JP2769447B2 - Emergency shut-off valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an emergency shut-off valve which closes with energy stored in a spring in an emergency, and more particularly, to improve the reliability of the spring by directly connecting the spring and a valve shaft. Emergency shutoff valve.

[0002]

2. Description of the Related Art As an example of a conventional emergency shut-off valve, Japanese Utility Model Laid-Open No.
There is one described in 3-150179.
This emergency shut-off valve whose main part is shown in FIG. 11 is basically composed of an output shaft 91 to which a valve element is attached, and a
An electric motor 93 meshed via a gear train including a gear train 2 and a mainspring spring 95 meshed with the output shaft 91 via a gear 94 and further increased by rotation of the output shaft 91 in the valve opening direction.
It is composed of

An idle gear 96 that supports the planetary gear 92 at an eccentric position is coaxial with the output shaft 91 and is connected to the output shaft 9.
An electromagnetic lock 97 is provided rotatably with respect to the gear 1 and allows or prevents the rotation of the idle gear 99. Here, a gear ratio is provided between the electric motor 93 and the output shaft 91 to reduce the rotation of the electric motor 93 to about 1/50. A gear ratio is provided between the output shaft 91 and the center axis of the mainspring 95 to increase the rotation of the output shaft 91 by about 20 times.

When the valve is opened in this configuration, the electric motor 9 is opened.
3 and the electromagnetic lock 97 are energized together. At this time, the rotation of the idle gear 96 is prevented by energizing the electromagnetic lock 97, so that the position of the planetary gear 92 is fixed and the rotation of the electric motor 93 is transmitted to the output shaft 91. Then, when the electric motor 93 is energized, the output shaft 91 and the butterfly-shaped valve body (not shown) attached to the lower end 91a are rotated by 90 ° to be in a fully open state, and stop in that state. At the time of this valve opening operation, the rotation of the output shaft 91 is also transmitted to the mainspring 95 via the gear 94,
The mainspring 95 is wound about five times. Thereby, energy is stored in the mainspring 95.

On the other hand, when the valve is closed, the electric motor 93 is closed.
And the electromagnetic lock 97 are turned off. At this time, since the rotation of the idle gear 96 is permitted by turning off the power supply to the electromagnetic lock 97, the position of the planetary gear 92 becomes free and the electric motor 93 and the output shaft 91 are disconnected. At the same time, the central axis rotates in a direction to release the energy of the mainspring spring 95 that has been wound and loosen the winding. This rotation is transmitted through the gear 94 to the output shaft 9.
1, the output shaft 91 rotates 90 ° in the valve closing direction,
The valve element also rotates to the fully closed state.

[0006]

However, this emergency shut-off valve has the following problems. First,
The reliability of the mainspring 95 is low. The reason for this is that the spring is not used in the mainspring 95 itself, but is used such that it is wound up about five times when the valve is opened. That is, due to the additional winding, it is difficult to avoid contact between the spring plates, and surface damage due to friction is inevitable. Since a special spring is usually provided with a special surface coating for securing strength and spring characteristics, the coating is damaged and may lead to failure such as breakage.

The amount of additional winding is derived from the gear ratio between the output shaft 91 and the central axis of the mainspring spring 95. This emergency shut-off valve uses the electric motor 93 as a drive source, and thus has such an effect. You have to adopt a different gear ratio. The output of the electric motor 93 having a size suitable for this type of application is not so strong at most about several kW, so that a strong spring having a large spring constant cannot be used as the spring 90, and therefore, the output shaft 91 is closed. This is because the driving force for rotating in the direction can be obtained only by the number of windings. In addition, external foreign matter may enter the mainspring 95 from the side end face and damage the surface coating, leading to a similar failure.

A second problem is that the structure is complicated, the number of parts is large, and the outer shape is large. Since the gear ratio between the output shaft 91 and the central axis of the mainspring spring 95 is not 1: 1 as described above, the mainspring spring 95 must be disposed via a gear 94 on a shaft separate from the output shaft 91. . Further, since the electric motor 93 is used as a drive source as described above, the electric motor 93 and the output shaft 91 need to be connected at the time of the valve opening operation, and they must be disconnected at the time of the valve closing operation. This is also because the lock 97 is provided.

