3 positions in the switching valve 800 are implement|achieved, and it is set as the waiting state corresponding to the collision of the valve body 5 as the 1st position of the rod 802 .

Moreover, the dumping function is shown as between the 1st position of the rod 802 and the 2nd position, and the impact by the collision with the rod 802 of the kicker 25 is relieve|moderated.

Further, in the present embodiment, when the valve body 5 is in the valve opening blocking position, the spool flow passage 801 is communicated as the third position of the rod 802, and the valve case biasing portion ( 70) to enable the supply of hydraulic pressure. For this reason, the valve case biasing part 70 is driven, and the movable valve part 54 is moved to a valve closing position.

In the switching valve 800 , it becomes possible to switch this function by the position of the rod 802 .

In addition, the dumping check valve 805 makes it possible to supply the hydraulic pressure stored in the hydraulic cylinder 710 to the dumping chamber 803 when there is no power supply such as a power outage. At the same time, even if the kicker 25 collides with the rod 802 after the rod 802 is extended to the first position, which is in a waiting state for the collision of the valve body 5, it is transferred from the dumping chamber 803 to the main cylinder port ( 702a) is blocked.

For this reason, the high-pressure state generated in the dumping chamber 803 by the collision of the kicker 25 is not transmitted to the main cylinder port 702a. For this reason, it becomes possible to exhibit a dumping function without the gate valve 100 being damaged by the high pressure generated in the dumping chamber 803 expanded to the 1st position.

When the kicker 25 collides with the rod 802 after the rod 802 is extended to the first position in a waiting state by the orifice portion 807, the hydraulic pressure stored in the dumping chamber 803 is transferred to the orifice portion. Through 807, it moves to the hydraulic cylinder 710 in a state in which the flow rate is suppressed. For this reason, the degeneracy of the rod 802 due to the collision of the kicker 25 is performed in a relaxed state.

Accordingly, the high-pressure state generated by the collision between the kicker 25 and the rod 802 is gently lowered. For this reason, the impact generated by the collision between the kicker 25 and the rod 802 is absorbed.

At this time, the spool flow path 801 is clogged. Further, the dumping check valve 805 from the dumping chamber 803 to the hydraulic cylinder 710 is directed in the closing direction. Accordingly, the high-pressure state generated by the collision between the kicker 25 and the rod 802 is not directly transmitted to the hydraulic cylinder 710 and the valve case bias portion 70 .

Further, when the rod 802 is retracted to the second position, the orifice portion 807 is blocked by the rod 802 . For this reason, the dumping chamber 803 does not maintain a dumping function, ie, a shock alleviation function. Thus, the dumping function is exhibited during the movement of the rod 802 from the first position to the second position.

When the valve case biasing portion 70 is in a high pressure state compared to the hydraulic cylinder 710 , communication is possible from the valve case biasing portion 70 toward the hydraulic cylinder 710 by the check valve 806 .

This is because, regardless of the open/close state of the spool flow path 801 , the check valve 806 becomes a parallel flow path, so that the valve case biasing portion 70 and the hydraulic cylinder 710 can communicate.

At the same time, when the hydraulic cylinder 710 is in a high pressure state compared to the valve case biasing part 70 , the check valve 806 is blocked from the valve case biasing part 70 toward the hydraulic cylinder 710 . That is, the check valve 806 can communicate depending on the open/close state of the spool flow passage 801 .

For this reason, depending on the opening/closing state of the spool flow path 801 set by the position of the rod 802, the pressure state of the valve case biasing part 70 can be controlled. That is, only when the spool flow path 801 is opened, a negative pressure (incompressible fluid) is supplied to the valve case biasing part 70, and the valve case biasing part 70 performs a closing operation.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve and spool valve which concern on 6th Embodiment of this invention are demonstrated based on drawing.

30 to 35 are cross-sectional views showing a switching valve (spool valve) in the present embodiment.

In this embodiment, what is different from the 5th embodiment mentioned above is the point regarding the specific structure of a spool valve, the same code|symbol is attached|subjected to other corresponding structures, and the description is abbreviate|omitted.

Fig. 30 is a diagram corresponding to Fig. 24 and showing the valve open state in which the rod of the spool valve is in the second position. Fig. 31 is a view corresponding to Fig. 25 and showing the valve closed state in which the rod of the spool valve is in the third position. Fig. 32 is a diagram corresponding to Fig. 26 and showing a collision standby state in which the rod of the spool valve is in the first position.

FIG. 33 : corresponds to FIG. 27, and is a figure which shows the dumping state in which the rod of a spool valve started moving toward a 2nd position rather than a 1st position. Fig. 34 is a diagram corresponding to Fig. 28 and showing a dumping state in which the rod of the spool valve has moved closer to the second position. FIG. 35 : is a figure which corresponds to FIG. 29 and shows the moment when the rod of a spool valve reached a 3rd position.

As shown in FIGS. 30-35, the selector valve 800 in this embodiment includes a rod 802, an inner spool 811, an outer spool 812, a casing 810, and a C ring. 814 (stopper) and a biasing member 804 .

The rod 802 is in the shape of a rod that can be stretched and contracted in the axial direction.

The inner spool 811 has a cylindrical shape capable of reciprocating along the rod 802 .

The outer spool 812 has a cylindrical shape capable of reciprocating along the rod 802 .

The casing 810 accommodates the rod 802 , the inner spool 811 , and the outer spool 812 .

The C ring 814 is cast around the rod 802 so as to be in contact with the inner spool 811 and the outer spool 812 .

The biasing member 804 applies a force to the inner spool 811 in the axial direction of the rod 802 .

The rod 802 has a circular rod shape in cross section and is disposed at the center of the casing 810 .

The casing 810 has a substantially cylindrical cylindrical portion 810a. Both ends of the cylindrical portion 810a in the axial direction are closed by the lid portions 810b and 810c.

The rod 802 is disposed coaxially with the cylindrical portion 810a.

In the casing 810 , a through hole 816 is provided at a central position of the lid portion 810b positioned at one end of the cylindrical portion 810a . The tip 802a of one end of the rod 802 passes through the through hole 816 . The tip 802a of the rod 802 can protrude from the through hole 816 to the outside of the casing 810 .

As for the lid part 810b used as the outer surface of the casing 810, the periphery of the through-hole 816 becomes the plane 810b1 which substantially orthogonally crosses the axis line of the cylindrical part 810a. One end of the cylindrical portion 810a is also formed on the same plane as the plane 810b1.

The plane 810b1 serves as an end position regulating part for regulating the end position of the closing operation in the closing operation of the rotary shaft 20 when the kicker 25 abuts.

