JP4534512B2 - Shut-off valve - Google Patents

Description

The present invention relates to a safety valve (International Patent Classification F16K 17/36) that operates according to an external situation, a valve that uses a magnet as an operation means (International Patent Classification F16K 31/06), and a valve that uses an electric motor as an operation means (International Patent) F16K 31/04), and particularly relates to a shutoff valve used as a shutoff mechanism of a gas shutoff device that prevents a gas accident, and more specifically, a valve element for a valve seat formed in a flow path The present invention relates to a shut-off valve mainly built in a gas meter or the like, which uses an electromagnetic solenoid or motor that performs a shut-off return operation of a flow path by moving the valve forward or backward.

  Various safety devices have been used in the past to prevent gas accidents that are likely to be a catastrophe once they occur. Among them, gas flow is monitored by a flow sensor built in a gas meter and gas is detected by a microcomputer. If the use status of the sensor is judged abnormal, or if the status of sensors such as seismic sensors, gas pressure sensors, gas alarms, carbon monoxide sensors is monitored and judged dangerous, the shutoff valve built in the gas meter The gas meter with built-in microcomputer gas shut-off device (hereinafter abbreviated as “microcomputer meter”) using a battery power source that shuts off the gas due to safety, ease of gas piping, low price, etc. has been promoted in recent years. Almost all households have been popularized.

  In addition, the ratio of centralized monitoring micrometers that have a telemeter function that centrally monitors gas flow rate information measured by a flow sensor using a telephone line or wireless communication will increase, making it more convenient as an information terminal. Improvement is demanded.

  There are two types of shutoff valve devices for this microcomputer meter.

  One is a shut-off valve device for an isolated microcomputer meter, which is driven electrically only when shut-off (closed), and the return operation is performed mainly by applying an external load, such as manually, and the external operation is transmitted to the shut-off valve. (This type of shutoff valve is hereinafter abbreviated as a unidirectional shutoff valve. The unidirectional shutoff valve is driven mainly by a self-holding electromagnetic solenoid).

  This return mechanism is a return shaft that urges the valve seat of the shut-off valve away from the valve seat, and many of them have an outer diameter slightly smaller than the valve seat so that gas does not leak even when the return shaft is kept pressed. And a second valve seat called an inner cylinder that is movable in the axial direction in conjunction with the return shaft.

  Between the inner cylinder and the valve seat, there is a gentle airtightness by a seal member.

  On the other hand, in central monitoring type microcomputer meters, etc., gas can also be shut off by electric energy from the battery installed in the microcomputer meter so that gas can be shut off and restored by simple electric switch operation, telephone line, wireless communication, etc. There is a demand for a shut-off valve (hereinafter abbreviated as a bi-directional shut-off valve) that does not require energy for maintaining the open state and the closed state.

  A bidirectional shut-off valve that uses an electric motor such as a self-holding electromagnetic solenoid or a stepping motor as a driving means has been put into practical use.

  These shut-off valves are arranged so that the gas upstream / downstream differential pressure is applied in the valve closing direction when the valve is closed in order to ensure the valve closing reliability.

  Therefore, it is necessary to raise the load corresponding to the pressure receiving area to which the upstream / downstream differential pressure is applied when the valve is opened. For example, when a differential pressure of 5 kPa is applied to a pressure receiving area with a diameter of 28 mm, it is necessary to drive a load of about 3N (hereinafter referred to as a differential pressure load).

  On the other hand, in recent years, the load that urges the valve body of this type of shut-off valve in the valve closing direction, that is, the valve closing force, has been reduced in weight in order to achieve a 10-year drive with a battery power source or to realize further power saving. In some cases, the valve closing force relative to the circumferential length of the valve seat, that is, the line seal load is less than 10 mN / mm.

  In the case of a shutoff valve with a valve seat diameter of 28 mm and a wire seal load of 10 mN / mm, the valve closing force is 0.86 N, and the above-mentioned differential pressure load is a load that is 3.5 times the valve closing force. Therefore, it is necessary to have a driving force that raises the load about 4.5 times the valve closing force when the valve is opened, i.e., energy close to 4.5 times the energy required for valve closing is required to eliminate the differential pressure load. Necessary.

  Therefore, reducing the differential pressure load leads to power saving of the shut-off valve, so conventionally, it is possible to open the small-diameter sub-valve first, use the differential pressure of the pilot valve, etc. Various devices such as deforming a part of the valve seat of the flexible body have been made.

  The differential pressure load reducing means that does not use a sub valve or pilot valve of the conventional cutoff valve will be described below.

  First, FIG. 12 shows a cross-sectional view of the valve portion of the shut-off valve of the first conventional example (see, for example, Patent Document 1).

  The valve portion of the shut-off valve includes a valve body 1 having a flexible body, and a plate-like body 3 attached to the valve stem 2 and arranged in a floating state in the air cavity of the valve body 1. The lifting member 4 is formed of a protrusion at an eccentric position.

  The operation of the valve portion of the shut-off valve configured as described above will be described.

  FIG. 12A shows the closed state of the valve portion, and the lower surface of the valve body 1 is in contact with the tip circumferential portion of the valve seat 5 and maintains a state in which no gas flows.

  At this time, the downstream side of the valve seat 5 may be at atmospheric pressure, and since gas pressure is applied upstream, a differential pressure load corresponding to the pressure receiving area to which normal gas pressure is applied is applied in the valve closing direction. .

  When the valve portion of the shut-off valve performs a return valve opening operation, a pulling force from a driving means (not shown) is applied to the valve stem 2.

  This lifting force is transmitted to the flange 6 of the valve body 1 through the lifting member 4 of the plate-like body 3. On the other hand, since a differential pressure load is applied to the pressure receiving portion of the valve body 1 (inside the inner diameter of the valve seat 5), the back surface of the lifting member 4 is partially bent in the valve body 1, and the valve body 1 is only that portion. It separates from the valve seat 2 and enters the state shown in FIG.

