JPH08159322A - Fluid shutoff device - Google Patents

Abstract

PURPOSE: To provide a fluid shutoff device capable of controlling a flowrate, giving a stable sealing function and consuming small electric power by incrementally driving and controlling a valve disc using the linear stroke of a motor-driven shutoff valve. CONSTITUTION: A cam groove 4a with a different feed pitch for a lead screw is formed on the rotor 4 of a motor M. A cylindrical fixed guide 5 with a long groove 5a is coupled to the external side of the groove 4a and fastened to an outer enclosure 3. In addition, the starting point of the groove 4a, the displacement point of the feed pitch and the hook section 5b of the groove 5a of the guide 5 are respectively provided with a stopper section for a shaft pin 1a. This pin 1a of a shaft 1 is engaged with the guide 4a for the lead screw and the long groove 5a of the guide 5. Also, a spring receiver 6 is jointed to the forward end 1b of the shaft 1 and springs 9 and 10 are laid among the receiver 6, a main valve 7 and a sub-valve 8. In addition, the engagement teeth 67 and 68 of the receiver 6 are kept engaged with and hold the peripheral teeth 71a and 80a of the valves 7 and 8, and that in such a state as allowing the slidable separation thereof.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid cutoff device,
More specifically, the present invention relates to a fluid cutoff device that can control the flow rate of a fluid by utilizing straight stroke control of a motor cutoff valve.

[0002]

2. Description of the Related Art Conventionally, a screw mechanism has been used as a mechanism for linearly driving a valve body by a motor. That is, as shown in FIG. 8, a male screw d to be screwed with a screw c is provided on the shaft e to be provided on the rotor b of the motor a, and the rotational motion of the rotor b of the motor a is converted into the linear motion of the shaft e. It is a thing. By connecting the shaft e of the motor a to the valve body f, the valve body f makes a linear motion and the valve body f is brought into close contact with or separated from the valve seat g. The use of such a technique has an advantage that a large propulsive force can be obtained, for example, by reducing the lead pitch of the screw.

[0003]

However, in the valve body drive device, since the screw having a small lead pitch adapted to the required maximum propulsive force is used, the number of rotations of the motor is increased to move the stroke of the valve body. There is a problem in that much power is required and power consumption increases. further,
Unlike the abnormal shutoff, the flow rate control of the fluid operates frequently, resulting in a problem that power consumption increases. The position accuracy of the sub-valve is unstable because it is determined by the backlash of the screw and the starting position of the rotor of the motor, and the springs for the main valve and the sub-valve are always loaded when the valve is opened, so the propulsive force When connecting the main valve and the auxiliary valve, the shaft is connected to the center inlet of the main valve body by penetrating the shaft.Therefore, when the auxiliary valve is opened, an extra back pressure load due to the cross-section integral of the shaft is applied. There was also a problem that it increased and required extra propulsion.

In order to solve the problems of the prior art, the present invention has a structure that minimizes the propulsive force required by the motor cutoff valve, and the rotation speed of the motor of the motor cutoff valve. It is an object of the present invention to provide a fluid shutoff device which can obtain low power consumption by efficiently controlling the driving force and a stable flow rate and valve sealability with a simplified structure.

[0005]

A fluid cutoff device of the present invention comprises a flow control device and a valve body moving device for driving and controlling the flow control device. In the flow rate control device, springs are respectively interposed between the spring receiver and the main valve and the auxiliary valve, and the pawls provided on the outer circumferences of the flow control devices guide or hold the springs. The main valve includes a sub-valve, and the sub-valve is opposed to the central portion inlet port of the main valve and the valve seat formed at the opening edge thereof. The spring receiver is connected to the shaft end of the valve body moving device described later.

In the valve body moving device, a cylindrical cam in which lead screws having different feed pitches are engraved is provided on a rotor of a motor, and the cam of a shaft connected to a spring receiver constituting the valve body of the above-mentioned flow control device is provided on the cam. The shaft pin is engaged, and the shaft pin is engaged with a long groove of a cylindrical fixed guide fixed to the motor.

[0007]

According to the fluid cutoff device of the present invention, when the motor of the valve body moving device rotates, the shaft is restrained by the cam (lead screw) engaged with the shaft pin and the long groove of the fixed guide and goes straight. Therefore, the rotational movement of the motor is converted into the linear movement of the valve body. At this time, the cam is a lead screw with a different feed pitch that can move the main valve and the sub valve of the flow rate control device stepwise by the propulsive force according to the required load even if the motor torque is constant. The flow rate of the fluid can be controlled in a short time with the minimum number of rotations. Further, by providing stable positions with no lead pitch in the cam groove portion and the long groove portion of the fixed guide, the valve position accuracy can be ensured and the state can be maintained even when an external impact is applied.