The present invention has been made to solve such a problem of the conventional emergency shut-off valve, and an object of the present invention is to increase the amount of winding of the mainspring spring when the valve is opened. Make it smaller to match the rotation angle,
It is an object of the present invention to provide an emergency shut-off valve in which the spring is prevented from being damaged by contact with a base plate to improve reliability, and the overall size of the emergency shut-off valve is reduced by making the mainspring coaxial with an output shaft. Then, by adopting a sufficiently powerful hydraulic device as a driving means for opening the valve on the output shaft, the amount of additional winding of the mainspring is matched with the rotation angle of the output shaft, and the reversing force of the mainspring is transmitted to the driving means. It is an object of the present invention to simplify the structure by eliminating the need for a mechanism for preventing the above. It is another object of the present invention to prevent damage to the mainspring due to foreign matter entering the mainspring from a side end face, thereby similarly improving reliability.

[0010]

[Means for Solving the Problems]

(1) To achieve this object, the emergency shut-off valve of the present invention
A valve element for opening and closing the fluid flow path, an output shaft to which the valve element is attached, a driving unit for rotating the output shaft in a valve opening direction, and a mainspring spring increased by rotation of the output shaft in the valve opening direction. The gist is that the inner end of the mainspring is attached to the output shaft.

(2) The emergency shut-off valve of the present invention comprises a valve element for opening and closing a fluid flow path, an output shaft to which the valve element is attached, driving means for rotating the output shaft in a valve opening direction, The gist of the present invention is an emergency shut-off valve having a mainspring spring that is increased by the rotation of the output shaft in the valve opening direction, and a protection plate that covers a side end surface of the mainspring.

(3) Further, the emergency shut-off valve of the present invention comprises (2)
Wherein the inner end of the mainspring is attached to the output shaft.

(4) Further, the emergency shut-off valve of the present invention comprises (1)
The emergency shut-off valve according to any one of (1) to (3), wherein the driving means is a hydraulic cylinder and a relief valve for releasing the hydraulic pressure applied to the hydraulic cylinder is provided.

(5) The emergency shut-off valve of the present invention comprises:
, Wherein two or more relief valves are provided in parallel.

[0015]

According to the emergency shut-off valve of the present invention having the above construction,
When the driving means generates a driving force, the driving force is transmitted to the output shaft. For this reason, the output shaft rotates in the valve opening direction, and the valve body also rotates with the rotation to open the fluid flow path. At this time, the mainspring is increased. When the driving force of the driving means is lost, the winding of the mainspring spring returns, and the output shaft rotates in the valve closing direction. At the same time, the valve body also rotates to close the fluid flow path.

(1) In the emergency shut-off valve of the present invention, the amount of additional winding of the mainspring in the valve open state is equal to the rotation angle of the output shaft and is small, so that contact between the base plates of the mainspring does not occur.

(2) In the emergency shut-off valve of the present invention, the protection plate is provided on the mainspring, so that the intrusion of external foreign matter which may cause damage to the mainspring from the side end face is prevented.

(3) In the emergency shut-off valve according to the present invention, both contact between the spring spring base plates and entry of external foreign matter from the side end face are prevented.

(4) In the emergency shut-off valve of the present invention, when hydraulic pressure is applied to the hydraulic cylinder, the output shaft and the valve body are rotated by the driving force generated by the hydraulic cylinder, and the fluid flow path is opened. When the relief valve is opened, the hydraulic pressure supplied to the hydraulic cylinder is released and disappears. For this reason, the output shaft and the valve element are rotated by the unwinding of the mainspring, and the fluid flow path is closed. At this time, the rotation of the output shaft in the valve closing direction is also transmitted to the hydraulic cylinder.

(5) In the emergency shut-off valve of the present invention, if a large-capacity relief valve is opened during the valve closing operation, the hydraulic pressure rapidly disappears, and the output shaft and the valve element rotate rapidly. The fluid flow path is immediately closed. If only the small-capacity relief valves are opened and the remaining relief valves are kept closed, the oil pressure gradually disappears, the output shaft and the valve body rotate slowly, and the fluid flow path is closed gently.

[0021]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of an emergency shut-off valve according to the present invention. An emergency shutoff valve 1 shown in a sectional view in FIG. 1 opens and closes a gas supply line in a system using gas, and is roughly divided into a valve unit 2 and a drive unit 3.