  In this way, the gas passage is formed and the differential pressure with the downstream is eliminated or reduced, whereby the differential pressure load is reduced, and the valve body 1 can be opened with a smaller driving force.

  Next, FIG. 13 shows a sectional view of the valve portion of the shutoff valve of the second conventional example (see, for example, Patent Document 2).

  The valve portion of the shut-off valve includes a valve body 11 that is flexible in the valve opening and closing direction, and a convex portion 15 that is attached to the valve rod 12 and is close to or abuts a point on the valve seat side in the vicinity of the valve seat 13 of the valve body 11. The push-up member 15 is formed so as to push a point in the vicinity of the valve seat of the valve body 11 when the valve rod 12 starts the valve opening operation.

  The valve body 11 is disposed so as to be fitted to the clasp 17 of the valve stem 12, and a rigid holding member 16 is disposed on the back surface of the valve body 11 so as to be freely movable with the clasp 17. A gap 18 is formed at the center of the member 16.

  The operation of the valve portion of the shut-off valve configured as described above will be described.

  FIG. 13A shows the closed state of the valve portion, and the lower surface of the valve body 11 is in contact with the circumferential portion of the tip of the valve seat 13 and maintains a state in which no gas flows.

  At this time, the downstream side of the valve seat 13 may be at atmospheric pressure, and since gas pressure is applied upstream, a differential pressure load corresponding to the pressure receiving area to which normal gas pressure is applied is applied in the valve closing direction. .

  When the valve portion of the shut-off valve performs a return opening operation, a pulling force from a driving means (not shown) is applied to the valve rod 12.

  FIG. 13B is a cross-sectional view showing the state of each part immediately after the valve stem 13 starts moving in the opening direction.

  Since the valve body 11 is urged in the valve closing direction by the differential pressure load, when the valve rod 3 starts to move, first, the central portion of the valve body is locally bent so that the gap 18 is reduced, and the push-up member 14 is moved. Approach the valve body 11.

  As a result, the pulling force of the valve stem 12 is concentrated on the convex portion 15 close to the valve seat 13, and a part of the seal between the valve body 11 and the valve seat 13 is opened. In this way, the gas passage is formed and the differential pressure with the downstream is eliminated or reduced, whereby the differential pressure load is reduced, and the valve element 11 can be opened with a smaller driving force.

  Next, FIG. 14 shows a cross-sectional view of the valve portion of the shut-off valve of the third conventional example (see, for example, Patent Document 3).

  The valve portion of this shut-off valve is connected to a valve body 21 made of an elastic member such as rubber that can come into contact with the valve seat 23, and an electric actuator (not shown) so as to be able to move forward and backward with respect to the valve seat 23. And a plate 22.

  The valve body 21 has a plurality of joint legs 24 integrally projecting on the back surface, and a flange 25 is integrally provided on each joint leg 24, and a plurality of joint holes 26 provided in the press holding plate 22 are provided in the joint body 24. Each is inserted and attached to the pressure holding plate.

  The operation of the valve portion of the shut-off valve configured as described above will be described.

  When the valve portion is closed, the lower surface of the valve body 21 is in contact with the tip circumferential portion of the valve seat 23 and maintains a state in which no gas flows.

  At this time, the downstream side of the valve seat 23 may be at atmospheric pressure, and since gas pressure is applied upstream, a differential pressure load corresponding to the pressure receiving area to which normal gas pressure is applied is applied in the valve closing direction. .

  When the valve portion of the shut-off valve performs the return valve opening operation, a lifting force from an electric actuator (not shown) is applied to the press holding plate 22.

  Since the valve body 21 is urged in the valve closing direction by the differential pressure load, when the pressing and holding plate 22 starts to move to the right side in the drawing, the flange portion 25 is hooked and the vicinity of the joint foot 24 is locally bent and deformed. The amount of deformation increases with the movement of the pressing and holding plate 22, and finally a minute gap is formed in a part of the contact portion between the valve seat 23 and the valve body 21.

In this way, the gas passage is formed and the differential pressure with the downstream is eliminated or reduced, whereby the differential pressure load is reduced, and the valve body 21 can be opened with a smaller driving force.
JP-A-4-282079 Japanese Patent Laid-Open No. 4-185981 JP 11-182893 A

  However, in the shut-off valve of the first conventional example, since the lifting member 4 is arranged at the eccentric position, the differential pressure elimination stage in the return valve opening operation, that is, when the lifting member 4 pulls up the flange 6 of the valve body 1. Simultaneously with the axial force of the valve stem 2, a lateral eccentric force 7 is applied to the valve stem 2, thereby applying an oblique load with respect to the original moving direction to the driving means not shown in the figure. There is a problem that the sliding portion of the means is likely to be worn or locked.

  Further, in the shut-off valve of the second conventional example, the push-up member 14 is arranged at the eccentric position as in the first conventional example, so that the eccentric force 19 is applied to the valve stem 12 and the sliding portion of the driving means is While there is a problem that the possibility of being worn or locked is high, the protrusion 15 of the push-up member 14 is in contact with the valve body 11 until a part of the seal between the valve body 11 and the valve seat 13 is opened. The valve stem 12 needs to drive the valve body 11 with a strong load that does not eliminate the differential pressure load, and therefore has a problem that the differential pressure at the limit at which the valve cannot be returned is relatively low. .

