TWI601898B - Gas control valve - Google Patents

Description

Gas control valve

The present invention relates to a gas control valve for controlling the amount of gas supplied to a gas burner of a gas appliance.

In general, a gas flow control device such as a gas furnace is provided with a flow regulating valve for regulating the gas supply flow rate and a safety valve for shutting off the supply of the gas.

In the prior art, a gas valve that performs opening and closing operations of a flow rate adjusting valve and a safety valve using one electric motor has been proposed (for example, refer to Patent Document 1). In the gas valve described in Patent Document 1, the flow rate adjusting valve is provided with a rotating body having a sealing function, which means a function of not allowing gas to flow in a predetermined range of rotation angle of the motor. The rotating body includes a rotating disk and a fixed disk, wherein the rotating disk is coupled to a rotating shaft of the motor, and the fixed disk is provided with a plurality of communicating holes of different sizes for adjusting the flow rate of the gas.

The range of the motor rotation angle that does not allow the gas to flow is to maintain the range in which the operating lever of the safety valve starts to advance to retreat. In other words, in the gas valve of Patent Document 1, by rotating the motor, the operating lever is first advanced as the rotating disk rotates to open the safety valve. Then, in use When the electromagnet keeps the safety valve in an open state, the motor is further rotated, thereby causing the operating lever to retreat. During this period, the position of the communication hole of the rotary disk is made to be inconsistent with the position of the communication hole of the fixed disk, so that the gas does not flow out through the flow regulating valve. Then, when the motor is further rotated, the communication hole of the rotary disk coincides with the position of the communication hole of any size of the fixed disk, thereby allowing the gas to pass through the flow regulating valve.

[Previous Technical Literature] [Patent Literature]

Patent Document 1: Japanese Gazette, JP-A-2002-323218

The gas valve described in Patent Document 1 is configured to rotate the rotary disk in conjunction with the rotation of the motor, and operate the two valves of the safety valve and the flow rate adjusting valve in accordance with the rotation of the rotary disk. That is to say, the rotary disk is always rotated when the safety valve is operated or when the flow regulating valve is operated. Further, the rotating disk and the fixed disk are configured such that the discs are tightly coupled to each other with a sealing surface by the coil spring so that the gas does not leak downstream from the gap between the two disks. Therefore, during the operation of the safety valve and the flow regulating valve, friction is always generated between the rotating disk and the fixed disk, so that the reliability of the sealing surface is lowered due to wear.

The present invention has been made to solve the above problems, The friction between the rotating disk and the fixed disk is reduced, so that the wear of the sealing surface can be suppressed.

In order to solve the above problems, in the present invention, in a gas control valve in which a rotating disc and a fixed disc are provided as a rotating body having a sealing function, a flow rate adjusting valve and a safety valve are opened and closed by one electric motor. Provided with a transmission cut-off portion for shutting off power transmission from the electric motor to the rotary disk within the operating range of the safety valve, wherein the sealing function refers to a function of not allowing gas to pass from the flow regulating valve within the operating range of the safety valve .

In another aspect of the present invention, a coupling force variable portion for varying the coupling force of the rotating disk to the fixed disk is provided, so that the bonding force is different within the safety valve operating range and the flow rate adjustment range.

According to the invention constructed as described above, since the rotation of the rotary disk is stopped within the operating range of the safety valve, friction is not generated between the rotary disk and the fixed disk, so that the wear of the sealing faces of the two disks can be prevented. .

Further, according to another aspect of the present invention, it is possible to weaken the coupling force of the rotary disk to the fixed disk within the flow rate adjustment range as compared with the safety valve operation range. When operating the safety valve, it is necessary to increase the bonding force of the sealing surface in order to prevent the gas from leaking from the gap between the rotating disk and the fixed disk toward the downstream. However, since the rotating disk is stopped at this time, even if the bonding force is enhanced, the disk does not generate friction, thereby preventing the sealing. The wear of the face. On the other hand, when the flow regulating valve is operated, since the gas is being supplied, the coupling force between the rotating disk and the fixed disk can be slightly weakened. Since the bonding force is small, even if the rotary disk rotates, the friction generated between the rotary disk and the fixed disk is small, so that the wear of the sealing faces of the two disks can be suppressed.

