WO2013150934A1

WO2013150934A1 - Gas control valve

Info

Publication number: WO2013150934A1
Application number: PCT/JP2013/058957
Authority: WO
Inventors: 里　宏一; 太一奥寺
Original assignee: 株式会社ミクニ
Priority date: 2012-04-06
Filing date: 2013-03-27
Publication date: 2013-10-10
Also published as: ES2825040T3; KR102061063B1; CN104220811A; CN104220811B; EP2835583B1; EP2835583A4; JP2013217539A; TWI601898B; KR20150004338A; TW201341695A; JP6016418B2; EP2835583A1

Abstract

The friction between a rotary disk (13) and a fixed disk (14) is prevented from being produced by providing a transmission interruption unit (a stopper (25) and a locking part (26)) for interrupting power transmission from a motor (28) to the rotary disk (13) in a safety valve operation range to stop the rotation of the rotary disk in the safety valve operation range. Moreover, an adhesion varying unit (a spring member (27) and a carriage ascent/descent cam) for varying the adhesion of the rotary disk (13) to the fixed disk (14) is further provided, and the adhesion of the rotary disk (13) to the fixed disk (14) is made lower in a flow rate adjustment range than in the safety valve operation range, thereby enabling the suppression of the friction produced between the rotary disk (13) and the fixed disk (14) in the flow rate adjustment range.

Description

Gas control valve

The present invention relates to a gas control valve that controls the amount of fuel gas supplied to a gas burner of a gas appliance.

Generally, a gas appliance such as a gas stove is provided with a flow rate adjusting valve for adjusting the gas supply flow rate and a safety valve for shutting off the gas supply in series.

Conventionally, a gas valve has been proposed in which the flow control valve and the safety valve are opened and closed with a single motor (see, for example, Patent Document 1). In the gas valve described in Patent Document 1, the flow rate adjustment valve includes a rotating body with a closing function that does not allow gas communication in a certain rotation angle range of the motor. The rotating body includes a rotating disk connected to a rotating shaft of a motor and a fixed disk having a plurality of communication holes with different sizes for adjusting the gas flow rate.

The rotation angle range of the motor that does not allow gas communication is the range from when the operating rod holding the safety valve starts to move backward. That is, in the gas valve of Patent Document 1, by rotating the motor, first, the operating rod is advanced in accordance with the rotation of the rotating disk to open the safety valve. Thereafter, the operation rod is moved backward by rotating the motor while the safety valve is kept open by the electromagnet. During this time, the position of the communication hole of the rotating disk and the position of the communication hole of the fixed disk are not matched to prevent gas from flowing through the flow rate control valve. When the motor is further rotated, the positions of the communication hole of the rotating disk and the communication hole of any size of the fixed disk coincide with each other, and the gas communication of the flow control valve is allowed.

Japanese Patent Laid-Open No. 2002-323218

In the gas valve described in Patent Document 1, the rotating disk is rotated in conjunction with the rotation of the motor, and both the safety valve and the flow control valve are operated in accordance with the rotation of the rotating disk. That is, the rotating disk is always rotating both when the safety valve is operated and when the flow rate adjusting valve is operated. Further, the rotating disk and the fixed disk are configured such that the disks are brought into close contact with each other by a coil spring so that gas does not leak downstream from the gap between the both disks. For this reason, there is a problem that during the operation of the safety valve and the flow control valve, rubbing always occurs between the rotating disk and the fixed disk, and the reliability of the closing surface is deteriorated due to wear.

The present invention has been made to solve such a problem, and an object thereof is to reduce friction generated between a rotating disk and a fixed disk and to suppress wear of a closing surface. .

In order to solve the above-described problems, in the present invention, the flow control valve and the safety valve are opened and closed by a single motor, and a closing function for preventing gas communication with the flow control valve in the safety valve operation range. In the gas control valve provided with a rotating disk and a fixed disk as an attached rotating body, a transmission blocking portion for blocking power transmission from the motor to the rotating disk in the safety valve operation range is provided.