Seal members 816a and 816b are provided in the through hole 816 , and one end of the rod 802 is slidable. In addition, a stopper 816c is provided at a position from the through hole 816 to the inside of the casing 810 to restrict the rod 802 from falling out from the through hole 816 .

At a position opposite to the lid portion 810c of the stopper 816c, one end of the biasing member 804 is in contact.

The biasing member 804 is disposed so as to surround the outer periphery of the rod 802 at a position close to the lid portion 810c, and to surround it in a spiral shape.

The other end of the rod 802 is located at one end in the dumping chamber 803 . A flange portion 802b is cast on the other portion of the rod 802 . The flange portion 802b is provided in the radially outward direction of the rod 802 . The radially outer surface of the flange portion 802b is slidably in contact with the inner peripheral surface of the cylindrical portion 810a on the entire circumference.

The lid portion 810c at the other end of the cylindrical portion 810a blocks the other end of the casing 810 .

The inner peripheral surface of the cylindrical portion 810a and the end surface 802b1 of the lid portion 810c and the flange portion 802b of the rod 802 form a sealed dumping chamber 803 .

At the center of the lid part 810c, the rod 802 and the guide rod 810d (axial direction regulating part) coaxial with the cylindrical part 810a protrude into the inside of the cylindrical part 810a.

The guide rod 810d is inserted into the regulating hole 802d provided at the other end of the rod 802 . The guide rod 810d and the regulating hole 802d of the rod 802 are slidable to each other.

A seal member 810e is provided between the guide rod 810d and the regulating hole 802d of the rod 802 . A sealing member 810f is provided between the radially outer side of the flange portion 802b of the rod 802 and the inner surface of the cylindrical portion 810a.

In the center of the guide rod 810d, a through hole 810d1 is formed in the axial direction.

The through hole 810d1 communicates with the outside through the rod internal space 803c located inside the regulating hole 802d of the rod 802 . The rod internal space 803c of the regulating hole 802d of the rod 802 is maintained in the same atmospheric pressure atmosphere as the outside by the through-hole 810d1.

The diameter dimension ?810 of the guide rod 810d and the diameter dimension ?802a at the tip 802a of the rod are in a relationship satisfying the following conditions.

In order to realize the second position state, a force is applied to the rod 802 in the right direction in a range weaker than the biasing force of the biasing member 804 . This force is borne by the hydraulic force due to the area difference defined by the diameter dimension ?802a of the tip 802a of the rod and the diameter dimension ?810 of the guide rod 810d.

In order to realize the first position state, when the pressure from the hydraulic cylinder 710 is introduced, the force is applied to the rod 802 in the direction toward the tip 802a with a force stronger than the biasing force of the biasing member 804. apply This force is borne by the hydraulic force due to the area difference defined by the diameter dimension ?802a of the tip 802a of the rod and the diameter dimension ?810 of the guide rod 810d.

In addition, the force acting on each surface of each part located inside the casing 810 which is a pressure vessel is set as follows.

That is, the force of the area difference defined by the diameter dimension φ802a of the tip 802a of the rod, which is the area exposed to the outside of the casing 810 and the diameter dimension φ810 of the guide rod 810d (area difference×inside) pressure) is set to act on the movable assembly inside of the casing 810 .

A C ring 814 is cast around the outer periphery of the rod 802 . The C ring 814 is fixed to the outer periphery of the rod 802 . The C ring 814 is formed integrally with the rod 802 and does not move with respect to the rod 802 .

An inner spool 811 coaxially disposed on the outer periphery of the rod 802 .

The inner spool 811 includes a substantially cylindrical cylindrical portion 811a, a flange portion 811b protruding radially inward from an end portion adjacent to the lid portion 810c of the cylindrical portion 811a, and a cylindrical portion ( It has a flange portion 811c protruding radially outward from an end portion adjacent to the lid portion 810b of the 811a.

The cylindrical portion 811a is disposed coaxially with the rod 802 . The inner peripheral surface of the cylindrical portion 811a is spaced apart from the outer peripheral surface of the rod 802 .

The diameter dimension of the inner peripheral surface of the cylindrical part 811a is set larger than the diameter dimension of the outer peripheral surface of the rod 802 .

A biasing member 804 is disposed between the inner peripheral surface of the cylindrical portion 811a and the outer peripheral surface of the rod 802 .

The cylindrical portion 811a is disposed at an outer peripheral position of the spiral biasing member 804 .

The inner peripheral surface of the flange portion 811b is in contact with the outer peripheral surface of the rod 802 . The inner peripheral surface of the flange portion 811b is made to be slidable in the axial direction with respect to the rod 802 .

The other end of the biasing member 804 is in contact with the surface 811b2 of the flange portion 811b opposite to the lid portion 810b.

The flange part 811b is made possible to apply a force by the biasing member 804 in the direction toward the lid part 810c from the lid part 810b.

The end face 811b1 of the flange part 811b which opposes the lid part 810c is made so that contact with the position opposing the lid part 810b of the C-ring 814 cast by the rod 802 is possible.

The outer peripheral surface of the flange portion 811c is slidably in contact with the inner peripheral surface of the cylindrical portion 810a of the casing 810 on the entire circumference.

In the cylindrical portion 810a of the casing 810 , the stepped surface 810a2 is formed so that the diameter of the position close to the lid portion 810c is smaller than the position close to the lid portion 810b.

The surface 811c1 of the flange portion 811c opposite to the lid portion 810c is allowed to contact the stepped surface 810a2.

At a position closer to the lid portion 810b than the flange portion 811c, a lid portion 810b and a casing space 803b surrounded by the cylindrical portion 810a of the casing 810 are formed.

A biasing member 804 is disposed inside the casing space 803b.

The casing space 803b communicates with the main cylinder port 702a.

An outer spool 812 coaxially disposed on the outer periphery of the rod 802 .

The outer spool 812 has a substantially cylindrical cylindrical portion 812a and a flange portion 812b protruding radially inward from an end portion adjacent to the lid portion 810c of the cylindrical portion 811a.

The cylindrical portion 812a is disposed coaxially with the rod 802 . The inner peripheral surface of the cylindrical portion 812a is in contact with the outer peripheral surface of the cylindrical portion 811a of the inner spool 811 .

The inner peripheral surface of the cylindrical portion 812a is made slidable with the outer peripheral surface of the cylindrical portion 811a of the inner spool 811 .

The inner peripheral surface of the flange portion 812b is in contact with the outer peripheral surface of the rod 802 . The inner peripheral surface of the flange portion 812b is made to be slidable in the axial direction with respect to the rod 802 .