1‧‧‧ gas control valve

11‧‧‧Flow regulating valve

12‧‧‧Safety valve

13‧‧‧ rotating disk

14‧‧‧ Fixed disk

20‧‧‧Connected parts

21‧‧‧Rack components

25‧‧ ‧block

26‧‧‧Kangding Department

27‧‧‧Spring parts

28‧‧‧Electric motor

32‧‧‧Rack lifting cam

32a‧‧‧Connecting cam

32b‧‧‧Elevator cam

Fig. 1 is a schematic view showing the configuration of a main part of a gas control valve of the present embodiment.

Fig. 2 is a cross-sectional view showing the gas control valve of the embodiment.

Figure 3 is a cross-sectional view of the gas control valve of Figure 2 taken along the line A-A.

FIG. 4 is a view showing a configuration example of a distance variable portion included in the gas control valve of the present embodiment.

Fig. 5 is a view showing an operation state of the distance varying unit of the embodiment.

Fig. 6 is a timing chart showing an operation example of the gas control valve of the present embodiment.

Fig. 7 is a view showing the state of the gas control valve at each time shown by I) to V) in the timing chart of Fig. 6.

Fig. 8 is a view showing the state of the gas control valve at each time shown by I) to III) and *1 in the time chart of Fig. 6.

Fig. 9 is a view showing the state of the gas control valve at each time shown by I), IV), V), and *2, *3 in the time chart of Fig. 6.

Fig. 10 is a view showing the state of the gas control valve at each time shown by I) and II) in the timing chart of Fig. 6.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a schematic view showing the configuration of a main part of a gas control valve 1 of the present embodiment. The gas control valve 1 of the present embodiment is applied to a control valve of a gas appliance such as a gas furnace, and is provided with a flow rate adjusting valve 11 for adjusting a supply flow rate of the gas and a safety for shutting off the supply of the gas. Valve 12.

The gas control valve 1 of the present embodiment is formed such that the flow rate adjustment valve 11 and the relief valve 12 are opened and closed by one motor 28. The flow regulating valve 11 is provided with a rotating body with a sealing function, wherein the sealing function refers to a function of not allowing gas to flow through the operating range of the safety valve, and the operating range of the safety valve means that the electric motor 28 is operating the safety valve 12. The range of angles of rotation. The rotating body with a sealing function includes a rotating disk 13 and a fixed disk 14, wherein the rotating disk 13 rotates in conjunction with the rotation of the motor 28, and the fixed disk 14 is disposed to face the rotating disk 13.

The safety valve 12 is provided with a magnet case 16. The magnet case 16 houses an electromagnet that is excited by a signal from the control circuit 29 and an adsorption piece that is adsorbed on the electromagnet. A valve body 17 projecting from the magnet case 16 toward the downstream side is connected to the adsorption sheet. When the safety valve 12 is in the closed state, the valve body 17 cuts the gas passage in a state of being biased toward the downstream side by a return spring (not shown).

The opening operation of the relief valve 12 is performed by the operation lever 18 that is movable toward the front-rear direction of the gas passage (the horizontal direction in FIG. 1). The connecting member 20 that rotates in conjunction with the motor 28 moves the operating lever 18 toward the upstream side to press the valve body 17 to open the gas passage. That is, the safety valve 12 is brought to an open state.

The connecting member 20 moves the safety valve 12 by advancing or retracting the operating lever 18 biased toward the downstream side by the spring 19 toward the front-rear direction of the gas passage. In other words, when the motor 28 rotates, the connecting member 20 rotates in conjunction with the rotation of the motor 28, and the operating lever 18 is advanced toward the upstream side by a link portion (not shown) that protrudes toward the operating lever 18 side. The safety valve 12 is opened. Then, when the electromagnet in the magnet case 16 is excited by the signal from the control circuit 29 to hold the safety valve 12 in the open state, the motor 28 is rotated in the reverse direction, whereby the operating lever 18 is retracted.

The range of the rotation angle of the motor 28 during the period from the start of the operation of the lever 18 to the return to the original position is the safety valve operation range. Further, when the electromagnet is stopped from being excited by the signal from the control circuit 29, the valve body 17 is moved toward the downstream side by the force of the return spring, thereby returning the safety valve 12 to the closed state.