  Also in the third conventional example, since the joint foot 24 is arranged inside the valve seat 23, that is, in the pressure receiving portion, the periphery of the joint foot 24 is sufficiently bent and deformed, and the contact between the valve seat 23 and the valve body 21 is brought about. Until the minute gap is formed in a part of the portion, the electric actuator (not shown) needs to drive the valve body 21 with a strong load that does not eliminate the differential pressure load. In addition, there is a problem that the differential pressure at the limit becomes relatively low, and at the same time, the place where the deformation is deformed when the valve is opened is always the back surface of the joint leg 24 of the valve body 21, so that It had the subject that the gas-seal property of the valve seat 23 might be reduced.

  The present invention solves the above-mentioned conventional problems, and the load on the drive means can be reduced because the differential pressure that can be returned and opened is high, and the drive means generates wear and lock because an oblique load does not occur at the time of return valve opening. There is provided a shut-off valve having a high differential pressure canceling effect and high reliability, and a valve device capable of effectively using the shut-off valve. For the purpose.

  In order to solve the above-described conventional problems, a shut-off valve according to the present invention includes a circular valve seat made of a flexible body that can abut against a valve seat formed in a flow path, and the valve seat includes the valve seat. A holding member disposed on the back surface of the valve seat abutting portion that abuts with the valve seat, a winding portion that extends from the outer periphery of the valve seat and includes the holding member, and a generally U-shaped winding portion that is closed. A driving means for linearly moving in the valve direction and the valve opening direction; and an engaging means formed on the holding member and hooking the valve seat; A plurality of portions are equally arranged at rotationally symmetric positions around the engaging portion with the driving means, and are formed in a protruding shape having the same height in the valve opening direction.

As a result, when the valve opens, the engagement means partially deflects and deforms the outer periphery of the valve seat contact part of the valve seat to form a small opening between the valve seat and the valve seat, thereby eliminating the differential pressure with a weak load. In addition, since the engaging means are evenly arranged at the rotationally symmetric positions, the diagonal loads when the differential pressure is eliminated cancel each other, and the driving means is not given an oblique load, so that wear or It is possible to realize a shut-off valve that has a high possibility of generating a lock, has a high differential pressure elimination effect, and has high reliability.

  Since the shutoff valve of the present invention has a high differential pressure that can be returned and opened, the load on the driving means can be reduced, and since there is no oblique load at the time of return opening, the driving means is less likely to cause wear or lock. Further, the effect of eliminating the differential pressure is high, such that the possibility of permanent deformation of the fluid seal portion of the valve seat is low, and high reliability can be obtained.

  According to a first aspect of the present invention, there is provided a flexible circular valve seat capable of contacting a valve seat formed in a flow path, and a back surface of a valve seat contacting portion where the valve seat contacts the valve seat. A holding member arranged, a winding portion extending from the outer periphery of the valve seat and including the holding member, and a drive for linearly moving the holding member in the valve closing direction and the valve opening direction. And an engaging means that is formed on the holding member and latches the valve seat, and the engaging means is centered on the engaging portion with the driving means on the outer peripheral side from the valve seat abutting portion. By arranging a plurality of valves equally at the rotationally symmetric positions and having a shut-off valve formed in the shape of a protrusion with the same height in the valve opening direction, the engaging means can be moved from the valve seat contact portion of the valve seat when the valve is opened. Difference in weak load by partially bending and deforming the outer periphery to form a small opening between the valve seat and the valve seat In addition, since the engaging means is evenly arranged at the rotationally symmetric position, the diagonal load at the time of eliminating the differential pressure cancels each other so that no oblique load is applied to the drive means. It is possible to realize a highly reliable shut-off valve having a high differential pressure elimination effect and low possibility of causing wear and lock.

According to a second aspect of the present invention, a circular valve seat made of a flexible body capable of abutting a valve seat formed in a flow path, and a back surface of a valve seat abutting portion where the valve seat abuts on the valve seat. and disposed a holding member, a cylindrical portion from the outer peripheral portion is extended outside of the holding member of said valve seat, and a plurality of lateral holes opened in the side surface of the cylindrical portion, the valve closing direction and opening the holding member Drive means for linearly moving in the direction, and engagement means formed on the holding member for latching the valve seat, the engagement means being rotationally symmetric about the engagement portion with the drive means By making the shut-off valve formed into a plurality of protrusions that can be inserted into the lateral holes of the holding member at equal positions , the engaging member is not the contact surface with the valve seat of the valve seat, and the back surface of the valve seat Since it can be formed on the outer peripheral surface of the holding member other than the contact surface with the holding member or on the rear surface of the holding member, the engaging means is closed. The engagement means pulls up a part of the valve seat extended from the outer peripheral side to the outside of the holding member at the time of the return valve opening, so that a wide range of the valve seat surface is warped from the valve seat. Because it is bent and deformed so that it peels off, there is little occurrence of rebound elastic force when deforming a narrow range of the valve seat with a large displacement, and the differential pressure can be eliminated or reduced with a weaker load. Since the narrow range is not deformed by a large displacement, permanent deformation is unlikely to occur, and a shutoff valve having a high differential pressure elimination effect and high valve closing reliability can be realized.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the present embodiment.

(Embodiment 1)
1 is a cross-sectional view of the shut-off valve in the open state according to Embodiment 1 of the present invention, FIG. 2 is a cross-sectional view of the shut-off state, FIG. 3 is a cross-sectional view when the return valve is open, and FIG. The perspective view of the combination of the valve seat partial cross section of the same shut-off valve and the holding member is shown.

In FIG. 1, a valve seat 33 made of a flexible body such as a synthetic rubber such as nitrile butadiene rubber (nitrile rubber) capable of contacting a valve seat 32 formed in a flow path 31, and a valve seat of the valve seat 33 A holding member 34 made of a synthetic resin such as polyoxymethylene (polyacetal) disposed on the back surface of the contact portion 33a, a stepping motor 35 which is a driving means for driving the holding member 34 in the coaxial direction with the valve seat 32, A shut-off valve is configured with a plurality of equally arranged rotationally symmetric positions on the outer peripheral side of the valve seat abutting portion 33a, and engaging means 36 for engaging the valve seat 33 and the holding member 34 at this position. Yes.