A surface 812b2 of the flange portion 812b that opposes the lid portion 810b is formed so as to be in contact with a position opposed to the lid portion 810c of the C-ring 814 cast on the rod 802 .

A surface 812b1 of the flange portion 812b opposite to the lid portion 810c is made to be in contact with an end surface 802b1 of the flange portion 802b of the rod 802 .

The end face 812a2 of the cylindrical part 812a of the outer spool 812 that faces the lid part 810b, and the flange part 811c of the inner spool 811 that faces the lid part 810c A space surrounded by 811c1 and the outer peripheral surface of the cylindrical portion 811a of the inner spool 811 and the inner peripheral surface of the cylindrical portion 810a of the casing 810 forms a spool flow passage 801 .

Alternatively, the end face 812a2 of the cylindrical portion 812a of the outer spool 812 opposite to the lid portion 810b and the flange portion 811c of the inner spool 811 opposite to the lid portion 810c are opposite to each other. A space surrounded by the surface 811c1, the outer peripheral surface of the cylindrical portion 811a of the inner spool 811, and the inner peripheral surface and the stepped surface 810a2 of the cylindrical portion 810a of the casing 810, the spool flow passage 801 is is forming

A main cylinder port opening 801a communicating with the main cylinder port 702a is formed in the cylindrical portion 810a of the casing 810 in the radial direction at a position capable of communicating with the spool flow path 801 .

The main cylinder port opening 801a can be blocked by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

In the cylindrical portion 810a of the casing 810, a pressure-reducing cylinder port opening 801b communicating with the pressure-reducing cylinder port 702b is formed at a position capable of communicating with the spool flow passage 801 in the radial direction.

The pressure-reducing cylinder port opening 801b can be blocked by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

The main cylinder port opening 801a is located closer to the lid part 810b in the axial direction position of the rod 802 than the pressure-reducing cylinder port opening 801b.

That is, the pressure-reducing cylinder port opening 801b is located closer to the lid portion 810c in the axial direction of the rod 802 than the main cylinder port opening 801a.

Accordingly, corresponding to the axial position of the rod 802 , a state in which only the pressure-reducing cylinder port opening 801b is blocked by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 is possible.

In addition, corresponding to the axial position of the rod 802, the main cylinder port opening 801a and the pressure-reducing cylinder port opening 801b are blocked by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 It is possible Do.

Further, corresponding to the axial position of the rod 802, a state in which the main cylinder port opening 801a and the pressure-reducing cylinder port opening 801b communicate is possible.

The clogging/communicating state between the main cylinder port opening 801a and the pressure-reducing cylinder port opening 801b corresponds to the axial positions of the rod 802 and the outer spool 812 .

A dumping check valve 805 communicating with the main cylinder port 702a is connected to the cylindrical portion 810a of the casing 810 to a flow path formed in the radial direction as a position communicating with the dumping chamber 803 .

In the cylindrical portion 810a of the casing 810 , a plurality of orifice portions 807 are formed in a radial direction at positions capable of communicating with the dumping chamber 803 .

The opening position of the orifice portion 807 in the cylindrical portion 810a is set so that the number of flow passages communicating with the dumping chamber 803 can be increased or decreased according to the movement position of the rod 802 in the axial direction.

As the orifice portion 807 , for example, from the lid portion 810b to the lid portion 810c at the axial position of the rod 802 , the orifice opening 807a, the orifice opening 807b, and the orifice are in order. An opening 807c is disposed.

The orifice opening 807a, the orifice opening 807b, and the orifice opening 807c communicate with each other by an orifice flow path 807d disposed at a position close to the outer periphery of the cylindrical portion 810a.

A notch part 802b3 is provided in the end face 802b1 of the flange part 802b of the rod 802 so that it may contact the inner peripheral surface of the cylindrical part 810a etc. at the outer peripheral position.

The notch portion 802b3 corresponds to the axial position of the rod 802, and the communication state between the orifice opening 807a, the orifice opening 807b, and the orifice opening 807c and the dumping chamber 803 can be changed. there is.

In addition, a flow path communicating with the main cylinder port 702a may be provided in the casing 810 so as to send excess oil (incompressible fluid) to the hydraulic cylinder 710 .

Next, operation|movement of the switching valve 800 in this embodiment is demonstrated.

The selector valve 800 in this embodiment consists of a 3-position valve which has three positions similarly to 5th Embodiment. The three positions correspond to the expansion and contraction state of the rod 802 in the axial direction, respectively.

As for the rod 802, the inner surface of the regulating hole 802d slides with respect to the guide rod 810d. At this time, the rod internal space 803c of the regulating hole 802d of the rod 802 is maintained in the same atmospheric pressure atmosphere as the outside by the through hole 810d1.

Moreover, the radially outer surface of the flange part 802b of the rod 802 slides with respect to the inner peripheral surface of the cylindrical part 810a all around.

That is, the position is regulated on both inner and outer surfaces of the flange portion 802b of the rod 802 in the radial direction.

At the same time, in the rod 802 , the tip 802a of one end slides in the through hole 816 .

Thereby, positional control is performed at the positions of both ends of the rod 802 .

For this reason, the movement direction is regulated so that the rod 802 can move along the axial direction.

Therefore, when the kicker 25 abuts against, collides with, or is pressed against, the tip 802a of the rod 802 as shown in FIGS. 33 to 35 , the moving direction of the rod 802 is different from the axial direction. It moves in the axial direction without shaking and stably.

The first position is, as shown in FIG. 32 corresponding to FIG. 26 , to a position in which the rod 802 extends in the axial direction by the maximum distance that can be moved toward one end, which is the end at which the kicker 25 abuts or collides. is done

The third position is, as shown in FIGS. 31 and 35 corresponding to FIGS. 25 and 29 , a position in which the rod 802 is retracted by the maximum distance that can be moved toward the other end in the axial direction.

As shown in FIG. 30 corresponding to FIG. 24, the 2nd position consists of a position between a 1st position and a 3rd position in the axial direction of the rod 802. As shown in FIG. The second position is such that the rod 802 is proximate to the third position in the axial direction.

Next, in the switching valve 800 in the present embodiment, the driving unit 705 such as the motor of the cylinder driving unit 730 of the gate valve 100 is energized (powered), and the normal valve opening/closing operation is controllable. The operation of the cylinder driving unit 730 and the driving unit 705 such as a motor in a non-powered state due to a power failure or the like is shown in detail.

In addition, the spool flow path 801 of the switching valve 800 is made so that the spool flow path 801 can be opened only when the movable valve part 54 is in a valve opening blocking position and a valve closing position in any power supply state and a non-power supply state.