In another aspect of the present invention, an adhesion force variable portion for making the adhesion force of the rotating disk to the fixed disk variable is further provided so that the adhesion force differs between the safety valve operation range and the flow rate adjustment range.

According to the present invention configured as described above, since the rotation of the rotating disk is stopped in the safety valve operation range, the friction between the rotating disk and the fixed disk does not occur, and between the two disks. Wear of the closing surface can be prevented.

Further, according to another aspect of the present invention, the adhesion of the rotating disk to the fixed disk can be weakened in the flow rate adjustment range compared to the safety valve operation range. When operating the safety valve, it is necessary to increase the contact force on the closing surface so that gas does not leak downstream from the gap between the rotating disk and the fixed disk. However, since the rotating disk is stopped at this time, even if the adhesion force is increased, the disk is not rubbed and wear of the closing surface can be prevented. On the other hand, when the flow control valve is operated, the gas is supplied, so that the adhesion between the rotating disk and the fixed disk can be somewhat weakened. Since the adhesive force is weak, even when the rotating disk rotates, the friction generated between the rotating disk and the fixed disk can be reduced, and the wear of the closing surface between both disks can be suppressed.

It is a schematic diagram which shows the principal part structure of the gas control valve by this embodiment. It is sectional drawing of the gas control valve by this embodiment. FIG. 3 is an AA cross-sectional view of the gas control valve shown in FIG. 2. It is a figure which shows the structural example of the distance variable part with which the gas control valve of this embodiment is provided. It is a figure which shows the operation state of the distance variable part by this embodiment. It is a timing chart which shows the operation example of the gas control valve by this embodiment. FIG. 7 is a diagram showing a state of a gas control valve at each timing indicated by I) to V) in the timing chart of FIG. FIG. 7 is a diagram showing a state of a gas control valve at each timing indicated by I) to III) and * 1 in the timing chart of FIG. It is a figure which shows the state of the gas control valve in each timing shown by I) IV) V) and * 2, * 3 in the timing chart of FIG. It is a figure which shows the state of the gas control valve in each timing shown by I) II) in the timing chart of FIG.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram showing a main configuration of a gas control valve 1 according to the present embodiment. The gas control valve 1 of this embodiment is applied to a gas appliance such as a gas stove, and includes a flow rate adjusting valve 11 for adjusting a gas supply flow rate and a safety valve 12 for cutting off the gas supply. I have.

The gas control valve 1 of the present embodiment is configured so that the flow control valve 11 and the safety valve 12 are opened and closed by a single motor 28. The flow rate adjusting valve 11 includes a rotating body with a closing function that does not allow gas communication in a safety valve operation range in which the motor 28 operates the safety valve 12. The rotating body with a closing function includes a rotating disk 13 that rotates in conjunction with the rotation of the motor 28 and a fixed disk 14 that is provided so as to face the rotating disk 13.

The safety valve 12 includes a magnet case 16. The magnet case 16 accommodates an electromagnet that is excited based on a signal from the control circuit 29 and an attracting piece that is attracted to the electromagnet. A valve element 17 protruding downstream from the magnet case 16 is connected to the attracting piece. When the safety valve 12 is closed, the valve body 17 blocks the gas flow path while being urged downstream by a return spring (not shown).

The opening operation of the safety valve 12 is performed by an operation rod 18 movable in the front-rear direction of the gas flow path (left-right direction in FIG. 1). The operating rod 18 is moved upstream by the link member 20 that rotates in conjunction with the motor 28, and pushes the valve body 17 to open the gas flow path. That is, the safety valve 12 is opened.