  The valve seat 33 extends from the outer peripheral portion of the back surface of the valve seat abutting portion 33a to the outside of the holding member 34, has a substantially U-shaped cross section, and has a winding portion 33b in which the axial gap 33c is thicker than the thickness of the outer peripheral portion of the holding member 34. The holding member 34 is rotatably mounted on the valve seat 33 so as to be included in the winding portion 33b, and the engaging means 36 has an axial thickness larger than that of the outer peripheral portion of the holding member 34. The protrusions having a thickness equal to or less than the thickness of the gap 33c are arranged at a plurality of positions on the outer periphery of the back surface of the holding member 34 that are evenly symmetrical (in this example, at two positions to be rotated by 180 °).

  Between the inner periphery of the winding part 33b of the valve seat 33 and the outer periphery of the holding member 34 facing each other, a substantially uniform gap 37 is formed over the circumference.

  The valve seat 33 is formed with a concave portion 38 at the center of the back surface of the valve seat abutting portion 33a, and the holding member 34 is formed with a convex portion 39 that is loosely fitted into the concave portion 38 at the central portion of the valve seat 33 abutting surface. Yes.

  A gap 40 extending from the inner side to the outer periphery of the valve seat abutting portion of the holding member 34 is formed on the back surface of the valve seat 33 and the facing portion of the holding member 34.

  When the thickness of the outer peripheral portion of the holding member 34 is 0.7 mm, the gap 33c of the winding portion 33b is appropriately 2 mm, the projection height of the engaging means 36 is about 1 mm, and the outer diameter of the valve seat 33 is 32 mm. It is appropriate that the outer diameter of the member 34 is 29 mm, the gap 37 is about 0.5 mm, and the gap 40 is about 0.3 mm.

  The shape and configuration of the valve seat 33 and the holding member 34 described above can be understood in a three-dimensional relationship from the perspective view of the combination of the valve seat 33 partial cross section and the holding member 34 in FIG.

  A lead screw 42 is formed on the rotating shaft 41 of the stepping motor 35, a lead nut 43 is formed in the center hole of the holding member 34, and is screwed together, and the holding member 34 is axially moved toward the stepping motor 35. A skirt 45 having a slit 44 is formed, and an engaging claw 47 that can be engaged with the slit 44 is formed in a central hole of a flange 46 that is a mounting plate of the stepping motor 35, so that the holding member 34 and the flange 46 are relatively positioned. The lead screw 42, the lead nut 43, the slit 44, and the engaging claw 47 constitute a linear mechanism that converts the rotation of the rotary shaft 41 into a linear motion in the axial direction of the valve seat 32. Yes.

  The stepping motor 35 is a non-magnetic metal thin plate can 48 and a seal member 49, and the rotor 50 and the stator 51 are hermetically maintained. 52 is arranged.

  A spring 53 is compressed and disposed between the flange 46 and the holding member 34 so as to urge the holding member 34 in the direction of the valve seat 32 (in the case of the above-described dimensions, an urging force of about 1 N is appropriate). Is).

  The operation and action of the shut-off valve configured as described above will be described below.

First, in the valve open state shown in FIG. 1, the holding member 34 moves backward toward the stepping motor 35, the valve seat 33 is detached from the valve seat 32, and the valve open state in which a fluid such as gas can pass is held. ing.

  The center of the shaft of the valve seat 33 and the holding member 34 is generally held by loose fitting between the concave portion 38 and the convex portion 39, and the engaging means 36 and the winding portion 33 b are gently in contact with each other to hold the valve seat 33. The position in the axial direction with respect to the member 34 is maintained, and since there is no differential pressure, the valve seat 33 is not deformed, and the gap 37 and the gap 40 are secured.

  When a gas flow rate is abnormal, an earthquake occurs, or when a shut-off command is issued by communication or external means, a shut-off valve signal from a control means such as a microcomputer meter (not shown) is applied to the stepping motor 35, and the rotor 50 is turned on. It rotates and is converted into a linear motion in the axial direction of the valve seat 32 via the lead screw 42 and the lead nut 43, the holding member 34 moves to the valve seat 32 side, and the valve seat 33 and the valve seat 32 abut against each other to close. Then, the holding member 34 is pushed slightly toward the valve seat 32, the gap 40 is reduced, the valve seat 33 is bent and deformed, and the entire circumference of the valve seat abutting portion 33a abuts on the valve seat 32 so that a fluid such as a gas can be obtained. At the end of the shut-off valve closing signal, the stepping motor 35 steps out and finishes the shut-off valve closing operation.

  Even when there is a slight angle shift between the valve seat 33 and the valve seat 32 when the valve is opened, or even when the valve seat abutting portion 33a is slightly deformed such as a wave, Since the valve seat 33 is bent and deformed in the gap 40, the valve seat 32 and the valve seat 33 can be brought into uniform contact with each other, and high valve closing performance can be realized.

  Further, it is necessary that the valve seat 33 and the holding member 34 relatively move at the time of the bending deformation. However, between the inner periphery of the winding portion 33b of the valve seat 33 and the outer periphery of the holding member facing the circumference, Since there is a substantially uniform gap 33c, there is no sliding resistance and the relative movement can be performed smoothly, and the improvement in valve closing performance due to deformation of the valve seat 33 in the gap 40 is not hindered.

  FIG. 2 is a cross-sectional view of the valve closing state when the differential pressure 54 is generated upstream and downstream of the valve seat 33 after shutting off and closing in this way.