First, in a normal power supply state, the selector valve 800 operates between the second position and the third position.

Specifically, the hydraulic motor 705m of the drive unit 705 is energized, and, on the other hand, as for the switching valve 800 in the valve open state, the rod 802 is located at the second position.

That is, in the state in which the movable valve part 54 is a retracted position, and the flow path H develops and can distribute|circulate, as shown in FIG. 30, the rod 802 is located in a 2nd position.

At this time, as shown in FIG. 30, the front-end|tip 802a of the rod 802 protrudes outside the plane 810b1 of the casing 810 from the through-hole 816.

At the same time, in the orifice portion 807 , only the orifice opening 807c communicates with the dumping chamber 803 by the notch portion 802b3 .

In addition, the main cylinder port opening 801a communicates with the spool flow path 801 . Only the pressure-reducing cylinder port opening 801b is blocked by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

Therefore, the spool flow path 801 is clogged.

The surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

The end face 811b1 of the flange portion 811b is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the end surface 802b1 of the flange portion 802b of the rod 802 .

In this state, since the pressure applied to the end face 802b1 of the flange portion 802b of the rod 802 is greater than the pressure applied to the end face 812a2 of the cylindrical portion 812a of the outer spool 812, the rod ( A pressure is acting on the 802 from the lid portion 810c toward the lid portion 810b.

Accordingly, since the C-ring 814 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811, the axial position of the rod 802 is regulated. At the same time, since the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814, the axial position of the outer spool 812 is regulated.

Further, since the end face 802b1 of the flange portion 802b of the rod 802 is in contact with the surface 812b1 of the flange portion 812b of the outer spool 812, the axial position of the rod 802 is regulated. do.

For this reason, as shown in FIG. 30, the spool flow path 801 is made into a closed state, and in the dumping chamber 803, only the orifice opening part 807c becomes a communication 2nd position.

In addition, in a normal power supply state, in the state after the movable valve part 54 reaches a valve opening blocking position, as shown in FIG. 31, immediately after the rod 802 moves from a 2nd position to a 3rd position. am.

Further, by driving the valve case biasing portion 70, the movable valve portion 54 performs a sealing operation to change the position in the flow path H direction, and the movable valve portion 54 moves from the valve opening blocking position, The valve slides to the closed position, and the flow path (H) is blocked. In this state, as shown in FIG. 31, the rod 802 is located in the 3rd position.

At this time, as shown in Fig. 31, the tip 802a of the rod 802 is pushed into the through hole 816 by the kicker 25 and is flush with the plane 810b1 of the casing 810; Alternatively, the position is inserted into the through hole 816 .

At the same time, in the orifice portion 807 , there is no opening communicating with the dumping chamber 803 .

In addition, the main cylinder port opening 801a and the pressure-reducing cylinder port opening 801b communicate with the spool flow path 801 together. The outer peripheral surface of the cylindrical portion 812a of the outer spool 812 does not block either the main cylinder port opening 801a or the pressure reducing cylinder port opening 801b.

Therefore, the spool flow path 801 is in a communication state.

The surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

At this time, the end face 811b1 of the flange portion 811b is not in contact with the C-ring 814 cast on the rod 802, but is spaced apart.

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the end surface 802b1 of the flange portion 802b of the rod 802 .

In this state, since the tip 802a of the rod 802 is in contact with the kicker 25 , the rod 802 is directed from the lid portion 810b to the lid portion 810c by the kicker 25 . is pressed with

The pressure applied to the rod 802 in this direction is applied to the pressure applied to the end face 812a2 of the cylindrical portion 812a of the outer spool 812 and to the end face 802b1 in the flange portion 802b of the rod 802 . It works regardless of the magnitude of the pressure.

Accordingly, the axial position of the rod 802 is regulated. At the same time, since the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814, the axial position of the outer spool 812 is regulated.

Further, since the surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2, the axial position of the inner spool 811 is regulated.

For this reason, as shown in FIG. 31, the orifice part 807 of the dumping chamber 803 is clogged, and the spool flow path 801 becomes the 3rd position which can communicate.

Next, when the movable valve part 54 performs an opening operation to change the position in the flow path H direction, and the movable valve part 54 slides from the valve closing position to the valve opening closing position, the rod 802 ) moves from the third position to the second position.

At this time, the pressure applied to the end face 802b1 of the flange portion 802b of the rod 802 is greater than the pressure applied to the end face 812a2 of the cylindrical portion 812a of the outer spool 812 . For this reason, the pressure is acting on the rod 802 in the direction toward the lid part 810b from the lid part 810c.

At the same time, since the abutment of the kicker 25 from the tip 802a of the rod 802 is released, the rod 802 moves in the direction from the lid portion 810c to the lid portion 810b. The rod 802 moves to a position where the C-ring 814 cast on the rod 802 comes into contact with the end face 811b1 of the flange portion 811b of the inner spool 811 .

For this reason, as shown in FIG. 30, the spool flow path 801 is made into a closed state, and in the dumping chamber 803, only the orifice opening part 807c becomes a communication 2nd position.

Next, for example, a case in which a power outage occurs and power supply to the hydraulic motor 705m of the drive unit 705 is lost will be described.

Next, the selector valve 800 in the non-powered state, such as when a power failure or emergency occurs, moves from the second position to the first position, from the first position to the third position, and further, the second position and the third position. It operates between positions.

On the other hand, when the gate valve 100 is in the valve open state and the hydraulic motor 705m of the drive unit 705 is energized, when a power failure or the like occurs and becomes a non-powered state, at that moment, switching is performed. In the valve 800, as shown in FIG. 30, the state in which the rod 802 is located in the 2nd position is maintained.

In this state, in step S00 shown in FIG. 23, the movable valve part 54 exists in a retracted position.

When a power failure occurs in step S01 shown in FIG. 23 , in steps S02 to S21 shown in FIG. 23 , the operation of the rotary drive motor 220 is regulated and the operation of the hydraulic motor 705m is released.

Next, in step S23 shown in FIG. 23 , in the hydraulic cylinder 710 , the cylinder volume starts to be reduced by the biasing force of the hydraulic biasing member 720 . For this reason, in step S24 shown in FIG. 23, the pressure of the hydraulic cylinder 710 is raised by the biasing force of the hydraulic biasing member 720. As shown in FIG.

Since the inside of the dumping chamber 803 is in dynamic pressure with the hydraulic cylinder 710 by the dumping check valve 805, the pressure in the dumping chamber 803 rises.

When the pressure in the dumping chamber 803 rises, the rod 802 is pressed and moved, resists the biasing force of the biasing member 804, and the volume of the dumping chamber 803 expands. Thereby, the rod 802 extends from the 2nd position shown in FIG. 30 to the 1st position shown in FIG.