The link member 20 operates the safety valve 12 by advancing and retracting the operation rod 18 urged downstream by a spring 19 in the front-rear direction of the gas flow path. That is, when the motor 28 rotates, the link member 20 also rotates in conjunction with it, and the operating rod 18 is advanced to the upstream side by a link lever portion (not shown) protruding to the operating rod 18 side to open the safety valve 12. To do. Thereafter, the electromagnet in the magnet case 16 is excited by a signal from the control circuit 29, and the operating rod 18 is moved backward by rotating the motor 28 in the reverse direction while keeping the safety valve 12 open.

Thus, the rotation angle range of the motor 28 from the time when the operating rod 18 starts moving forward to the time when the operating rod 18 moves back to the original position becomes the safety valve operating range. When the excitation of the electromagnet is released by a signal from the control circuit 29, the valve element 17 receives the force of the return spring and moves downstream, and the safety valve 12 returns to the closed state.

The fixed disk 14 is provided with a fixed communication hole 15 having a certain opening area. On the other hand, the rotary disk 13 is provided with a rotation side communication hole (not shown) whose opening area is gradually changed along the circumferential direction. When the rotary disk 13 rotates and the position of the rotation side communication hole coincides with the position of the fixed side communication hole 15, the gas supplied from the upstream side (the right side in FIG. 1) of the safety valve 12 is supplied to the rotation side communication hole and the fixed side. It flows to the gas burner side (upper side in FIG. 1) (not shown) through the side communication hole 15. Thus, the rotation angle range of the motor 28 when the gas communication is allowed between the rotary disk 13 and the fixed disk 14 becomes the flow rate adjustment range.

Further, the gas control valve 1 of the present embodiment includes a carriage member 21 between the link member 20 and the rotary disk 13 that rotates in conjunction with the link member 20 and transmits power from the motor 28 to the rotary disk 13. ing. The carriage member 21 includes a power transmission shaft 22 on the surface on the rotating disk 13 side. On the other hand, the rotary disk 13 includes a power transmission bearing 23 on the surface on the carriage member 21 side. A part of the front end side of the power transmission shaft 22 is fitted into the power transmission bearing 23, and the power transmission shaft 22 is configured to be movable in the vertical direction inside the power transmission bearing 23.

Further, the gas control valve 1 of the present embodiment includes a transmission cutoff unit for cutting off power transmission from the motor 28 to the rotary disk 13 in the safety valve operation range. The transmission blocking portion includes, for example, a stopper 25 provided on the case 24 of the gas control valve 1 and a locking portion 26 provided on the carriage member 21 and engaged with the stopper 25 to stop the rotation of the carriage member 21. It is configured.

By providing this transmission cut-off section, the carriage member 21 stops rotating in the safety valve operation range, and the safety valve 12 is operated by the link member 20 rotating independently from the carriage member 21. On the other hand, in the flow rate adjustment range that is the range of the rotation angle at which the motor 28 operates the flow rate adjustment valve 11, the carriage member 21 rotates in conjunction with the link member 20 and transmits the power of the motor 28 to the rotary disk 13.

In addition, the gas control valve 1 of the present embodiment further includes an adhesion force variable portion for making the adhesion force of the rotating disk 13 to the fixed disk 14 variable, and the adhesion force in the safety valve operation range and the adhesion force in the flow rate adjustment range. Are different. Preferably, the contact force is maximized in the safety valve operation range, and the contact force is minimized in the flow rate adjustment range.

For example, the contact force varying portion includes a spring member 27 provided between the carriage member 21 and the rotating disk 13, and a distance varying portion for varying the distance between the carriage member 21 and the rotating disk 13. It is configured with. That is, when the distance between the carriage member 21 and the rotary disk 13 is reduced by the distance variable portion, the spring member 27 is reduced and the urging force against the rotary disk 13 is increased. Thereby, the contact | adhesion power with respect to the fixed disk 14 of the rotating disk 13 becomes large.

On the other hand, when the distance between the carriage member 21 and the rotary disk 13 is widened by the distance variable portion, the spring member 27 is extended, and the urging force against the rotary disk 13 is reduced. Thereby, the contact | adhesion force with respect to the fixed disk 14 of the rotating disk 13 becomes small. A detailed configuration example of the distance variable unit will be described later.