The valve portion 2 mainly includes a body 5 having ports 6 and 7 formed therein and a ball valve 9 rotatably held therein. The ball valve 9 is formed with a through hole 10 penetrating in the horizontal direction. In the state shown in FIG. 1, the through hole 10 is perpendicular to the gas flow path between the ports 6 and 7, and the ball valve 9 comes into close contact with the valve seat 11 on the inner surface of the body 5 to close the gas flow path. ing. By rotating the ball valve 9, the through hole 10 can be switched to an open state (see FIG. 2) parallel to the gas flow path. A cylindrical stem 13 that holds the ball valve 9 is rotatably held on the upper part of the body 5. The stem 13 is for connecting the ball valve 9 and a gear shaft 15 of the drive unit 3 described later.

The drive section 3 has an outer shape formed by an oil case 17, an upper lid 18 for sealing the upper part thereof, and a switch case 19 further above the oil case 17, and the gear shaft 15 is rotatable at the center thereof. It is pivoted. The drive section 3 is for driving the ball valve 9 of the valve section 2 to open and close by rotating the gear shaft 15. For this purpose, an electromagnetic pump 21, a relief valve 22, a hydraulic cylinder 23, and a mainspring 25 are provided. have.

The oil case 17 is a substantially rectangular parallelepiped member whose upper part is open, has a portion through which the gear shaft 15 is inserted and a mainspring spring 25 built in, and oil chambers 26 and 27 formed on both sides thereof. ing. The oil chambers 26 and 27 are portions that store oil supplied to the hydraulic cylinder 23 and that incorporate the electromagnetic pump 21 and the relief valve 22. The oil chambers 26 and 27 communicate with each other. The electromagnetic pump 21 has a solenoid 29 and pressurizes oil in an oil chamber 26 to
3 to send. On the other hand, the relief valve 22 switches the communication relationship between the hydraulic cylinder 23 and the oil chamber 27. The oil case 17 is attached to the valve section 2 via a mount 14, and the gear shaft 15 is connected to the stem 13.

The upper part of the oil case 17 is sealed by an upper lid 18, and oil chambers 26 and 27 are shut off from the outside. The upper lid 18 has a hydraulic cylinder 23 and an oil chamber 26,
27 and oil passages 31 and 33 that communicate with each other.
These are communicated by a communication path 35. Further, a maintenance port 34 which is normally closed and used when replenishing or replacing oil is provided.

A hydraulic cylinder 23 is provided above the upper cover 18. The hydraulic cylinder 23 has pistons 37 on both sides of the gear shaft 15 and a liner 38 serving as a sliding surface thereof, and has head covers 32, 3 on both ends.
Pressure chambers 41, 41 are provided by sealing with 2. The oil passages 31, 33 communicate with the pressure chambers 41, 41. A rack and pinion mechanism is provided between the pistons 37, 37 and the gear shaft 15, so that the reciprocating motion of the pistons 37, 37 is converted into the rotational motion of the gear shaft 15. Also, the head covers 32, 32
Limiters 36, 3 for limiting the movement of the pistons 37, 37
6 are provided.

The details are shown in the AA sectional view of FIG. Rack gears 42, 42 are formed on the pistons 37, 37 on the opposite sides of the pressure chambers 41, 41, respectively. On the other hand, a pinion gear 43 is formed on the gear shaft 15, and is meshed with the rack gears 42, 42. Thus, when the hydraulic pressure P is applied to the pressure chambers 41 from the electromagnetic pump 21, the gear shaft 15 is rotated counterclockwise in FIG. With this rotation, the ball valve 9 of the valve section 2 is rotated to perform an opening and closing operation.

Returning to FIG. 1, a switch case 19 is mounted on the upper portion of the hydraulic cylinder 23, and micro switches 45 and 46 for detecting the rotation angle of the gear shaft 15 are provided inside the switch case 19. The microswitch 45 has a role as a limit switch that issues a stop signal for the electromagnetic pump 21 when the valve unit 2 is at a position where the valve unit 2 is fully opened. Also, it has a role of confirming that the valve portion 2 is fully opened. The micro switch 46 is
It has a role of confirming that the valve section 2 is fully closed.
A cam 47 for operating the micro switches 45 and 46 is attached to the upper end of the gear shaft 15.