  In FIG. 2, the central portion of the valve seat 33 bulges toward the valve seat 32 due to the biasing force of the differential pressure 54, and the fitting of the concave portion 38 of the valve seat 33 and the convex portion 39 of the holding member 34 is released. For this reason, the outer periphery of the valve seat 33, that is, the inner periphery of the entraining portion 33b, falls slightly inward so that the diameter of the inner periphery becomes smaller, but the inner periphery of the entraining portion 33b of the valve seat 33 and the outer periphery of the holding member facing each other. The circumferential gap 33c is not 0, the outer periphery of the holding member 34 and the inner periphery of the entraining portion 32b are not in contact with each other and the valve closing performance is not deteriorated, and the holding member 34 is in the final stage of the shut-off valve closing operation. Since the engagement means 36 and the winding portion 33b are separated from each other because they are slightly pushed toward the valve seat 32, the engagement means 36 does not affect the valve closing performance.

  After the final push-in operation and step-out operation of the shut-off valve closing operation, the rotor 50 is slightly reversed so that the stress between the valve seat 32 and the lead screw 42 and the lead nut 43 is removed and stabilized by the spring 53. Therefore, it is possible to provide a valve device with high long-term reliability, which is less likely to cause permanent deformation.

  Next, the return valve opening operation will be described with reference to FIGS.

  When returning from the valve opening, it is necessary to raise the load corresponding to the pressure receiving area applied to the upstream and downstream differential pressures of the valve seat 33. For example, when a pressure of 5 kPa is applied to the pressure receiving area of 28 mm in diameter, the differential pressure load of about 3N is applied. Need to drive.

  On the other hand, reducing the differential pressure load leads to realizing power saving of the shut-off valve in order to target driving for 10 years with a battery power source or to realize further power saving.

  When a return valve opening signal from a control means such as a microcomputer meter (not shown) is applied to the stepping motor 35, the rotor 50 rotates in the reverse direction during the shut-off valve closing operation, via the lead screw 42 and the lead nut 43. Therefore, the holding member 34 moves in a direction away from the valve seat 32. First, the holding member 34 is first moved within the play in the rotational direction of the slit 44 and the engaging claw 47. The valve seat 33 moves slightly relative to the valve seat 33, the engaging means 36 then contacts the winding portion 33b of the valve seat 33, and the engaging means 36 pulls the winding portion 33b. FIG. 3 shows that a small amount of fluid can be circulated by pulling in the axial direction from the outer periphery of the contact portion 33a and partially bending and deforming toward the holding member 34 to form a small opening 55 between the valve seat 32 and the valve seat 33. It becomes a state.

  In the return valve opening operation so far, during the movement of the holding member 34 until the opening 55 is formed between the valve seat 32 and the valve seat 33, the pressure receiving portion inside the valve seat contact portion 33a of the valve seat 33 is driven. The holding member 34 can be moved with a small load, and the engaging means 36 bends and deforms so that the wide range of the surface of the valve seat 33 is peeled off from the valve seat 32. Therefore, the narrow range of the valve seat 33 is increased. The opening 55 can be formed with a weaker load with less occurrence of repulsive elastic force generated when the deformation is caused by the displacement.

  In the case of the specific dimensions described above, the differential pressure load of about 3N can be reduced to about 1.7N without the engagement means 36 (the stepping motor 35 includes about 2.7N including the biasing force of the spring 53). Need to drive the load).

  At this time, since the engaging means 36 are evenly arranged at the rotationally symmetric positions, the diagonal loads when the differential pressure is eliminated cancel each other, and the stepping motor 35 is not subjected to the diagonal loads, and wear and lock are generated. The possibility of letting it be low.

  In addition, as described in the description of the valve closing state, the fitting of the concave portion 38 of the valve seat 33 and the convex portion 39 of the holding member 34 is released, and the holding member is opposed to the inner periphery of the winding portion 33b of the valve seat 33. The circumferential gap 33c between the outer periphery and the outer periphery is not 0, and the relative separation operation between the valve seat 33 and the holding member 34 is not hindered in the initial stage of the return valve opening operation, so the holding member 34 is moved with a weak load. it can.

  When the opening 55 is formed between the valve seat 32 and the valve seat 33, a small amount of fluid can flow, and this flow causes the side of the valve seat 32 of the valve seat 33 to have a high pressure portion, and the back surface has a low pressure portion. As a result, the differential pressure 54 upstream and downstream of the valve seat 33 decreases, the valve seat 33 cannot abut against the valve seat 32 against the tension of the engaging means 36, and finally the valve seat contact of the valve seat 33 The entire circumference of the contact portion 33a is detached from the valve seat 32, and thereafter, the differential pressure is rapidly eliminated, and the valve seat 33 moves integrally with the holding member 34 to the stepping motor 35 side, and the valve opening state shown in FIG. Return to.

  Even in the return valve opening operation, after the holding member 34 abuts on the stepping motor 35 and performs the step-out operation, the operation between the lead screw 42 and the lead nut 43 is performed by slightly rotating the rotor 50 backward. It is possible to realize a valve device with high long-term reliability that is less likely to cause permanent deformation.

In this way, the engaging means 36 pulls the entraining portion 33 b and partially deforms from the outer periphery of the valve seat contact portion 33 a of the valve seat 33 to form a small opening 55 between the valve seat 32 and the valve seat 33. Thus, the differential pressure can be eliminated or reduced with a weak load, and at the same time, since the engaging means 36 is evenly arranged at the rotationally symmetric position, the diagonal loads when the differential pressure is eliminated cancel each other, The possibility that the stepping motor 35 is worn or locked without applying an oblique load is low.

  Furthermore, since the narrow range of the valve seat 33 is not deformed by a large displacement, permanent distortion is unlikely to occur, and the holding member 34 rotates slightly relative to the valve seat 33 during the return valve opening operation, and the engaging means 36 Is formed on the holding member 34, and the bending deformation position of the valve seat 33 is not displaced and fixed in the rotational direction during the repetitive operation, so the possibility that the valve seat contact portion 33a of the valve seat 33 is permanently deformed is low. High valve closing reliability can be realized.