2 to 5 are diagrams showing a specific configuration example of the gas control valve 1 according to the present embodiment. FIG. 2 is a sectional view of the gas control valve 1 according to the present embodiment. FIG. 3 is a cross-sectional view taken along line AA of the gas control valve 1 shown in FIG. FIG. 4 is a diagram illustrating a configuration example of a distance variable unit provided in the gas control valve 1 of the present embodiment. FIG. 5 is a diagram illustrating an operation state of the distance variable unit. 2 to 5, components having the same functions as those shown in FIG. 1 are given the same reference numerals.

2 and 3, the link member 20 is connected to the motor rotation shaft 31 and is rotated in conjunction with the rotation of the motor 28. The carriage member 21 is connected to the link member 20 and rotates in conjunction with the rotation of the motor 28 via the link member 20. The link member 20 and the carriage member 21 are provided with a carriage raising / lowering cam 32 as a distance variable portion. The carriage raising / lowering cam 32 also has a function of connecting the link member 20 and the carriage member 21.

As shown in FIGS. 4 and 5, the carriage raising / lowering cam 32 includes a link cam portion 32 a provided on one surface of the link member 20 (surface facing the carriage member 21), and one surface of the carriage member 21 (on the link member 20. And a carriage cam portion 32b provided on the opposing surface.

The link cam portion 32a is constituted by two concave portions formed along the circumferential direction of the link member 20. One end side of the recess is formed by a substantially vertical surface, and the other end side is formed by an inclined surface (tapered surface) having a predetermined angle. The carriage cam portion 32b is constituted by two convex portions formed along the circumferential direction of the carriage member 21, and one end side of the convex portion is formed by a substantially vertical surface, and the other end side has a predetermined angle. It is formed by a slope (tapered surface).

The concave portion of the link cam portion 32a and the convex portion of the carriage cam portion 32b are configured to have substantially the same size, and the tapered surface has substantially the same inclination. For this reason, as shown in FIG. 5A, the link cam portion 32a and the carriage cam portion 32b are just fitted together, whereby the link member 20 and the carriage member 21 rotate in conjunction with each other. That is, when the locking portion 26 of the carriage member 21 does not engage with the stopper 25 of the case 24 and the link member 20 and the carriage member 21 rotate in conjunction with each other, the link cam portion 32a and the carriage cam portion 32b are The carriage member 21 is in the lowered state as shown in FIG.

Further, the tapered surface of the link cam portion 32a and the tapered surface of the carriage cam portion 32b are formed to face each other. Therefore, when a certain force or more acts in the opposite directions along the tapered surface, the carriage cam portion 32b slides along the tapered surface as shown in FIG. 5B, and the carriage cam portion 32b becomes the link member. It rides on the flat part in which the 20 link cam parts 32a are not formed. As a result, the carriage member 21 is raised. At this time, the spring member 27 is in a contracted state as compared with the lowered state of FIG.

That is, in this embodiment, when the locking portion 26 of the carriage member 21 is engaged with the stopper 25 of the case 24, the link member is used when the rotation of the carriage member 21 is stopped even if the motor 28 is rotating. 20 can be rotated independently of the carriage member 21 independently. At this time, the carriage raising / lowering cam 32 is disengaged and the carriage cam portion 32 b rides on the flat portion of the link member 20, so that the carriage member 21 is raised.

As shown in FIGS. 2 and 3, in this embodiment, the motor rotation shaft 31 that is the rotation center of the link member 20 and the carriage member 21 is a rod moving shaft 33 in which the operation rod 18 moves in the front-rear direction of the gas flow path. The motor rotating shaft 31 is set at a position offset from the rod moving shaft 33. The link member 20 connected to the motor rotating shaft 31 includes a link lever portion 20a that protrudes toward the rod moving shaft 33. When the link member 20 rotates in conjunction with the motor 28, the link lever portion 20a pushes the slider 34, and the operation rod 18 connected to the slider 34 moves forward and backward in the gas flow path. ing.