The fixed disk 14 is provided with a fixed side communication hole 15 having a fixed aperture area. On the other hand, the rotary disk 13 is provided with a rotation side communication hole (not shown) whose aperture area is gradually changed in the circumferential direction. When the rotary disk 13 is rotated, the position of the rotating side communication hole is communicated with the fixed side When the positions of the holes 15 match, the gas supplied from the upstream side (the right side in FIG. 1) of the relief valve 12 flows to the gas burner side (not shown) via the rotation side communication hole and the fixed side communication hole 15 (upper side of Figure 1). The range of the rotation angle of the motor 28 when the gas is allowed to flow between the rotary disk 13 and the fixed disk 14 is the flow rate adjustment range.

Further, in the gas control valve 1 of the present embodiment, a carriage member 21 is provided between the coupling member 20 and the rotary disk 13, and the gantry member 21 is rotated in conjunction with the coupling member 20, thereby Power from the motor 28 is transmitted to the rotating disk 13. A power transmission shaft 22 is provided on a surface of the gantry member 21 on the side of the rotary disk 13. On the other hand, a power transmission bearing 23 is provided on the surface of the rotary disk 13 on the side of the gantry member 21. Further, a part of the front end side of the power transmission shaft 22 is inserted into the power transmission bearing 23, and the power transmission shaft 22 is movable in the vertical direction inside the power transmission bearing 23.

Further, the gas control valve 1 of the present embodiment is provided with a transmission cut-off portion for shutting off power transmission from the motor 28 to the rotary disk 13 within the safety valve operation range. The transmission cutting portion includes, for example, a stopper 25 and a locking portion 26, wherein the stopper 25 is disposed on the casing 24 of the gas control valve 1, and the locking portion 26 is disposed on the gantry member 21 by The stopper 25 is engaged to stop the rotation of the gantry member 21.

By providing the transmission cutting portion, the gantry member 21 stops rotating in the safety valve operation range, and the coupling member 20 is separately rotated from the gantry member 21 to individually rotate the safety valve 12. On the other hand, in the flow adjustment range, the gantry member 21 and the coupling member 20 The rotation of the motor 28 is transmitted in conjunction with the rotation of the motor 28, wherein the flow rate adjustment range is a range of rotation angles when the motor 28 operates the flow rate adjustment valve 11.

Further, the gas control valve 1 of the present embodiment is further provided with a coupling force variable portion for allowing the coupling force of the rotary disk 13 to the fixed disk 14 to be varied, so that the bonding force within the operating range of the safety valve and the flow rate adjustment range are The binding force is different. Preferably, the bonding force is maximized within the operating range of the safety valve, and the bonding force is minimized within the flow adjustment range.

The coupling force variable portion is configured, for example, to be provided with a spring member 27 and a distance variable portion, wherein the spring member 27 is provided between the gantry member 21 and the rotary disk 13, and the distance variable portion is for the gantry member 21 and The distance between the rotating disks 13 can be varied. That is, when the distance between the gantry member 21 and the rotary disk 13 is shortened by the distance variable portion, the spring member 27 contracts, and the urging force applied to the rotary disk 13 becomes large. Thereby, the coupling force of the rotary disk 13 to the fixed disk 14 becomes large.

On the other hand, when the distance between the stage member 21 and the rotary disk 13 is increased by the distance variable portion, the spring member 27 is stretched, so that the force applied to the rotary disk 13 becomes small. Thereby, the coupling force of the rotary disk 13 to the fixed disk 14 becomes small. In addition, a detailed configuration example of the distance variable unit will be described later.

2 to 5 are views showing a specific configuration example of the gas control valve 1 of the present embodiment. Fig. 2 is a cross-sectional view showing the gas control valve 1 of the present embodiment. Figure 3 is a cross-sectional view taken along line A-A of the gas control valve 1 shown in Figure 2 . 4 is a view showing that the gas control valve 1 of the present embodiment has a variable distance A diagram of a structural example of the department. Fig. 5 is a view showing an operation state of the variable distance portion. In addition, in FIGS. 2 to 5, structural elements having the same functions as those of the structural elements shown in FIG. 1 are denoted by the same reference numerals.