At this time, as shown in FIG. 32 , the tip 802a of the rod 802 protrudes from the through hole 816 to the outside by a maximum distance from the plane 810b1 of the casing 810 .

At the same time, in the orifice portion 807 , all of the orifice opening 807c , the orifice opening 807b , and the orifice opening 807a communicate with the dumping chamber 803 .

Moreover, the main cylinder port opening 801a is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical part 812a of the outer spool 812. Similarly, the pressure-reducing cylinder port opening 801b is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

Therefore, the spool flow path 801 is clogged.

In this state, in the hydraulic cylinder 710 , the pressure is increased by the biasing force of the hydraulic biasing member 720 , and the hydraulic pressure is supplied to the main cylinder port 702a.

Here, although the spool flow path 801 is blocked, flow is possible from the main cylinder port 702a to the dumping chamber 803 by the dumping check valve 805 connected in parallel with the spool flow path 801.

For this reason, hydraulic pressure is supplied to the dumping chamber 803 .

For this reason, in the dumping chamber 803 in which the pressure has risen, hydraulic pressure is acting on the end face 802b1 of the flange part 802b of the rod 802 from the lid part 810c toward the lid part 810b.

The surface 811c1 of the flange portion 811c of the inner spool 811 is at a position closer to the lid portion 810b than the stepped surface 810a2. That is, the surface 811c1 of the flange portion 811c is at a position spaced apart from the step surface 810a2.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

The end face 811b1 of the flange portion 811b is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the surface 802b2 of the flange portion 802b of the rod 802 .

Further, the C-ring 814 cast on the rod 802 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811 . A force is applied to the flange portion 811b of the inner spool 811 by the biasing member 804 in a direction from the lid portion 810b toward the lid portion 810c.

Here, hydraulic pressure is acting on the rod 802 in the direction from the lid portion 810c to the lid portion 810b on the end face 802b1 in the flange portion 802b. In addition, the rod 802 has a biasing member in a direction from the lid portion 810b opposite to the hydraulic pressure to the lid portion 810c via the flange portion 811b and the C ring 814 of the inner spool 811 . (804) is at work.

Compared to the biasing force of the biasing member 804 , the hydraulic pressure acting on the end face 802b1 is larger.

For this reason, the rod 802 moves and expands in the direction toward the lid part 810b from the lid part 810c.

Accordingly, since the C-ring 814 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811, the axial position of the rod 802 is regulated. At the same time, since the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814, the axial position of the outer spool 812 is regulated.

Further, since the end face 802b1 of the flange portion 802b of the rod 802 is in contact with the surface 812b1 of the flange portion 812b of the outer spool 812, the axial position of the rod 802 is regulated. do.

For this reason, as shown in FIG. 32, the spool flow path 801 is made into the closed state, and in the dumping chamber 803, the orifice part 807 becomes the 1st position which can communicate.

For this reason, in step S25 shown in FIG. 23, the rod 802 extended to the 1st position is in a waiting state waiting for the collision of the kicker 25. As shown in FIG.

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In this state, in step S26 to step S28 shown in FIG. 23 , the operation of the rotation drive motor 220 is released and the rotation shaft 20 is rotated by the front-end biasing device 230 .

For this reason, the movable valve part 54 starts a closing rotation operation|movement toward a valve opening blocking position from a retracted position.

In this state, the rotational operation of the rotating shaft 20 is not controlled even in the rotating shaft driving unit 200 . For this reason, the closing rotation operation|movement from the retracted position of the movable valve part 54 toward the valve opening blocking position is performed extremely rapidly.

In step S29 shown in FIG. 23 , by the closing operation, the kicker 25 abuts or collides with the tip 802a of the rod 802 positioned at the first position as shown in FIG. 33 . Continuing, the kicker 25 moves the rod 802 from the first position toward the second position by pressing the end of the rod 802 .

At this time, the tip 802a of the rod 802 protrudes outward from the through hole 816 rather than the plane 810b1 of the casing 810, but is located closer to the second position than the first position. .

At the same time, in the orifice portion 807, as shown in Fig. 33, the orifice opening 807c and the orifice opening 807b communicate with the dumping chamber 803, but are located closest to the lid portion 810b. The orifice opening 807a is blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

Moreover, the main cylinder port opening 801a is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical part 812a of the outer spool 812. Similarly, the pressure-reducing cylinder port opening 801b is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

Therefore, the spool flow path 801 is clogged.

The surface 811c1 of the flange portion 811c of the inner spool 811 is located closer to the lid portion 810b than the stepped surface 810a2. That is, the surface 811c1 of the flange portion 811c is at a position spaced apart from the step surface 810a2.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

The end face 811b1 of the flange portion 811b is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the surface 802b2 of the flange portion 802b of the rod 802 .

In this state, by the operation of the rod 802 colliding with the kicker 25, the volume of the dumping chamber 803 is about to be reduced instantaneously.

In this state, the tip 802a of the rod 802 moves from the lid part 810b to the lid part 810c by the impact force or pressing force of the kicker 25 that abuts or collides with the tip 802a. A force is acting in the direction of

The pressing force or impact force of the kicker 25 is transmitted to the dumping chamber 803 from the end face 802b1 in the flange portion 802b of the rod 802 .

For this reason, the dumping chamber 803 becomes high pressure instantaneously. Here, the rising pressure of the dumping chamber 803 is relieved by the orifice portion 807 communicating with the dumping chamber 803 .

For this reason, when the rod 802 is at a position close to the first position, all of the orifice opening 807c , the orifice opening 807b , and the orifice opening 807a are in communication with the dumping chamber 803 . For this reason, the pressure rise in the dumping chamber 803 can be released to the hydraulic cylinder 710 .

As the rod 802 moves in the direction close to the second position, the orifice opening 807a is blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

At this time, the flow rate of the hydraulic pressure released from the dumping chamber 803 to the hydraulic cylinder 710 can be reduced by the notch portion 802b3 .

Further, as the rod 802 moves closer to the second position, next, the orifice opening 807b is blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

Also at this time, the flow rate of the hydraulic pressure released from the dumping chamber 803 to the hydraulic cylinder 710 can be relaxed by the notch 802b3.

By the pressing force of the kicker 25 or the impact force, the rod 802 receives a reaction force from the end face 802b1 in the flange portion 802b. By this reaction force, it is possible to resist the impact force or the pressing force of the kicker 25 , and to relieve the movement of the rod 802 . That is, the movement of the kicker 25 can be relieved. That is, the closing operation of the movable valve unit 54 can be relieved.