  In the return valve opening operation when the differential pressure 54 becomes abnormally high, the valve seat 33 is bent to some extent because the engaging portion 36b other than the engaging means 36 of the holding member 34 is included in the winding portion 33b. A highly reliable shut-off valve that is engaged in the axial direction at a portion other than the rear engagement means 36 and has a low possibility of detachment of the valve seat 33 and the holding member 34 even at a high differential pressure, and is difficult to break.

  In addition, since the valve body is configured only by the holding member 34 in which the valve seat 33 and the engaging means 36 are integrally formed, it is possible to realize a cut-off valve that is inexpensive and has few destruction sites.

  As described above, according to the first embodiment, since the differential pressure that can be returned and opened is high, the load on the driving means can be reduced, and since the oblique load is not generated when the return valve is opened, the driving means can generate wear and lock. Therefore, it is possible to realize a shut-off valve having a high differential pressure elimination effect and high reliability, such that the possibility of permanent deformation of the fluid seal portion of the valve seat is low.

( Reference Example 1 )
FIG. 5 is a graph showing the relationship between the torque required for pulling up the holding member and the position of the holding member during the return valve opening operation of the valve device in Reference Example 1 of the present invention.

  This valve device comprises the shut-off valve shown in FIG. 1 and control means capable of switching the driving torque.

  In FIG. 5, the control means is slightly longer than the position (position 2 mm) where the valve seat 33 is separated from the valve seat 32 from the position (position 0.5 mm) at which the engagement means 36 begins to bend the valve seat 33 when the valve is opened. Drive up to the stroke (position 2.5 mm) by switching to high torque control.

  For example, the frequency for driving the stepping motor 35 is 100 pps at high torque, and 200 pps at others.

  By driving in this way, the holding member 34 is driven with a high load until the differential pressure 54 is eliminated or reduced in the return valve opening operation of the shutoff valve, and the valve seat 33 is reliably peeled off from the valve seat 32, After that, it is possible to realize a valve device that switches to low-torque driving that can further suppress power and performs efficient driving that can reduce power consumption.

(Embodiment 2 )
FIG. 6 shows a sectional view of the shut-off valve in the opened state in the second embodiment of the present invention.

  In FIG. 6, the valve seat 63 is formed with a cylindrical portion 63a that extends from the outer peripheral portion of the back surface of the valve seat abutting portion 33a to the outside of the holding member 64. Horizontal holes 63c are opened at positions (in this example, at two positions to be rotated by 180 °), the holding member 64 is mounted on the valve seat 63 so as to be contained in the cylindrical portion 63b, and the engaging means 66 is the holding member 64. A protrusion 66a is formed on the opposite side of the valve seat 32, and is arranged so as to be inserted into two lateral holes 63c of the valve seat 63 to constitute a shut-off valve.

  Others are the same as those in FIG.

  In the return valve opening operation of the shut-off valve, as the stepping motor 35 rotates, the holding member 64 moves in a direction away from the valve seat 32, and the engaging means 66 pulls the lateral hole 63c of the valve seat 63. The valve seat 63 is pulled in the axial direction from the outer periphery of the valve seat abutting portion 63a and is partially bent toward the holding member 64 to form a small opening between the valve seat 32 and the valve seat 63, so that a small amount of fluid flows. It becomes possible.

  In the returning valve opening operation so far, it is necessary to drive the pressure receiving portion inside the valve seat abutting portion 63a of the valve seat 63 during the movement of the holding member 64 until the opening is formed between the valve seat 32 and the valve seat 63. The holding member 64 can be moved with a small load, and the engaging means 66 bends and deforms so that the wide range of the surface of the valve seat 63 is warped and peeled off from the valve seat 32, so that the narrow range of the valve seat 63 is greatly displaced. The repulsion elastic force generated when deforming is small, and the opening can be formed with a weaker load.

  At this time, since the engaging means 66 are evenly arranged at the rotationally symmetric positions, the oblique loads when the differential pressure is eliminated cancel each other, and the stepping motor 35 is not subjected to the oblique loads, so that wear and lock are generated. The possibility of letting it be low.

  When an opening is formed between the valve seat 32 and the valve seat 63, a small amount of fluid can flow, the pressure difference between the upstream and downstream of the valve seat 63 is reduced, and finally the entire valve seat contact portion 63a of the valve seat 63 is reduced. The circumference disengages from the valve seat 32, and thereafter, the differential pressure is rapidly eliminated, and the valve seat 63 moves to the stepping motor 35 side integrally with the holding member 64 to return to the valve open state.

  Other operations and states are substantially the same as those of the shut-off valve in FIG.

  The shut-off valve of FIG. 6 is characterized in that the valve seat 63 does not have an undercut (unreasonable removal) in the molding like the entangled portion 33b in the shut-off valve of FIG. A thermoplastic synthetic resin elastomer such as polyurethane or polyester elastomer, which is difficult to undercut, but can be selected as the material of the valve seat 63, and a chemically stable valve seat 63 utilizing the characteristics of this thermoplastic synthetic resin elastomer is provided. it can.

  However, unlike the shut-off valve in FIG. 1, the relative position in the rotational direction between the valve seat 63 and the engaging means 64 does not change, so that a specific portion of the valve seat 63 is repeatedly deformed and easily generates permanent deformation. It is necessary to design while paying attention to the amount of deformation of the sheet 63.

( Reference Example 2 )
FIG. 7 is an assembly schematic diagram of the valve body of the shut-off valve in Reference Example 2 of the present invention.