As shown in FIGS. 2 and 3, the connecting member 20 is connected to the motor rotating shaft 31, and is rotated in conjunction with the rotation of the motor 28. The gantry member 21 is connected to the coupling member 20 and is rotated in conjunction with the rotation of the motor 28 via the coupling member 20 . A gantry lifting cam 32 as a distance variable portion is provided on the coupling member 20 and the gantry member 21. The gantry lifting cam 32 also has a function of connecting the connecting member 20 to the gantry member 21.

As shown in FIGS. 4 and 5, the gantry lifting cam 32 includes a connecting cam portion 32a and a gantry cam portion 32b, wherein the connecting cam portion 32a is provided on one surface of the connecting member 20 (the surface facing the gantry member 21) The gantry cam portion 32b is provided on one surface (the surface facing the coupling member 20) of the gantry member 21.

The connection cam portion 32a is composed of two recessed portions formed along the circumferential direction of the coupling member 20, and one end side of the recessed portion 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 gantry cam portion 32b is composed of two convex portions formed along the circumferential direction of the gantry member 21. One end side of the convex portion 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 concave portion connecting the cam portion 32a and the convex portion of the gantry cam portion 32b are formed to have substantially the same size, and the tapered surfaces also have substantially the same inclination angle. Therefore, as shown in FIG. 5(a), the connecting cam portion 32a and the table The frame cam portions 32b are just fitted together, whereby the coupling member 20 is rotated in conjunction with the gantry member 21. That is, when the locking portion 26 of the gantry member 21 is not engaged with the stopper 25 of the casing 24, and the coupling member 20 is rotated in conjunction with the gantry member 21, the coupling cam portion 32a and the gantry cam portion 32b are connected. The fitting and the gantry member 21 are in a lowered state as shown in Fig. 5(a).

Further, the tapered surface of the connecting cam portion 32a and the tapered surface of the gantry cam portion 32b are formed to face each other. Therefore, when a predetermined force or more acts in a direction opposite to each other along the tapered surface, as shown in FIG. 5(b), the gantry cam portion 32b slides along the tapered surface, and the gantry cam portion 32b moves to the joint. The member 20 is not formed with a flat portion that connects the cam portions 32a. Thereby, the gantry member 21 is brought into an elevated state. At this time, the spring member 27 is in a contracted state as compared with the lowered state of FIG. 5(a).

In other words, in the present embodiment, the locking portion 26 of the gantry member 21 engages with the stopper 25 of the casing 24, and the gantry member 21 stops rotating when the motor 28 rotates, thereby becoming a connecting member. The state in which the gantry member 21 can be rotated separately from the gantry member 21 can be rotated. At this time, the engagement of the gantry lifting cam 32 is released, and the gantry cam portion 32b is moved to the flat portion of the coupling member 20, whereby the gantry member 21 is raised.

As shown in FIG. 2 and FIG. 3, in the present embodiment, the motor rotating shaft 31 that serves as the center of rotation of the connecting member 20 or the gantry member 21 is not located on the lever that moves the operating lever 18 in the front-rear direction of the gas passage. The extension shaft of the moving shaft 33 is moved, and the motor rotating shaft 31 is disposed at a position deviated from the rod moving shaft 33. The connecting member 20 connected to the motor rotating shaft 31 is provided with a link portion 20a that protrudes toward the rod moving shaft 33 side. When the connecting member 20 rotates in conjunction with the motor 28, the link portion 20a pushes the slider 34 to advance or retreat the operating lever 18 connected to the slider 34 in the front-rear direction of the gas passage.

As described above, the valve body 17 of the relief valve 12 is provided in front (upstream side) of the operating lever 18, and the valve body 17 is pressed by the moving operating lever 18 to open the gas passage. An electromagnet 35 for holding the safety valve 12 in an open state is provided further in front of the valve body 17.

Next, the operation of the gas control valve 1 of the present embodiment configured as described above will be described. 6 to 10 are views showing an operation example of the gas control valve 1 of the present embodiment. Among them, Figure 6 is a time chart. 7 to 10 are views showing the state of the gas control valve 1 at each time indicated by I) to V) and *1 to *3 in the time chart of Fig. 6 .