Next, the mainspring 25 will be described.
The mainspring 25 is an elastic strip-shaped base plate 25.
a is spirally wound, its outer end 25b is locked to the pole 51 as shown in the enlarged view of FIG. 3, and its inner end 25c is
7 is assembled to the gear shaft 15 as shown in FIG. The pole 51 is fixed to the upper cover 18 by bolts 53 and 54. A groove 15a is provided in the gear shaft 15 in the axial direction, and an inner end 25c of the mainspring 25 is attached to the groove 15a. The base plate 25a is coated with a lubricant. The periphery of the mainspring 25 is held by a strap 55 to prevent contact with other members.

The mainspring 25 is mounted on the gear shaft 1.
5 rotates in the valve-opening direction, and the energy is increased and accumulates energy (see FIG. 7). When the pressure application of the electromagnetic pump 21 is released, the energy is released. It is for rotating in the valve closing direction. Since a torque is required at the time of rewinding, the mainspring spring 25 is assembled about one turn from the free state and preloaded, even when the winding is not increased (FIG. 5).

The relationship between the state of the mainspring 25 and the open / closed state of the valve section 2 is as follows. First, the valve 2 is closed (FIG. 1) when the mainspring 25 has not been further wound. At this time, the pistons 37 in the hydraulic cylinder 23 come into contact with the limiters 36, 36 of the head covers 32, 32. On the other hand, when the mainspring 25 is further wound, the valve portion 2 is open (FIG. 2).

A guide plate 50 is provided at the lower end of the mainspring 25.
A thrust sheet 49 is attached to a surface of the mainspring 25 facing the spring. A thrust sheet 49 is also provided at the upper end of the mainspring 25. The guide plate 50 is a base plate 25 of the mainspring 25.
This is for preventing the intrusion of foreign matter between the spaces a. The upper end is not provided because the distance from the upper lid 18 is originally narrow and foreign matter is unlikely to enter. The thrust sheet 49 is a disk-shaped member as shown in FIG. 8, and is made of a low-friction material (such as a fluororesin). This thrust sheet 49 is
Even if the base plate 25a slightly protrudes in the thrust direction due to problems such as machining accuracy, the friction is reduced to prevent the coating from peeling off.

Next, the relief valve 22 will be described with reference to the sectional view of FIG. The relief valve 22 held in the oil chamber 27 of the oil case 17 includes a solenoid case 57 fixed to the upper cover 18 and a core 5 held inside the solenoid case 57.
8 and a solenoid 30, and a movable iron core 59 movable up and down with respect to the core 58. Above the core 58, the valve seat 6 is provided.
3 are provided. And a stem 61 penetrating the core 58 is attached to the upper end of the movable iron core 59,
The valve body 62 is attached to the tip via a spring 65. A return oil port 67 for receiving return oil from the oil passage 33 is provided above the valve seat 63, and an orifice plate 66 having a small hole is attached thereto.

FIG. 9 shows a state in which the solenoid 30 is energized to move the movable iron core 59 upward.
Is in contact with the valve seat 63 to close the oil passage.
That is, the communication between the hydraulic cylinder 23 and the oil chamber 27 is cut off. When the energization of the solenoid 30 is cut off, the movable iron core 59 becomes free, and the oil pressure in the return oil port 67 pushes the valve body 62 away from the valve seat 63 to open the oil flow path. And the oil chamber 27 communicate with each other.

Next, the operation of the emergency cutoff valve 1 will be described. First, a state in which the gas supply is stopped will be described. In this case, the power supply to both the electromagnetic pump 21 and the relief valve 22 is turned off. Since the electromagnetic pump 21 is off, no hydraulic pressure is generated, and therefore no hydraulic pressure is applied to the hydraulic cylinder 23. For this reason, only the elastic force for returning the winding of the mainspring 25 acts on the gear shaft 15. Therefore, the gear shaft 15 is in the state shown in FIGS. 4 and 5, and at this time, the ball valve 9 in the valve section 2 is in the closed state in contact with the valve seat 11 (FIG. 1). As a result, the gas supply is stopped. At this time, in the hydraulic cylinder 23, the pistons 37, 37 are in contact with the limiters 36, 36 of the head covers 32, 32, thereby preventing the gear shaft 15 from further rotating.