  In FIG. 7, a flexible valve seat 73 having holes 73 a formed at rotationally symmetric positions of 120 ° at three positions outside a portion that contacts a valve seat (not shown), and the back surface of the valve seat 73. The holding member 74 formed with a hole 74a at a position opposite to the hole 73a, and the valve seat 73 and the holding member 74 are rotated by passing through the hole 73a and the hole 74a and fixed by snap fitting. A valve body is constituted by the locking member 76 that is latched at a symmetrical position, and a shut-off valve is constituted by a drive means (not shown) that drives the holding member 74 in the axial direction.

  A detailed description of the shutoff valve and a description of its operation are omitted.

As shown in FIG. 7, the engaging means 76 is not necessarily integral with the holding member 74, and is not necessarily limited to the holding member 7.
4 may not be included in the outer periphery of the valve seat 73, and the engaging position of the engaging means 76 may be three or more as long as it is equally rotationally symmetrical. The unevenness in the central portion may be reversed as long as it fits gently, and the valve seat 73 may not have a protruding valve seat abutting portion.

( Reference Example 3 )
FIG. 8 is a cross-sectional view of the shut-off valve in the opened state in Reference Example 3 of the present invention, and FIG. 9 is a cross-sectional view when the return valve is opened.

  In FIG. 8, a holding member 84 that is engaged with the valve seat 83 and has a cylindrical portion 84a projecting toward the valve seat 83 around the center hole and a plunger 93 of the electromagnetic solenoid 85 are integrally formed, and the tip of the tip is thin. A connecting body 87 having a shaft portion 87a slidably disposed through a central hole of the holding member 84, and a connecting member 84 and a tip of the moving body 87 connected to each other with a gap 90 in the valve seat 83 moving direction. The shut-off valve is configured by means 88 and a spring 89 that is compressed and arranged between the inside of the holding member 84 and the connecting means 88 so as to urge the holding member 84 in the direction in which the holding member 84 approaches the moving body 87. .

  The valve seat 83 extends from the outer peripheral portion of the back surface of the valve seat abutting portion 33a to the outside of the holding member 84 to form a winding portion 83b having a substantially U-shaped cross section and a thicker axial gap than the outer peripheral portion of the holding member 84. The holding member 84 is rotatably attached to the valve seat 83 so as to be included in the winding portion 38b, and the engaging means 86 has a thickness in the axial direction larger than the thickness of the outer peripheral portion of the holding member 84 and the gap of the winding portion 83b. The protrusions having a thickness equal to or less than the thickness of the holding member 84 are arranged at a plurality of positions on the outer periphery of the back surface of the holding member 84 that are equally symmetrical with respect to rotational symmetry (in this example, two positions at a rotation target position of 180 °).

  The detailed configuration between the valve seat 83 and the holding member 84 is substantially the same as that of the shut-off valve in FIG.

  Since the spring 92 disposed between the flange 91 of the electromagnetic solenoid 85 and the holding member 84 is weaker than the spring 89, the gap 90 is usually formed between the cylindrical portion 84a of the holding member 84 and the connecting means 88. .

  The operation and action of the shut-off valve configured as described above will be described below.

  In the valve open state shown in FIG. 8, the plunger 93 and the core 94 come into contact with each other and are magnetically attracted by the magnet 95, so that the valve seat 83 is separated from the valve seat 82 and the flow path 81 is opened.

  When a shut-off signal is applied to the electromagnetic solenoid 85, the plunger 93 is disengaged from the core 94, urged by the spring 92, the valve seat 83 abuts the valve seat 82, and the flow path 81 is shut off. become.

  Next, the return valve opening operation when the upstream / downstream differential pressure of the valve seat 83 is high in the closed state will be described.

  When a return valve opening signal is applied to the electromagnetic solenoid 85, the plunger 93 is electromagnetically attracted to the core 94 and starts moving toward the core 94, but the valve seat 83 cannot be detached from the valve seat 82 because of the high differential pressure. The member 84 hardly moves, the spring 89 is compressed, the moving body 87 (plunger 93) and the holding member 84 move relative to each other, and the connecting means 88 contacts the cylindrical portion 84a of the holding member 84 as shown in FIG. It will be in the state.

  Thereafter, the valve seat 83 is bent by the engaging means 84 to form a partial opening, so that the differential pressure can be eliminated or reduced with a weak load. This operation and effect are substantially the same as those of the shut-off valve in FIG. Since it is the same, description is abbreviate | omitted.

  Normally, the electromagnetic solenoid 85 operates at high speed, and the electromagnetic attraction force is small when the distance between the plunger 93 and the core 94 (ie, the magnetic gap) is wide, and the electromagnetic attraction force increases as the magnetic gap becomes narrower. Therefore, in the latter stage of the valve opening return operation of FIG. 9, the magnetic gap is sufficiently small so that the electromagnetic attractive force is large and the differential pressure canceling operation by the engaging means 84 can be reliably performed.

  After the differential pressure is eliminated or reduced, the valve seat 83 is moved away from the valve seat 82, and the holding member 84 is urged by the differential force between the spring 89 and the spring 92 and moves to the electromagnetic solenoid 85 side. On the other hand, the plunger 93 also comes into contact with the core 94 and returns to the valve open state shown in FIG.

  Thus, after the magnetic gap of the suction part of the electromagnetic solenoid 85 is sufficiently small and the electromagnetic attractive force is increased, the valve seat 83 is bent to eliminate and reduce the differential pressure. A valve can be realized.

( Reference Example 4 )
FIG. 10 is a cross-sectional view of the valve device in the opened state in Reference Example 4 of the present invention, and FIG. 11 is a cross-sectional view at the time of the return valve opening.

  In FIG. 10, a flexible valve seat 103 that can contact the valve seat 102 formed in the flow path 101, and a stainless steel holding member disposed on the back surface of the valve seat 102 of the valve seat 103. 104, a self-holding electromagnetic solenoid 105 that drives the holding member 104 in the same direction as the valve seat 103, and a plurality of the solenoids 105 are equally arranged at rotationally symmetric positions on the outer peripheral side from the contact portion of the valve seat 102. The shut-off valve is configured by including an engaging means 106 that latches the seat 103 and the holding member 104.