First, as shown in Fig. 6(e), the motor 28 is reversed (CCW) at the time I). Shortly after the start of the rotation of the motor 28, the link portion 20a does not abut against the slider 34 (refer to I of Fig. 8), so that the operating lever 18 does not move toward the upstream side as shown in Fig. 6(d). Therefore, as shown in Fig. 6(c), the valve body 17 of the relief valve 12 is in a closed state (refer to I of Fig. 8).

Further, at the time I), the connecting cam portion 32a is fitted to the gantry cam portion 32b (refer to I of FIG. 7) and I) of FIG. 10, thereby The gantry lifting cam 32 is in a lowered state as shown in Fig. 6(b). Further, as shown in I) of FIG. 9, the position of the fixed-side communication hole 15 provided in the fixed disk 14 completely does not coincide with the position of the rotation-side communication hole 41 provided in the rotary disk 13. Therefore, as shown in Fig. 6 (a), the flow rate adjusting valve 11 is in a completely closed state.

Then, when the motor 28 continues to reverse, the locking portion 26 of the gantry member 21 abuts against the stopper 25 of the casing 24 and is locked, thereby stopping the rotation of the gantry member 21. When the motor 28 is further reversed in this state, the coupling member 20 is separated from the gantry member 21 in the stopped state and continues to rotate independently. At this time, as shown in the front part of *2 of Fig. 6(b), the gantry cam portion 32b slides along the tapered surface and moves to the flat portion of the coupling member 20, thereby causing the gantry lifting cam 32 to rise. High state (refer to II of Fig. 7) and II) of Fig. 10).

When the gantry lifting cam 32 is in the raised state, the spring member 27 disposed between the gantry member 21 and the rotating disk 13 is in a contracted state. That is, as shown in I) and II) of FIG. 10, the length of the spring member 27 when the stage lifting cam 32 is in the raised state is compared with the length d1 of the spring member 27 when the stage lifting cam 32 is in the lowered state. D2 becomes shorter. Therefore, the rotary disk 13 receives a strong force from the spring member 27. As a result, the coupling force of the rotary disk 13 to the fixed disk 14 becomes larger than when the stage lifting cam 32 is in the lowered state.

Further, when the connecting member 20 is separately rotated from the gantry member 21, the link portion 20a is pressed against the slider 34 by the rotation of the connecting member 20, and as shown in Fig. 6(d) 1 The operating lever 18 is moved toward the upstream side as shown in the front section. As a result, as shown in FIG. 6(c), the relief valve 12 is in an open state (refer to II of FIG. 8). In this state, the electromagnet 35 is excited in accordance with a signal from the control circuit 29, thereby keeping the safety valve 12 in an open state.

Next, when the safety valve 12 is kept in the open state by the force of the electromagnet 35, the rotation of the motor 28 is switched to the forward rotation (CW) at the time II) shown in FIG. 6(e). Thereby, as shown in the rear part of *1 of FIG. 6(d), the operation lever 18 is retracted toward the downstream side. Further, as shown in the rear portion of *2 of Fig. 6(b), the gantry cam portion 32b slides in a direction opposite to the front along the tapered surface. As a result, the connecting cam portion 32a is fitted to the gantry cam portion 32b, and the gantry lifting cam 32 is lowered (see III of FIG. 7) and I) of FIG.

In the operation up to this point, the range of the rotation angle of the motor 28 in the period from the start of the operation lever 18 toward the upstream side to the backward position to the original position is the safety valve operation range shown in *1 in FIGS. 6 and 8. . In addition, in the period in which the gantry cam portion 32b starts to rise along the tapered surface and rises to the lowered state, and then the gantry member 21 stops rotating while the tapered surface is lowered again to the lowered state, only the connecting member 20 is individually connected. The state of rotation is performed so that the power of the motor 28 is not transmitted to the rotary disk 13 via the gantry member 21. This rotation angle range is the non-power transmission range shown by *2 in FIGS. 6 and 9.