At this time, in the hydraulic cylinder 710 , the pressure fluctuation is absorbed by the deformation of the hydraulic biasing member 720 .

The rising pressure of the dumping chamber 803, which has become a high pressure momentarily, is blocked by the dumping check valve 805 toward the main cylinder port 702a. For this reason, transmission of the high-pressure impact to the main cylinder port 702a and the part which communicates with the main cylinder port 702a is prevented.

Further, the C-ring 814 cast on the rod 802 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811 . A force is applied to the flange portion 811b of the inner spool 811 by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

Here, the impact force of the kicker 25 is acting on the rod 802 . In addition to this, in the rod 802, through the flange portion 811b and C-ring 814 of the inner spool 811, the biasing member 804 in the direction from the lid portion 810b to the lid portion 810c. There is a negative force at work.

Accordingly, since the C-ring 814 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811, the axial position of the rod 802 is regulated. At the same time, since the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814, the axial position of the outer spool 812 is regulated.

Further, since the end face 802b1 of the flange portion 802b of the rod 802 is in contact with the surface 812b1 of the flange portion 812b of the outer spool 812, the axial position of the rod 802 is regulated. do.

The spool flow path 801 maintains a closed state. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. The biasing member 804 applies a force to the rod 802 .

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In addition, by the closing operation, the rotation operation is continued from the retracted position of the movable valve part 54 toward the valve opening blocking position, and the movable valve part 54 approaches toward the valve opening blocking position.

In this state, the kicker 25 moves the rod 802 toward the second position by pressing it in a state in contact with the end of the rod 802, and, as shown in Fig. 34, the rod 802 moves to the second position. close to position

At this time, the tip 802a of the rod 802 protrudes from the through hole 816 so as to be located outside the plane 810b1 of the casing 810, but becomes a position close to the second position.

Here, by the operation of the rod 802 continuously pressed against the kicker 25, the volume of the dumping chamber 803 is continuously reduced. At this time, the dumping chamber 803 maintains a high-pressure state by gradually lowering. Here, the pressure in the dumping chamber 803 is continuously relieved by the orifice portion 807 communicating with the dumping chamber 803 .

At this time, the high pressure is continuously released from the dumping chamber 803 to the hydraulic cylinder 710 through the orifice portion 807 .

At this time, in the orifice portion 807 , as shown in FIG. 34 , the orifice opening 807c positioned closest to the lid portion 810c communicates with the dumping chamber 803 . In contrast, the orifice opening 807b and the orifice opening 807a positioned close to the lid portion 810b are blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

Moreover, the main cylinder port opening 801a communicates with the spool flow path 801 by the outer peripheral surface of the cylindrical part 812a of the outer spool 812. On the other hand, the pressure-reducing cylinder port opening 801b is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical portion 812a of the outer spool 812 .

Therefore, the spool flow path 801 is clogged.

The surface 811c1 of the flange portion 811c of the inner spool 811 is located closer to the lid portion 810b than the stepped surface 810a2. That is, the surface 811c1 of the flange portion 811c is at a position spaced apart from the step surface 810a2.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

The end face 811b1 of the flange portion 811b is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the surface 802b2 of the flange portion 802b of the rod 802 .

In this state, the volume of the dumping chamber 803 is continuously reduced by the operation of the rod 802 pressed by the kicker 25 .

In this state, the tip 802a of the rod 802 is directed from the lid part 810b to the lid part 810c by the pressing force of the kicker 25 that abuts or collides with the tip 802a. force is at work.

The pressing force of the kicker 25 is transmitted to the dumping chamber 803 from the end face 802b1 in the flange portion 802b of the rod 802 .

Due to this, the dumping chamber 803 maintains a high-pressure state. Here, the pressure relief of the dumping chamber 803 by the orifice portion 807 continues.

For this reason, as the rod 802 moves to a position close to the second position, the orifice opening 807a and the orifice opening 807b are blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

At this time, the flow rate of the hydraulic pressure released from the dumping chamber 803 to the hydraulic cylinder 710 can be reduced by the notch portion 802b3 .

In addition, as the rod 802 moves to approach the second position, the flow rate of the hydraulic pressure released from the dumping chamber 803 to the hydraulic cylinder 710 by the notch 802b3 can be reduced.

As the rod 802 moves and approaches the second position, the flow rate of the orifice portion 807 decreases, and furthermore, it is possible to moderate the moving speed of the rod 802 .

For this reason, the movement of the kicker 25, ie, the relaxation of the closing operation|movement of the movable valve part 54, can be performed inclinedly.

In the hydraulic cylinder 710 , pressure fluctuations are continuously absorbed by the deformation of the hydraulic biasing member 720 .

The pressure in the high-pressure dumping chamber 803 is shut off toward the main cylinder port 702a by the dumping check valve 805 . For this reason, transmission of the high-pressure impact to the main cylinder port 702a and the part which communicates with the main cylinder port 702a is prevented.

Further, the C-ring 814 cast on the rod 802 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811 . A force is applied to the flange portion 811b of the inner spool 811 by the biasing member 804 in a direction from the lid portion 810b toward the lid portion 810c.

Here, the pressing force of the kicker 25 is acting on the rod 802 . In addition to this, in the rod 802, through the flange portion 811b and C-ring 814 of the inner spool 811, the biasing member 804 in the direction from the lid portion 810b to the lid portion 810c. There is a negative force at work.

Accordingly, since the C-ring 814 is in contact with the end face 811b1 of the flange portion 811b of the inner spool 811, the axial position of the rod 802 is regulated. At the same time, since the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814, the axial position of the outer spool 812 is regulated.

Further, since the end face 802b1 of the flange portion 802b of the rod 802 is in contact with the surface 812b1 of the flange portion 812b of the outer spool 812, the axial position of the rod 802 is regulated. do.

The spool flow path 801 remains closed until the rod 802 reaches the second position. The main cylinder port 702a and the pressure-reducing cylinder port 702b are blocked. The biasing member 804 applies a force to the rod 802 .

From the hydraulic cylinder 710 in which the pressure has risen toward the valve case biasing part 70, it is blocked by the check valve 806.

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

In addition, by the closed rotation operation, the kicker 25 is pressed firmly in a state in contact with the end of the rod 802, so that the rod 802 reaches the second position.

In this state, the orifice portion 807 is blocked by the movement of the rod 802 , and the dumping chamber 803 is blocked with respect to the hydraulic cylinder 710 .