As described above, the valve element 17 of the safety valve 12 is provided at the tip (upstream side) of the operation rod 18, and the gas flow path is opened when the moved operation rod 18 pushes the valve element 17. To. An electromagnet 35 for holding the safety valve 12 in an open state is provided further ahead of the valve body 17.

Next, the operation of the gas control valve 1 according to this embodiment configured as described above will be described. 6 to 10 are diagrams showing an operation example of the gas control valve 1 according to the present embodiment. Among these, FIG. 6 is a timing chart. FIGS. 7 to 10 are diagrams showing the state of the gas control valve 1 at each timing indicated by I) to V) and * 1 to * 3 in the timing chart of FIG.

First, as shown in FIG. 6E, the motor 28 is reversely rotated at the timing I) (CCW). Immediately after the rotation of the motor 28, the link lever portion 20a is not in contact with the slider 34 (see I in FIG. 8), and the operating rod 18 has not moved upstream as shown in FIG. 6D. Therefore, as shown in FIG.6 (c), the valve body 17 of the safety valve 12 is a valve closing state (refer I of FIG. 8).

At timing I), the link cam portion 32a and the carriage cam portion 32b are fitted (see I in FIG. 7 and I) in FIG. 10), and the carriage lifting cam as shown in FIG. 6B. 32 is in a descending state. Further, as shown in FIG. 9I), the position of the fixed side communication hole 15 provided in the fixed disk 14 and the position of the rotation side communication hole 41 provided in the rotary disk 13 do not coincide at all. For this reason, as shown to Fig.6 (a), the flow control valve 11 is a closed state completely.

Thereafter, when the motor 28 continues to reverse, the locking portion 26 of the carriage member 21 comes into contact with the stopper 25 of the case 24 and locks, thereby stopping the rotation of the carriage member 21. When the motor 28 continues to reverse in this state, the link member 20 continues to rotate independently of the carriage member 21 in the stopped state. At this time, as shown in the front part of * 2 in FIG. 6B, the carriage cam portion 32b slides along the tapered surface and rides on the flat portion of the link member 20, so that the carriage raising / lowering cam 32 is lifted. (See FIG. 7 II) and FIG. 10 II)).

When the carriage raising / lowering cam 32 is in the raised state, the spring member 27 provided between the carriage member 21 and the rotary disk 13 is in a contracted state. That is, as shown in I) and II) of FIG. 10, compared to the length d1 of the spring member 27 when the carriage lifting cam 32 is in the lowered state, the spring member when the carriage lifting cam 32 is in the raised state. The length d2 of 27 is shortened. Therefore, the rotating disk 13 receives a strong force from the spring member 27. As a result, the adhesion force of the rotary disk 13 to the fixed disk 14 is stronger than when the carriage elevating cam 32 is in the lowered state.

In addition, when the link member 20 is independently rotated independently of the carriage member 21, the link lever portion 20a pushes the slider 34 by the rotation of the link member 20, whereby the * 1 in FIG. As shown in the front part, the operating rod 18 moves upstream. As a result, as shown in FIG.6 (c), the safety valve 12 changes to a valve open state (refer II of FIG. 8). In this state, the safety valve 12 is held open by exciting the electromagnet 35 with a signal from the control circuit 29.

Next, while the safety valve 12 is held open by the force of the electromagnet 35, the rotation of the motor 28 is switched to the forward rotation (CW) at the timing II) shown in FIG. As a result, as shown in the rear part of * 1 in FIG. Further, as shown in the rear part of * 2 in FIG. 6B, the carriage cam portion 32b slides in the opposite direction along the tapered surface. As a result, the link cam portion 32a and the carriage cam portion 32b are fitted, and the carriage elevating cam 32 is lowered (see III in FIG. 7 and I) in FIG. 10).