After passing the non-power transmission range, the motor 28 also continues to rotate forward (CW). Then, as shown in IV of FIG. 7 and IV) of FIG. 9, a part of the fixed-side communication hole 15 provided on the fixed disk 14 is provided. The positions of a part of the rotation side communication hole 41 provided on the rotary disk 13 coincide. Therefore, as shown in FIG. 6(a), the flow rate adjusting valve 11 is in a state in which gas is allowed to flow at a minimum flow rate (refer to IV of FIG. 7). When the motor 28 is further rotated forward, the area in which the fixed-side communication hole 15 communicates with the rotation-side communication hole 41 is gradually increased, and accordingly, the flow rate of the gas is gradually increased. The timing V) shown in each of FIGS. 6 , 7 , and 9 shows a state in which the flow rate of the gas that is allowed to flow is maximized by the communication between the fixed-side communication hole 15 and the rotation-side communication hole 41 .

The range of the rotation angle of the motor 28 in the period in which the position of the fixed side communication hole 15 coincides with the position of the rotation side communication hole 41 and allows the gas to flow (the period from the minimum state to the maximum state of the gas flow rate) is as shown. 6 and the flow adjustment range shown in *3 in Fig. 9. As is clear from Fig. 6, the flow rate adjustment range of *3 is considerably larger than the safety valve operation range of *1.

As described in detail above, in the present embodiment, the gas control valve 1 provided with the rotary disk 13 and the fixed disk 14 as a rotating body having a sealing function is provided with a motor 28 for use in the safety valve operating range. The transmission cut-off portion (the stopper 25 and the locking portion 26) that is cut off to the power of the rotary disk 13 is a function that does not allow gas to pass through the flow regulating valve 11 within the operating range of the safety valve. .

By providing such a transmission cutting portion, the rotation of the rotary disk 13 is stopped within the operation range of the safety valve, so that no friction is generated between the rotary disk 13 and the fixed disk 14, thereby preventing the two disks from being mutually Wear of the sealing surface.

Further, in the present embodiment, the coupling force variable portion (the spring member 27 and the gantry lifting cam 32) for changing the coupling force of the rotary disk 13 to the fixed disk 14 is provided. Further, in the operating range of the safety valve, the spring member 27 is contracted by causing the gantry lifting cam 32 to be raised to maximize the bonding force. On the other hand, in the flow rate adjustment range, the spring member 27 is extended by lowering the stage lifting cam 32, and the bonding force is minimized.

When the safety valve 12 is operated, it is necessary to increase the bonding force of the sealing surface in order to prevent the gas from leaking from the gap between the rotating disk 13 and the fixed disk 14 toward the downstream. In the present embodiment, since the rotary disk 13 is stopped during the operation range of the safety valve, friction is not generated between the disks even if the bonding force is enhanced, and abrasion of the sealing surface can be prevented.

On the other hand, in the flow rate adjustment range in which the flow rate adjusting valve 11 is operated, since the gas is actually being supplied, the coupling force between the rotary disk 13 and the fixed disk 14 can be slightly weakened. Since the bonding force is small, even if the rotary disk 13 rotates, the friction generated between the rotary disk 13 and the fixed disk 14 is small, so that the wear of the sealing faces of the two disks can be suppressed.

Further, in the above embodiment, as shown in FIG. 6, the non-power transmission range is set to be larger than the safety valve operation range, but the present invention is not limited thereto. For example, it is also possible to set the safety valve operating range to be the same as the non-power transmission range.

In addition, in the above embodiment, the transmission cut is provided The structure of the two members of the broken portion and the variable force portion has been described, but the present invention is not limited thereto. For example, it is also possible to adopt a configuration in which only the transmission cutting portion is provided, and the coupling force of the rotating disk 13 to the fixed disk 14 is the same as that when the gantry lifting cam 32 is in the raised state. In this case, the friction generated between the rotary disk 13 and the fixed disk 14 can be suppressed at least within the operating range of the safety valve.

Further, in the above-described embodiment, the example in which the motor rotating shaft 31 and the rod moving shaft 33 are set at positions deviated from each other and the motor 28 is rotated in both the normal rotation and the reverse rotation is described. However, the present invention has been described. It is not limited to this. In other words, as long as the transmission cutting portion and the coupling force variable portion are provided, it is not necessary to set the motor rotating shaft 31 and the rod moving shaft 33 at positions which are mutually offset, and the motor 28 can be oriented in one direction. Rotate to move.