At this time, in the orifice part 807, similarly to the state shown in FIG. 30, the orifice opening 807c located closest to the lid part 810c is separated from the dumping chamber 803 by the notch part 802b3. are communicating Further, the orifice opening 807b and the orifice opening 807a positioned close to the lid portion 810b are blocked by the outer peripheral surface of the flange portion 802b of the rod 802 .

For this reason, pressure relief is complete|finished. At this time, the pressure fluctuation is absorbed by the deformation|transformation of the hydraulic pressure member 720 in the hydraulic cylinder 710, and the pressure of the dumping chamber 803 is falling enough.

Moreover, the main cylinder port opening 801a communicates with the spool flow path 801 by the outer peripheral surface of the cylindrical part 812a of the outer spool 812. On the other hand, the pressure reduction cylinder port opening 801b is blocked with respect to the spool flow path 801 by the outer peripheral surface of the cylindrical part 812a of the outer spool 812.

Therefore, the spool flow path 801 is clogged.

A force is applied to the flange portion 811b by the biasing member 804 in a direction from the lid portion 810b to the lid portion 810c.

The end face 811b1 of the flange portion 811b is in contact with the C-ring 814 cast on the rod 802 .

The surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2.

For this reason, the biasing member 804 is in a state in which the biasing of the rod 802 is released.

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the surface 802b2 of the flange portion 802b of the rod 802 .

In this state, a pressing force is applied to the tip 802a of the rod 802 in the direction from the lid portion 810b to the lid portion 810c by the kicker 25 in contact with the tip 802a.

The pressing force of the kicker 25 is transmitted to the dumping chamber 803 from the end face 802b1 in the flange portion 802b of the rod 802 .

From the hydraulic cylinder 710 toward the valve case biasing portion 70 , it is blocked by the check valve 806 .

For this reason, the pressure of the valve case biasing part 70 does not fluctuate.

Accordingly, the valve case biasing portion 70 maintains the state in which the distal end of the movable portion 72 is retracted by the biasing member 73 .

Moreover, in step S30 shown in FIG. 23, the movable valve part 54 arrives at a valve opening blocking position by a closing rotation operation|movement as shown in FIG.

In this state, the kicker 25 is pressed while abutting against the end of the rod 802 . Due to this, the rod 802 passes through the second position to reach the third position.

At this time, the kicker 25 comes into contact with the flat surface 810b1 of the lid part 810b of the casing 810 . For this reason, the kicker 25 becomes an operation stop position, and the closing operation|movement of the kicker 25 is complete|finished. The plane 810b1 regulates the end position of the closing operation in the closing operation of the kicker 25 .

Here, as shown in FIG. 35, simultaneously with the moment when the movable valve part 54 reached|attained the valve opening blocking position, the rod 802 will reach|attain the 3rd position.

When the rod 802 reaches the third position, the spool flow path 801 first enters the communication state by the movement of the rod 802 .

At this time, as shown in FIG. 35, the tip 802a of the rod 802 is pushed into the through-hole 816 by the kicker 25 and is flush with the plane 810b1 of the casing 810; Alternatively, it is at a position inserted into the through hole 816 .

At the same time, in the orifice portion 807 , there is no opening communicating with the dumping chamber 803 .

In addition, the main cylinder port opening 801a and the pressure-reducing cylinder port opening 801b communicate with the spool flow path 801 together. The outer peripheral surface of the cylindrical portion 812a of the outer spool 812 does not block either the main cylinder port opening 801a or the pressure reducing cylinder port opening 801b.

Therefore, the spool flow path 801 is in a communication state.

The surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2.

The flange portion 811b is urged by the biasing member 804 in the direction from the lid portion 810b to the lid portion 810c.

At this time, the end face 811b1 of the flange portion 811b is not in contact with the C-ring 814 cast on the rod 802, but is spaced apart.

Accordingly, no force is applied to the rod 802 by the biasing member 804 .

The surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 cast on the rod 802 .

The surface 812b1 of the flange portion 812b is in contact with the end surface 802b1 of the flange portion 802b of the rod 802 .

In this state, the tip 802a of the rod 802 is in contact with the kicker 25 . This state is maintained regardless of the magnitude of the pressure applied to the end face 812a2 of the cylindrical portion 812a of the outer spool 812 and the pressure applied to the end face 802b1 of the flange portion 802b of the rod 802 . do.

In this way, the tip 802a of the rod 802 is in contact with the kicker 25 . For this reason, the rod 802 is pressed by the kicker 25 in the direction toward the lid part 810c from the lid part 810b.

Accordingly, the axial position of the rod 802 is regulated. At the same time, the surface 812b2 of the flange portion 812b of the outer spool 812 is in contact with the C-ring 814 . For this reason, the axial position of the outer spool 812 is regulated.

Further, the surface 811c1 of the flange portion 811c of the inner spool 811 is in contact with the step surface 810a2. For this reason, the axial direction position of the inner spool 811 is restricted.

For this reason, as shown in FIG. 35, the orifice part 807 of the dumping chamber 803 is clogged, and the spool flow path 801 becomes the 3rd position which can communicate.

Then, the hydraulic pressure supply is replaced by the switching function of the switching valve 800 .

That is, from the hydraulic cylinder 710 toward the valve case biasing portion 70 , it is blocked by the check valve 806 , but communicates with the spool flow passage 801 .

For this reason, the pressure of the valve case biasing part 70 rises.

Accordingly, the valve case biasing part 70 generates a driving force greater than the biasing force of the biasing member 73 , and the distal end of the movable part 72 is extended.

At this time, it is pressed by the front-end|tip part of the movable part 72, and in step S31 shown in FIG. 23, the sealing operation|movement in which the movable valve part 54 changes the position in the flow path H direction.

For this reason, the movable valve part 54 slides from a valve opening blocking position to a valve closing position, and the flow path H is blocked.

For this reason, the valve closing operation by the springback as a normal closing operation in an emergency such as a power failure is completed.

By the above, the gate valve 100 of this embodiment performs step S21, step S25, step S26, and step S29 in this order. For this reason, it becomes possible to show the shock alleviation function and the hydraulic pressure switching function as a hydraulic damper in the switching valve 800. As shown in FIG.

Incidentally, in the inside of the casing 810, the rod internal space 803c and the spool flow passage 801 are in the same pressure state except for the dumping operation state (pressure relief state) in which high pressure is applied to the dumping chamber 803. . In addition, the rod internal space 803c is always maintained at atmospheric pressure.

Conversely, in the inside of the casing 810 , in the dumping operation state (pressure relief state), only the dumping chamber 803 becomes high pressure by the dumping check valve 805 .