Further, since the main valve and the sub valve of the flow rate control device are engaged with and moved through the flexible joint constituted by the spring and the outer peripheral pawl between the main valve and the sub valve, the main valve and the sub valve are held or moved.
The spring load does not become a load at the time of opening the valve and can reduce the propulsive force, and the shaft is not penetrated to the inlet in the center of the main valve, so the area of the inlet, that is, the back pressure load is reduced. It can be minimized, and as a result, the propulsive force during the operation of opening the auxiliary valve can be minimized.

[0009]

The following is a concrete example of the fluid cutoff device of the present invention. 1, 2, and 3 are side sectional views showing the structure of the fluid cutoff valve. In the figure, the fluid cutoff valve includes a valve body moving device A, a flow rate control device B controlled by the device, and a valve seat E formed in the fluid passage. That is,
The valve body moving device A is airtightly attached to the outside of the housing C such as a meter, and the flow rate control device B is arranged so as to be in close contact with and separated from the valve seat E formed in the fluid passage D of the housing C.

Next, the structure of the valve body moving device A will be described with reference to FIGS. The valve body moving device A is
It is mainly composed of a drive motor M as a rotary motion source and a conversion means T for converting this rotary motion into a rectilinear motion. The drive motor M has a shaft 1 directly connected to a valve body (which will be described later), an outer casing 3 (a mounting plate 3a and a rear cover 3) that is loosely fitted to the outside of the shaft 1 and has a permanent magnet 2 wound around the outer periphery thereof.
The rotor 4 is rotatably supported by b), and the electromagnetic coil 3c is sandwiched by the outer casing 3. Further, the conversion means T is, as shown in FIG. 4, a rotor 4 of the drive motor M.
And a fixed fixing having a cam (lead screw 4a) integrally formed with a resin or the like and having a different feed pitch, a shaft pin 1a engaging with the cam (lead screw 4a), and a long groove 5a engaging with the shaft pin 1a. It is composed of a guide 5. The fixed guide 5 is fixed to the rear cover 3b, and a cam (lead screw 4a) is loosely fitted in the central hole 5b.

The operation of the valve body moving device A having the above structure will be described below with reference to FIG. Fig. 5 shows shaft pin 1a
FIG. 7 is a development view of a mechanical portion showing a state in which the cam moves while engaging with the cam (lead screw 4 a) and the long groove 5 a of the fixed guide 5. In the figure, X is a fully open state, Y is a sub valve open state, Z
Is in the fully closed state, and the flow control device B is controlled from the fully opened state X (the shaft pin 1a is in the S1 position) to the auxiliary valve open state Y (the shaft pin 1a is in the S2 position) by the drive control of the drive motor M.
To the fully closed state Z (the shaft pin 1a is at the S3 position). For example, if a stepping motor is used as the drive motor M, the auxiliary valve open state Y is reached with a small propulsive force at the portion 4a1 having a long feed pitch of the cam (lead screw 4a) and a large propulsive force is provided at the portion 4a2 having a short feed pitch. The fully closed state Z is reached. Therefore, the shaft 1 has a cam (lead screw 4a) having a long feed pitch 4a1 and the shaft 1 has about 3
/ 4 rotation, in a short 4a2 portion, it moves straight about 1 rotation. Incidentally, S1 to S3 indicate stable positions where the shaft pin 1a in the valve body moving device A should be stopped. Engaged in both parts of
At the S2 position, the transition portion (flat surface portion) from the cam groove 4a1 to 4a2 and the height L1 (on the drawing) of the long groove 5a of the fixed guide 5 are engaged and surrounded, and at the S3 position, the cam groove 4a2 is fixed to the fixed guide 5. The long groove 5a is engaged with and surrounded by the hook portion 5b set to the height L2 (on the drawing) of the long groove 5a. Therefore, S1-S
3, the shaft pin 1a, that is, the shaft 1 is held in a predetermined stable position.