In the operation so far, the rotation angle range of the motor 28 from the time when the operating rod 18 advances upstream to the original position is the safety valve operating range indicated by * 1 in FIGS. 6 and 8. It becomes. Also, the carriage member 21 stops rotating until the carriage cam portion 32b starts to rise along the taper surface and then descends along the taper surface and then comes down again, and the link member 20 stops. In this state, only the motor 28 is rotated, and the power of the motor 28 is not transmitted to the rotary disk 13 via the carriage member 21. This rotation angle range is a power non-transmission range indicated by * 2 in FIGS.

After the power non-transmission range is passed, the motor 28 continues forward rotation (CW). Then, as shown in IV) of FIG. 7 and IV) of FIG. 9, a part of the fixed side communication hole 15 provided in the fixed disk 14 and a part of the rotation side communication hole 41 provided in the rotary disk 13. And the positions match. For this reason, as shown to Fig.6 (a), the flow control valve 11 changes to the state which accept | permits gas communication with the minimum flow volume (refer IV of FIG. 7). When the motor 28 continues to rotate forward, the area where the fixed side communication hole 15 and the rotation side communication hole 41 communicate with each other increases, and the gas flow rate increases accordingly. Timing V) shown in each of FIG. 6, FIG. 7, and FIG. 9 shows a state in which the gas flow allowed by the communication is maximized.

Thus, the rotation of the motor 28 while the position of the fixed side communication hole 15 and the position of the rotation side communication hole 41 coincide with each other and gas communication is permitted (from the minimum gas flow to the maximum gas flow rate). The angle range is the flow rate adjustment range indicated by * 3 in FIGS. As apparent from FIG. 6, the flow rate adjustment range of * 3 is considerably larger than the safety valve operation range of * 1.

As described above in detail, in the present embodiment, in the gas control valve 1 including the rotating disk 13 and the fixed disk 14 as a rotating body with a closing function that does not allow gas communication with the flow rate control valve 11 in the safety valve operation range. In addition, a transmission blocking portion (stopper 25 and locking portion 26) for blocking power transmission from the motor 28 to the rotating disk 13 in the safety valve operation range is provided.

By providing such a transmission cut-off portion, the rotation of the rotating disk 13 is stopped in the safety valve operation range, so that no rubbing occurs between the rotating disk 13 and the fixed disk 14, and both disks It is possible to prevent the wear of the closing surface in between.

Further, in the present embodiment, an adhesion force variable portion (spring member 27 and carriage raising / lowering cam 32) for making the adhesion force of the rotating disk 13 to the fixed disk 14 variable is provided. In the safety valve operation range, the contact force is maximized by retracting the spring member 27 by moving the carriage lifting cam 32 upward. On the other hand, in the flow rate adjustment range, the adhesion force is minimized by extending the spring member 27 with the carriage elevating cam 32 in the lowered state.

When operating the safety valve 12, it is necessary to increase the close contact force on the closing surface so that gas does not leak downstream from the gap between the rotating disk 13 and the fixed disk 14 as a precaution. In this embodiment, since the rotating disk 13 is stopped in this safety valve operation range, even if the adhesion force is increased, the disk is not rubbed, and wear of the closing surface can be prevented.

On the other hand, in the flow rate control range in which the flow rate control valve 11 is operated, since the gas is actually supplied, the adhesion between the rotating disk 13 and the fixed disk 14 can be somewhat weakened. Since the adhesive force is weak, even if the rotating disk 13 rotates, the friction generated between the rotating disk 13 and the fixed disk 14 can be reduced, and the wear of the closing surface between the both disks can be suppressed.

In the above embodiment, as shown in FIG. 6, the power non-transmission range is set to be larger than the safety valve operation range, but the present invention is not limited to this. For example, the safety valve operation range and the power non-transmission range may be set to have the same size.