In addition, the timing at which the release control unit 101 outputs the release instruction signal in step S26 is waiting for the rod 802 to extend to the first position and to wait for the kicker 25 to collide in step S25. This is done after the state has been detected. Here, the reception state of the rod 802 can be detected by a position sensor with respect to the rod 802 or the like.

In the present embodiment, similarly to the above-described sixth embodiment, the effect of realizing a normal closing operation that simultaneously exhibits incompressible fluid supply switching and shock mitigation can be achieved.

EMBODIMENT OF THE INVENTION Hereinafter, the gate valve which concerns on 7th Embodiment of this invention is demonstrated based on drawing.

Fig. 36 is a cross-sectional view in the rotational axis direction for explaining the rotational shaft driving unit of the oil gate valve in the present embodiment.

What is different from the second embodiment described above with respect to this embodiment is that the planetary gear clutch of the rotating shaft drive unit is related, and the corresponding components other than the above are assigned the same reference numerals and the description thereof is omitted.

The rotary shaft drive unit 200 in the present embodiment is configured to have a function equivalent to that of the rotary shaft drive unit 200 in the second embodiment described above.

The rotary shaft drive unit 200 in this embodiment also consists of an electric actuator for rotating the rotary shaft 20 similarly to 2nd Embodiment mentioned above.

In the rotary shaft drive unit 200, the mainspring shaft 231c and the brake shaft 241c are configured as a single joint shaft 205c.

The joint shaft 205c is arranged parallel to the rotation shaft 20 . The joint shaft 205c is configured to correspond to the mainspring shaft 231c in the above-described embodiment.

A spring 231 and an excitation-actuated brake 241 are connected to the joint shaft 205c.

The spring 231 and the excitation-actuated brake 241 are connected to the joint shaft 205c at different positions in the axial direction on the joint shaft 205c.

In addition, a relay gear 209 is disposed between the rotation drive motor 220 and the drive gear 211 .

The mass gear 244 and the minor gear 243 are rotatably mounted on the rotating shaft 20 .

A non-excitation brake 221 is connected to the rotation drive motor 220 .

The non-excitation operation brake 221 exerts a brake function at the time of shearing, and stops the rotation of the rotation drive motor 220 .

The non-excitation operation brake 221 releases the brake function when energized, and enables the rotational drive motor 220 to be rotationally driven. The non-excitation operation brake 221 is connected to the brake operation release part 225f.

In addition, the rotation drive motor 220 may be accompanied by the gear unit which adjusts torque and rotation speed, and the motor unit for control other than the said structure.

A counterweight CW (balance) of the neutral valve body 5 is provided on the rotating shaft 20 , and the torque required for the rotation drive motor 220 and the spring 231 can be reduced.

The counterweight CW is provided at a position axially symmetric with the neutral valve body 5 of the rotation shaft 20 . In addition, this counter weight CW can also be provided as the switch (stopper) 21 for operation|movement of the selector valve 800 .

In addition, in FIG. 36, the code|symbol 32 has shown the location where the counterweight is attached.

In the present embodiment, similarly to the above-described embodiment, the effect of realizing a normally closed operation that simultaneously exhibits incompressible fluid supply switching and shock relaxation can be achieved.

In this invention, it is also possible to select and combine the individual structures in each said embodiment as appropriate.

10… valve case
11… hollow body
20… axis of rotation
25… kicker
30… neutral valve
40… movable valve part
50… movable valve plate
54… Movable valve part (movable valve plate part)
63… valve frame
70… Valve case detail (pressure-reducing cylinder)
71… fixed part
72… Movable part (extensible rod)
73... bias member (pressure spring)
80… Valve plate detail (maintenance spring)
90… Valve frame detail (auxiliary spring)
100… gate valve
101… release control
102... UPS device
200… rotating shaft drive
220… rotary drive motor
221… excitation-actuated brake
225f… brake action release
227... power
230… shear bias device
231… mainspring
700… Hydraulic drive (incompressible fluid drive)
700… hydraulic drive
701… hydraulic pressure generator
702… hydraulic pipe
705... drive part
705b... excitation-actuated brake
705f… brake action release
705m… hydraulic motor
707... power
710… Hydraulic Cylinder (Main Cylinder)
720… Hydraulic bias member (main spring)
800… switching valve (spool valve)
802… Load (transition sensor)
H… Euro

Claims (7)

A gate valve capable of normally closed operation, comprising:
A valve case having a hollow portion and a first opening and a second opening that are installed to face each other between the hollow portion and serve as a communicating passage;
a valve body capable of opening and closing the flow path;
a rotating shaft that rotatably supports the valve body between a retracted position and a valve opening blocking position in the hollow portion and has an axis extending in a flow path direction;
a rotating shaft driving unit having a rotational driving motor capable of rotating the rotating shaft and rotating the valve body;
a movable valve part that enables the position in the flow path direction to be changed and is installed on the valve body;
a valve case part attached to the valve case to move and close the movable valve part at the valve opening blocking position in the flow path direction;
And a hydraulic driving unit for driving by supplying working hydraulic pressure to the valve case part;
a hydraulic pressure generating unit for generating hydraulic pressure from the hydraulic driving unit;
a driving unit having a hydraulic motor for driving the hydraulic pressure generating unit and a hydraulic biasing member;
a power supply to the rotary shaft driving unit and the driving unit;
a first non-excitation brake for regulating the operation of the rotation drive motor during shearing;
a second non-excitation brake for regulating the operation of the hydraulic motor during shearing;
and a brake operation release unit for releasing the operation of the first non-excitation operation brake and the second non-excitation operation brake,
gate valve.
According to claim 1,
The brake operation release unit,
the first non-excitation brake for regulating the operation of the rotation drive motor;
capable of independently disengaging the second non-energized actuation brake regulating the operation of the hydraulic motor;
gate valve.
According to claim 1,
The brake operation release unit,
Release the operation of the first non-excitation operation brake that regulates the operation of the rotation drive motor,
thereafter, releasing the operation of the second non-exciter-actuated brake that regulates the operation of the hydraulic motor,
gate valve.
4. The method according to any one of claims 1 to 3,
The brake operation release unit,
connected to a release control unit capable of outputting a release instruction signal based on information in the flow path;
gate valve.
5. The method of claim 4,
determining whether or not the release control unit outputs a release instruction signal based on the information in the flow path;
gate valve.
According to claim 1,
The brake operation release unit,
Release the operation of the second non-excitation brake that regulates the operation of the hydraulic motor,
After enabling the hydraulic damper to operate,
to release the operation of the first non-exciter-actuated brake that regulates the operation of the rotary drive motor,
gate valve.
4. The method according to any one of claims 1 to 3,
The brake operation release unit,
made capable of manual operation,
gate valve.

Images