Next, the structure of the flow control device B will be described. As shown in the side sectional views of FIGS. 1, 2 and 3 and the external view of FIG. 6, the flow rate control device B is the valve body moving device A described above.
Is a valve body connected to one end 1b of the shaft 1 of the above, and includes a spring receiver 6 formed of resin or the like and a main valve 7
And a sub-valve 8, a main valve 7, and a main valve first spring 9 and a sub-valve second spring 10 interposed between the sub-valve 8 and the spring receiver 6, respectively. Specifically, the spring receiver 6 has a plurality of first valve guides 67 for main valves and second valve guides 68 for auxiliary valves each having inward locking claws 67a and 68a on the outer periphery thereof (in the case of the figure). 3). Further, the main valve 7 is the valve body 7
a, an adjacent valve support 7b, and a plate 7c. Specifically, the valve 7a is made of an elastic material such as rubber and has an inflow port 7d at the center, and its opening edge. A valve seat 7e is formed in the. Further, the valve support 7b
Is formed of resin or the like, and four (not limited to four) struts 71b are erected on the valve support body 7b, and each tip is connected by a ring 72a having an outward locking hook shape in cross section. The valve body 7a and the plate 7c are heat-welded to the protrusions (not shown) of the valve support body 7b which are inserted into the through holes (not shown).
Are attached together by. Further, the auxiliary valve 8 is formed of resin or the like like the valve support 7 b of the main valve 7, and the valve portion 8
On the outer periphery of 0, an outward locking hook-shaped ring 80b is formed. The sub valve 8 is held or guided by an outward locking hook-shaped ring 80b engaged with an inward locking claw 68a of the second valve guide 68 of the spring receiver 6.

By the way, in the above embodiment, the main valve and the sub valve
Although the one using a stage valve body is shown, as shown in FIG. 7, a three stage stage valve body in which a sub valve 11 similar to the main valve 7 is provided between the main valve 7 and the sub valve 8 may be used. According to this structure, there is an advantage that the flow rate can be controlled more precisely than the two-stage valve body.

The operation of the flow rate control device according to the present invention will be described below with reference to FIGS. Since the main valve 7 and the sub valve 8 receive a force in a direction of separating from the spring receiver 6 by the springs 9 and 10, the locking pawl 6
7a and the ring 72a, and the locking claw 68a and the ring 80b are attracted to each other and held (the shaft pin 1a is at the S1 position). However, the shaft 1 moves to the left (on the drawing) in the first stage (the sub valve is open) (the shaft pin 1a moves to S
2 position), the holding state between the locking claw 67a and the ring 72a is broken, but even if the valve body tilts, the tilt is corrected by the action of the flexible joint B1 by the spring 9.
Since the main valve 7 is familiar and normally adheres to the valve seat E, stable valve sealability can be ensured. However, the fluid continues to circulate from the fluid passage in the inlet 7d, and the auxiliary valve 8 is moved to the inlet 7 by the second stage shaft movement (fully closed state).
The fluid is completely shut off by coming into close contact with the valve seat 7e of d (position S3 in the cam groove). At this time, the holding state between the locking claw 68a and the ring 80b is also broken, but similarly to the above, the action of the flexible joint B1 by the spring 10 can ensure the stability of the valve sealability.

Next, the operation of the fluid cutoff valve constructed by directly connecting the flow rate control device B to the shaft tip of the valve body moving device A will be described with reference to FIGS. When the drive motor M (hereinafter, stepping motor) is pulse-controlled, the rotor 4 of the stepping motor M starts rotating. As a result, the shaft pin 1a is guided by the cam groove 4a1 of the cam (lead screw 4a) and the long groove 5a of the fixed guide 5, and the auxiliary valve opening state Y is reached at about 3/4 rotation.
(The shaft pin 1a reaches the S2 position). During this time,
Although the main valve 7 reaches the valve seat E, even if the main valve 7 comes into contact with the valve seat E in an inclined state for some reason, the flow rate control device B has a flexible joint B1 interposed between the main valve 7 and the spring receiver 6. Therefore, the tilted state is corrected by the mutual guide between the main valve 7 and the locking claws of the spring receiver 6, and the main valve 7 fits in the valve seat E and normally comes into close contact (the shaft pin 1a is in the S2 position). Stability is secured. At this time, the shaft pin 1a is inserted into the cam groove 4 in the long groove 5a of the fixed guide 5.
In the stable position S2 between a1 and 4a2, the valve seat E is the main valve 7
Blocked by. On the other hand, the inflow port 7d is in the open state and maintains the controlled flow rate.

When the stepping motor M continues to rotate, the fully closed state Z (the shaft pin 1a moves to S
3 position), the auxiliary valve 8 comes into close contact with the inlet valve seat 7e of the main valve 7 to shut off the fluid. At this time, the shaft pin 1a is in the stable position S3 of the hook portion 5b of the fixed guide 5 and maintains the fluid cutoff state.

Further, as shown in FIG. 7, by providing a sub valve 11 similar in shape to the main valve 7 between the main valve 7 and the sub valve 8,
The flow rate can be adjusted with higher accuracy.