When supplying gas, both the electromagnetic pump 21 and the relief valve 22 are turned on. Then, the hydraulic pressure is generated by turning on the electromagnetic pump 21, and the oil is pumped from the oil chamber 26. When the relief valve 22 is turned on, the communication between the hydraulic cylinder 23 and the oil chamber 27 is cut off as shown in FIG. The pistons 37, 37 are pushed inward in FIG. For this reason, as shown in FIGS.
5 rotates against the elasticity of the mainspring 25, and the ball valve 9 of the valve portion 2 rotates accordingly. By this rotation, the spring 25 is further wound, and energy is stored.

When the rotation angle reaches 90 °, the micro switch 45 detects this and issues a stop signal. For this reason, the electromagnetic pump 21 is turned off, and the oil pumping is stopped.
On the other hand, since the communication between the hydraulic cylinder 23 and the oil chamber 27 is still cut off while the relief valve 22 is kept on, the hydraulic pressure already applied to the pressure chambers 41 is maintained as it is. For this reason, the gear shaft 15 cannot rotate and maintains that state. At this time, in the valve section 2, the through hole 10 of the ball valve 9 is parallel to the gas flow path (FIG. 2),
Gas supply is provided. As described above, since the ball valve 9 and the gear shaft 15 rotate only 90 °, the winding amount of the mainspring spring 25 is also only 1/4 turn, and the base plates 25a hardly come into contact with each other due to the additional winding. The coating film is not damaged.

To stop the gas supply, the power supply to the relief valve 22 is turned off. Then, the relief valve 2 shown in FIG.
2, the movable iron core 59 is free, while the oil pressure of the pressure chambers 41, 41 is applied to the valve body 62, so that the valve body 62 is separated from the valve seat 63 to open the oil passage, and the pressure chamber 4 is opened.
The hydraulic pressures 1 and 41 are released to the oil chamber 27 and disappear. Therefore, the force acting on the gear shaft 15 is only the elasticity of the spiral spring 25 that has been increased. Therefore, the energy stored in the mainspring 25 is released, that is, the gear shaft 15 is rotated in the direction of unwinding. As a result, the pistons 37 of the hydraulic cylinder 23 are
The oil is pushed out toward the inside and outside, and the oil in the pressure chambers 41 and 41 flows out to the oil chamber 27 via the relief valve 22.

Here, the return oil port 6 of the relief valve 22
7 is provided with an orifice plate 66, so that the outflow speed of the oil is regulated, and therefore the pistons 37, 37
And the gear shaft 15 move slowly. When the gear shaft 15 rotates 90 °, the pistons 37, 3
7 comes into contact with the limiters 36, 36 of the head covers 32, 32 and stops. As a result, the ball valve 9 of the valve section 2 is closed, and the supply of gas is stopped. Oil chamber 2
The oil that has flowed out into the chamber 7 flows into the oil chamber 26 because the oil chambers 26 and 27 are in communication with each other, and is ready for the next valve opening operation. If a power failure or the like occurs during gas supply, the valve closing operation is naturally performed, and the gas supply is stopped.

Next, a second embodiment of the present invention will be described. The emergency shut-off valve of this embodiment is provided with two relief valves 22A and 22B in parallel as shown in the arrangement diagram of FIG. 10, and the other parts are the same as those of the first embodiment. is there. Hereinafter, the differences will be described.

First, regarding the relief valve 22A, the first
There is no difference from the relief valve 22 of the embodiment. On the other hand, the relief valve 22B is different in that the orifice plate 66 is not provided. That is, the relief valve 22A and the relief valve 22B have different oil outflow speeds when the power is turned off, and the relief valve 22B is faster.
In this emergency shutoff valve, the relief valves 22A, 22B
Are turned on and off independently of each other.

When the gas supply is stopped at the emergency shut-off valve, the electromagnetic pump 21, the relief valve 22A,
All of 22B are de-energized, and the valve unit 2 is closed to stop gas supply as in the case of the first embodiment. When supplying gas, the electromagnetic pump 2
1. When all energization of the relief valves 22A and 22B is turned on, the valve unit 2 is opened as in the case of the first embodiment, and when fully opened, only the electromagnetic pump 21 is energized off and maintains that state. , Gas is supplied.