Further, the above-described embodiments are merely illustrative of an embodiment of the present invention, and the technical scope of the present invention is not limited thereto. That is, the present invention can be implemented in various forms without departing from the gist thereof or its main features.

1‧‧‧ gas control valve

11‧‧‧Flow regulating valve

12‧‧‧Safety valve

13‧‧‧ rotating disk

14‧‧‧ Fixed disk

15‧‧‧Fixed side communication hole

16‧‧‧Magnetic box

17‧‧‧ valve body

18‧‧‧Operator

19‧‧‧ Spring

20‧‧‧Connected parts

21‧‧‧Rack components

22‧‧‧Power transmission shaft

23‧‧‧Power transmission bearing

24‧‧‧Shell

25‧‧ ‧block

26‧‧‧Kangding Department

27‧‧‧Spring parts

28‧‧‧Electric motor

29‧‧‧Control circuit

Claims (8)

A gas control valve is formed to open and close a flow regulating valve and a safety valve by an electric motor, wherein the flow regulating valve is used to regulate a supply flow rate of the gas, and the safety valve is used to cut off the gas The gas control valve is characterized in that the flow regulating valve is provided with a rotating body with a sealing function, wherein the sealing function refers to a function of not allowing gas to circulate within the operating range of the safety valve, The safety valve operating range refers to a range of rotation angles of the motor when the safety valve is actuated, and the rotating body with a sealing function includes a rotating disk and a fixed disk, wherein the rotating disk and the rotation of the motor Rotating in conjunction with the rotating disk, the fixed disk is disposed opposite to the rotating disk, and a gantry member is disposed between the connecting member and the rotating disk, and the connecting member is rotated in conjunction with the motor Disposing the safety valve, the gantry member rotating in conjunction with the coupling member to transfer power from the electric motor to the rotating disk, The air control valve is provided with a transmission cutting portion for stopping the coupling member and the gantry member by stopping rotation of the gantry member within the operating range of the safety valve The rotation is performed separately and separately, and the power transmission from the motor to the rotating disk is cut off. The gas control valve according to claim 1, further comprising a coupling force variable portion for allowing a coupling force of the rotary disk to the fixed disk to be varied, thereby making the safety valve operating range The binding force within the flow is different from the binding force within the flow adjustment range, wherein the flow adjustment range It refers to the range of rotation angles of the motor when the flow regulating valve is operated. The gas control valve of claim 2, wherein the bonding force is maximized within the operating range of the safety valve, and the bonding force is minimized within the flow adjustment range. The gas control valve according to claim 2, wherein the binding force variable portion is configured to include a spring member and a distance variable portion, the spring member being disposed on the gantry member and the seat Between the rotating disks, the distance variable portion is configured to vary the distance between the gantry member and the rotating disk. The gas control valve according to claim 1, wherein the transmission cutoff portion includes a stopper provided on a casing of the gas control valve and a card disposed on the gantry member The fixed portion is formed such that the locking portion engages with the stopper to stop the rotation of the gantry member. The gas control valve according to claim 5, wherein the binding force variable portion is configured to include a spring member and a distance variable portion, the spring member being disposed on the gantry member and the rotation The distance variable portion is for changing a distance between the gantry member and the rotating disk. The gas control valve according to claim 6, wherein the distance variable portion includes a gantry lifting cam disposed on the connecting member and the gantry member, by the locking When the portion is engaged with the stopper to stop the rotation of the gantry member, the gantry lifting cam is raised, and when the locking portion is not engaged with the stopper, The gantry lifting cam is lowered. The gas control valve according to claim 7, wherein the gantry lifting cam includes: a connecting cam portion disposed on the connecting member; and a gantry cam portion disposed on the gantry member When the gantry lifting cam is in a lowered state, the connecting cam portion is engaged with the gantry cam portion, thereby being in a state in which the gantry member can be rotated in conjunction with the connecting member, and When the gantry lifting cam is in the raised state, the engagement between the connecting cam portion and the gantry cam portion is released, whereby the connecting member can be separately rotated from the gantry member. status.