In the above embodiment, the configuration including both the transmission blocking portion and the adhesion varying portion has been described, but the present invention is not limited to this. For example, it may be configured to include only the transmission blocking unit, and the adhesion force of the rotating disk 13 to the fixed disk 14 may be the same as that when the carriage lifting cam 32 is in the raised state. In this case, at least in the safety valve operation range, rubbing that occurs between the disk 13 and the fixed disk 14 can be suppressed.

In the above embodiment, the motor rotating shaft 31 and the rod moving shaft 33 are set at offset positions, and the motor 28 is rotated in two directions of normal rotation and reverse rotation. However, the present invention is limited to this. Not. In other words, if the configuration includes the transmission blocking portion and the adhesion force varying portion, the motor rotation shaft 31 and the rod moving shaft 33 do not necessarily need to be set at offset positions, and the motor 28 is also operated by rotation in one direction. It may be.

In addition, each of the above-described embodiments is merely an example of implementation in carrying out the present invention, and the technical scope of the present invention should not be construed in a limited manner. That is, the present invention can be implemented in various forms without departing from the gist or the main features thereof.

Claims

A gas control valve configured to open and close a flow rate adjusting valve for adjusting a gas supply flow rate and a safety valve for shutting off the gas supply by a single motor,
The flow rate adjusting valve includes a rotating body with a closing function for preventing gas communication in a safety valve operation range that is a range of a rotation angle at which the motor operates the safety valve, and the rotating body with a closing function is It consists of a rotating disk that rotates in conjunction with the rotation of the motor, and a fixed disk that is provided so as to face the rotating disk.
A gas control valve comprising: a transmission cut-off portion for cutting off power transmission from the motor to the rotating disk in the safety valve operation range.
The apparatus further comprises a contact force variable portion for making the contact force of the rotating disk with respect to the fixed disk variable, the contact force in the safety valve operation range, and a flow rate that is a range of a rotation angle at which the motor operates the flow rate control valve. 2. The gas control valve according to claim 1, wherein the adhesion force in the adjustment range is made different.
3. The gas control valve according to claim 2, wherein the contact force is maximized in the safety valve operation range, and the contact force is minimized in the flow rate adjustment range.
It rotates in conjunction with the link member between the link member designed to operate the safety valve by rotating in conjunction with the motor and advancing and retracting the operating rod, and the power from the motor. A carriage member for transmitting to the rotating disk;
The adhesive force varying portion includes a spring member provided between the carriage member and the rotating disk, and a distance varying portion for varying the distance between the carriage member and the rotating disk. The gas control valve according to claim 2 or 3, wherein the gas control valve is formed.
It rotates in conjunction with the link member between the link member designed to operate the safety valve by rotating in conjunction with the motor and advancing and retracting the operating rod, and the power from the motor. A carriage member for transmitting to the rotating disk;
The transmission cut-off portion is configured by a stopper provided in the case of the gas control valve and a locking portion provided in the carriage member, and the locking portion engages with the stopper to engage the carriage member. The gas control valve according to claim 1, wherein the gas control valve is configured to stop rotation.
The adhesive force varying portion includes a spring member provided between the carriage member and the rotating disk, and a distance varying portion for varying the distance between the carriage member and the rotating disk. The gas control valve according to claim 5, wherein the gas control valve is formed.
The distance variable portion is configured by a carriage lifting cam provided on the link member and the carriage member,
The carriage elevating cam is in a raised state when the rotation of the carriage member is stopped due to the engagement of the locking portion with the stopper, and when the locking portion is not engaged with the stopper. The gas control valve according to claim 6, wherein the gas control valve is in a descending state.
The carriage lifting cam is composed of a link cam portion provided on the link member and a carriage cam portion provided on the carriage member,
When the carriage elevating cam is in the lowered state, the link cam portion and the carriage cam portion engage with each other, so that the carriage member can rotate in conjunction with the link member. The link cam portion and the carriage cam portion are disengaged when the link member is in the raised state, whereby the link member can be rotated independently of the carriage member. The gas control valve described.