When stopping the gas supply,
There are two types of stop methods, slow stop and quick stop. When performing the slow stop, the energization of the relief valve 22A is turned off, and the relief valve 22B is kept energized. Then, the oil flow path is opened in the relief valve 22A in the same manner as in the first embodiment, and the oil in the pressure chambers 41, 41 slowly flows out to the oil chamber 27 through the orifice plate 66. For this reason, the ball valve 9 of the valve section 2 moves slowly to be in the closed state, and the supply of gas is stopped. After the ball valve 9 is fully closed, the energization of the relief valve 22B is also turned off. The operation of turning off the relief valve 22B at this time may be automatically performed using a delay circuit.

To perform quick stop, both the relief valves 22A and 22B are turned off. Then, the oil flow path is opened by both the relief valves 22A and 22B. Here, since the relief valve 22B is not provided with the orifice plate 66, the outflow speed of the oil at the relief valve 22B is not regulated and is high. For this reason, the oil quickly flows out of the pressure chambers 41, 41 into the oil chamber 27, the valve section 2 is also quickly closed, and the supply of gas is stopped.

As described above, two types of stop methods, a slow stop and a quick stop, are possible. If a sudden change in the gas flow rate is disliked, the stop is performed by a slow stop, and in an emergency, the stop is performed by a quick stop. You can use them properly. Also,
When a power failure or the like occurs during gas supply, the gas supply is stopped by quick stop. The quick stop may be performed by first turning off only the relief valve 22B and turning off the relief valve 22A after the valve unit 2 is fully closed.

As described above in detail, in the emergency stop valve according to the present embodiment, since the inner end 25c of the mainspring 25 that drives the gear shaft 15 when the valve is closed is directly attached to the gear shaft 15, the valve portion 2 is opened. In this case, the amount of additional winding of the mainspring 25 is limited to 1/4 turn, and there is almost no contact between the base plates 25a of the mainspring 25, so that frictional damage of the coating film does not occur. In addition, since the guide plate 50 is provided at the lower end of the mainspring 25, damage of the coating film due to entry of foreign matter between the base plates 25a is also prevented. Further, since the low-friction thrust sheets 49, 49 are provided on the surface of the guide plate 50 on the side of the mainspring 25 and on the upper end of the mainspring 25, even if the base plate 25a slightly protrudes in the thrust direction, the coating film may be damaged by friction. There is no.

Further, since the mainspring spring 25 is assembled in a state of being wound from the free state, the valve 2
When the spring is changed from the open state to the closed state, the mainspring spring 25 generates a sufficient torque to rotate the gear shaft 15 against the flow resistance in the relief valve 22 to perform the valve closing operation.

A hydraulic cylinder 23 connected to the gear shaft 15 and a rack and pinion is provided.
The valve opening operation is performed by driving the hydraulic cylinder 23 with the hydraulic pressure that generates the pressure, so that the valve opening operation can be performed with a sufficient driving force against the reaction force of the mainspring 25. Also,
Since the relief valve 22 that releases the hydraulic pressure of the hydraulic cylinder 23 during the valve closing operation is provided to drain the oil from the hydraulic chambers 41, 41, the connection between the motor and the gear shaft as in the case of the motor drive is established. No special mechanism for shutting off is required. Further, when a power failure or the like occurs during gas supply, the valve portion 2 can be reliably closed by the energy stored in the mainspring 25.

The orifice plate 66 is connected to the relief valve 22.
Is provided to regulate the oil flow rate, so that the valve closing operation can be performed slowly so as not to cause a sudden change in the gas flow rate. Further, since the mainspring 25 also rewinds slowly, damage due to contact with the base plate 25a of the mainspring 25 due to inertial impact due to abrupt operation is prevented, and reliability is further improved. The speed can be changed by changing the hole diameter of the orifice plate 66. Further, since two relief valves 22 are provided and only one orifice plate 66 is attached, two types of valve closing speeds, slow stop and quick stop, can be selected as needed.