[0018]

Since the present invention has the above-mentioned structure, it has the following effects. In the valve body moving device, the rotational movement of the drive motor is converted into the linear movement with different valve stroke and propulsion force by using the lead screw with different feed pitch, which enables highly efficient control of the valve body. Specifically, the one that conventionally required about 5 revolutions was 1 + 3 /
The number of rotations is four, and the power consumption of the drive motor of the valve body moving device can be reduced.

Since the shaft pin stopper portion (flat surface portion) is provided at the starting point and transition point of the feed pitch of the cam groove and the long groove of the fixed guide, each valve in the fully opened state, the sub valve opened state, and the fully closed state is provided. Position accuracy can be secured.

Further, in the flow rate control device, by providing a plurality of stages of similar valve bodies each having an inlet and a valve seat, it is possible to control the flow rate with high accuracy, and to use the main valve, the sub valve and the like valve elements. Adopts a flexible joint in which the locking claw provided on the valve body is engaged with the supporting claw of the valve guide panel without directly connecting the shaft, and
Since a spring is interposed between the valve body and the valve guide plate, even if the shaft center of the shaft or the valve body comes into contact with the valve seat in an inclined state, the valve is actuated by the synergistic action of the spring and the claw engagement. Since the body fits in the valve seat and comes into close contact with the valve seat, the sealing performance of the valve body is stabilized.

Further, since the shaft is directly connected to the flexible joint, not to the valve body, the back pressure load due to the cross-section integral of the shaft is eliminated, and the back pressure load applied to the sub valve when the sub valve is opened is minimized. It is possible to reduce the power consumption.

As a result, by using the flow rate control device which is driven and controlled by the valve body moving device, a safe and low power consumption fluid having a controlled flow rate and a stable valve sealability with a simplified structure is provided. A breaker is obtained, and the power consumption is reduced to 1/3 of that of the conventional one, and the life of the battery is extended.

[Brief description of drawings]

FIG. 1 is an operation state diagram showing a side section of a fluid cutoff valve according to an embodiment of the present invention.

FIG. 2 is an operation state diagram showing a side cross section of a fluid cutoff valve according to an embodiment of the present invention.

FIG. 3 is an operation state diagram showing a side cross section of a fluid cutoff valve that is an embodiment of the present invention.

FIG. 4 is an exploded perspective view showing a conversion mechanism for rotating / straightening motion of the present invention.

FIG. 5 is a development view of a mechanical portion showing an operating state of rotation / straight translational motion of the present invention.

FIG. 6 is an external view showing a fluid cutoff valve of the present invention.

FIG. 7 is a sectional view showing an embodiment of a flow rate control device of the present invention.

FIG. 8 is a side sectional view of a conventional fluid cutoff valve.

[Explanation of symbols]

 A valve body moving device B flow control device C housing D fluid passage E valve seat 1 shaft 1a shaft pin 4 rotor 5 fixed guide 6 spring receiver 7 main valve 8 auxiliary valve 9 spring 10 spring

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shinya Watanabe 1 Sasakinojikan, Fukushima-shi, Fukushima Tohoku-oki Denki Co., Ltd. (72) Inventor Atsushi Goto 1 Sasakinoji-kan, Fukushima-shi, Fukushima Prefecture Incorporated (72) Inventor Akio Nobunaga 1-270, Sennaku, Atsuta-ku, Nagoya-shi, Aichi Aichi Clock Electric Co., Ltd. (72) Inventor Hiroyuki Wami 1-270, Sennen-ku, Nagoya, Aichi Inside Aichi Clock Electric Co., Ltd.

Claims (2)

[Claims] 1. A cylindrical cam in which a plurality of lead screws having different feed pitches are engraved on a rotor of a motor, and a shaft pin engaging with the lead screws of the cylindrical cam,
A valve body moving device for driving the shaft straightly by the motor, comprising a cylindrical fixed guide provided with a long groove for engaging the shaft pin to suppress rotation of the shaft of the motor, and an output of the shaft of the valve body moving device. A spring receiver connected to the end portion, a locking claw group protruding from the spring receiver for engaging and holding or sliding contact and separation with an outer peripheral claw of the valve body group; and the spring receiver and the valve body group. A flexible joint having a spring group stretched between them; a main valve having outer peripheral pawls that are engaged with and held by locking pawls of the flexible joint and that are slidable and separable from each other; A fluid cutoff device comprising a flow control device which is linearly driven stepwise by the valve body moving device, which comprises an inflow port formed in a central portion of the valve and at least one auxiliary valve opposite to the valve seat. 2. A stable position of the valve body is provided by providing shaft pin stopper portions at the lead screw starting point and the feed pitch transition point of the cylindrical cam and the long groove of the fixed guide in the valve body moving device, respectively. The fluid cutoff device according to claim 1.