A micro switch 45 is provided to detect that the gear shaft 15 is rotated by 90 ° by the valve opening operation and to turn off the power supply to the electromagnetic pump 21. In the state, and the fully open state is maintained. Further, since the limiters 36, 36 are provided on the head covers 32, 32 of the hydraulic cylinder 23, the pistons 37, 37 abut against the limiters 36, 36 when the valve portion 2 is fully closed by the valve closing operation. The shaft 15 is stopped, and the fully closed state is maintained.

This embodiment does not limit the present invention in any way, and various modifications and improvements can be made without departing from the scope of the present invention. For example, in the embodiment, the electromagnetic pump 21 serving as a hydraulic pressure source and the oil chambers 26 and 27 for storing oil are provided inside.
These may be provided outside.

[0052]

As apparent from the above description, in the emergency shut-off valve of the present invention, the inner end of the mainspring is attached to the output shaft. There has been provided an emergency shut-off valve which is made smaller in size to prevent damage due to contact of a spring spring element plate to improve reliability and to make the whole spring coaxial with an output shaft to reduce the overall size.

Further, by employing a sufficiently powerful hydraulic device as a driving means for opening the valve on the output shaft, it is possible to make the amount of additional winding of the mainspring spring coincide with the rotation angle of the output shaft. A mechanism for preventing transmission of the force to the driving means is not required, and the structure is simplified. In addition, since the protection plate for covering the side end surface of the spring is provided, damage to the spring due to foreign matter entering the spring from the side end surface is prevented, and the reliability is greatly improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of an emergency stop valve according to the present invention in a closed state.

FIG. 2 is a sectional view of the emergency stop valve according to the present invention in an open state.

FIG. 3 is a side view of a mainspring.

FIG. 4 is a sectional view (valve closed state) illustrating a rack and pinion mechanism.

FIG. 5 is a plan view of the mainspring (in a closed state).

FIG. 6 is a cross-sectional view (in a valve-opened state) illustrating a rack and pinion mechanism.

FIG. 7 is a plan view of the mainspring (in a valve-open state).

FIG. 8 is a plan view of a thrust sheet.

FIG. 9 is a cross-sectional view illustrating a configuration of a relief valve.

FIG. 10 is a plan view illustrating an arrangement when two relief valves are provided.

FIG. 11 is a diagram illustrating a main part of a conventional emergency stop valve.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Emergency shut-off valve 9 Ball valve 10 Through-hole 15 Gear shaft 21 Electromagnetic pump 22 Relief valve 23 Hydraulic cylinder 25 Spring spring 25c Inner end 49 Thrust seat 50 Guide plate

Claims (4)

(57) [Claims] 1. A valve body for opening and closing a fluid flow path, an output shaft to which the valve body is attached, driving means for rotating the output shaft in a valve opening direction, and winding by rotating the output shaft in a valve opening direction. An emergency shut-off valve having an increased mainspring spring, wherein the output shaft supporting an inner end of the mainspring in a groove is opened.
By rotating in the valve direction, the spring
While matching the rotation angle of the inner end with the rotation angle of the output shaft,
Further, the mainspring spring is increased, and the
Energy stored by additional winding of the mainspring
And while matching the direction of the rotational torque for rotating the valve closing direction of the output shaft, as the drive torque for rotating the valve closing direction of the output shaft, emergency shutdown, characterized in that an acting directly on the output shaft valve. 2. A valve body for opening and closing a fluid flow path, an output shaft to which the valve body is attached, driving means for rotating the output shaft in a valve opening direction, and winding by rotating the output shaft in the valve opening direction. An emergency shutoff valve having an increased mainspring spring, comprising: a protective plate for covering a side end surface of the mainspring spring. 3. The emergency shut-off valve according to claim 2, wherein the output shaft supporting the inner end of the mainspring spring in a groove is opened.
By rotating in the valve direction, the spring
While matching the rotation angle of the inner end with the rotation angle of the output shaft,
Further, the mainspring spring is increased, and the
Energy stored by additional winding of the mainspring
And while matching the direction of the rotational torque for rotating the valve closing direction of the output shaft, as the drive torque for rotating the valve closing direction of the output shaft, emergency shutdown, characterized in that an acting directly on the output shaft valve. 4. The emergency shut-off valve according to claim 1, wherein the driving means is a hydraulic cylinder, and two relief valves for releasing hydraulic pressure applied to the hydraulic cylinder are provided in parallel. Or an emergency shut-off valve, characterized in that it comprises more than one.