  The valve seat 103 is extended from the outer peripheral portion of the back surface of the valve seat 102 to the outside of the holding member 104, and a holding portion 104 b is formed in which the cross section is substantially U-shaped and the axial gap is thicker than the thickness of the outer peripheral portion of the holding member 104. The member 104 is mounted on the valve seat 103 so as to be enclosed in the winding portion 103b, and the engaging means 36 is a protrusion that protrudes from the outer peripheral portion of the holding member 104 into the gap of the winding portion 103b in the direction opposite to the valve seat 102. The holding member 104 is arranged at a plurality of positions on the outer periphery of the back surface that are equally symmetrical with respect to rotation (in this example, two positions at a rotation target position of 180 °).

  A spring 108 is arranged between the holding member 104 and the flange 107 of the self-holding electromagnetic solenoid 105 in a direction to urge the valve seat 103 against the valve seat 102, and the magnet 111 causes the plunger 109 to resist the urging force. Magnetic attraction is performed on the core 110 side.

  A second valve seat 112 made of a synthetic resin such as polyoxymethylene having a slightly smaller outer diameter than the valve seat 102 is arranged coaxially with the valve seat 102, and the second valve is loaded by an external load such as a person pushing with a finger. A return shaft 113 that moves the seat 112 in the axial direction, a spring 114 that urges the valve seat 103 to retreat the second valve seat 112 away from the valve seat 102, a valve seat 102, A shut-off valve return mechanism by an external force is constituted by a seal member 115 such as a synthetic rubber disposed between the two valve seats 112, and a valve device is constituted by including the shut-off valve and the return mechanism.

  About the valve apparatus comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, in the valve open state shown in FIG. 10, the plunger 109 and the core 110 are in contact with each other and magnetically attracted by the magnet 111, the valve seat 103 is separated from the valve seat 102, and the flow path 101 is opened.

  When a shut-off valve closing signal is applied to the self-holding electromagnetic solenoid 105, the plunger 109 is disengaged from the core 110 and is urged by the spring 114 so that the valve seat 103 contacts the valve seat 102 and the flow path 101 is shut off. The valve is closed.

  Next, the return valve opening operation when the upstream / downstream differential pressure of the valve seat 103 is high in the closed state will be described.

  When the valve device is returned and opened, the second valve seat is moved when a person pushes it with a finger or moves the return shaft 113 closer to the self-holding electromagnetic solenoid 105 by an external load such as a return device using an electric motor. 112 also moves integrally, the second valve seat 112 abuts on the valve seat 103, and further pushed, the valve seat 103 is detached from the valve seat 102 and starts moving integrally with the second valve seat 112, The plunger 109 moves in the direction of the core 110 and finally the plunger 109 and the core 110 abut.

  In the course of the movement of the second valve seat 112, the seal member 115 holds the valve seat 102 and the second valve seat 112 in an airtight manner. Even if an abnormal operation such as fixing the return shaft 113 is performed in a state where it is pushed in for self-harm or mischief, the fluid such as the gas is not eliminated and the fluid such as the gas does not flow. Is safe without flowing.

  When the plunger 109 and the core 110 come into contact with each other, a magnetic attraction force by the magnet 111 acts to hold the plunger 109 and the core 110 against the urging force of the spring 108, and then drives the return shaft 113 such as releasing a finger. When the external load is removed, the second valve seat 112 starts to move toward the valve seat 102 by being biased by the spring 114, but the valve seat 103 follows the second valve seat 112 by the above-described differential pressure. Try to start moving.

  At this time, the holding member 104 is sucked by the core 110 integrally with the plunger 109 via the central portion of the valve seat 103, and only the outer peripheral portion of the valve seat 103 follows the second valve seat, so that the engagement means 106 pulls the winding portion 103b of the valve seat 103, and the valve seat 103 is pulled in the axial direction from the outer periphery of the contact portion of the second valve seat 112, and is partially bent toward the holding member 104 to be deformed. A small opening 116 is formed between the valve seat 103 and a small amount of fluid can flow.

  This state is shown in FIG.

  When the opening 116 is formed between the second valve seat 112 and the valve seat 103, a small amount of fluid can flow, and the differential pressure upstream and downstream of the valve seat 103 is reduced. The second valve seat 112 is separated from the second valve seat 112, retracts to the inside of the valve seat 102, and returns to the valve open state.

  In the return valve opening operation so far, the engaging means 106 bends the valve seat 103 and peels it from the second valve seat 112 with a small force, so that it is possible to return to a larger differential pressure. Since they are uniformly arranged at rotationally symmetric positions, the diagonal loads when the differential pressure is eliminated cancel each other, and since the diagonal load is not applied to the plunger 109, there is a low possibility of causing wear or lock.

  Thus, in this embodiment, at the time of return opening, the self-holding electromagnetic solenoid 105 is returned by moving the second valve seat 112 by an external force or the like until the return valve opening is completed. Since the valve seat 112 seals the gas, the gas does not leak even when the second valve seat is stopped 112 during the operation, and the second valve seat after the self-holding electromagnetic solenoid 105 is restored and adsorbed. When the gas passage is opened by retreating 112, the valve seat 103 is bent and deformed at the rotation target position by the engaging means 106 to form a small opening 116 between the second valve seat 112 and the differential pressure is eliminated. Alternatively, in order to alleviate, it is possible to realize a highly reliable valve device that is reopened with an external force that can be opened to a higher differential pressure and that is less likely to cause wear or lock on the plunger 109 or the like.

  As described above, the shutoff valve and the valve device according to the present invention can reduce the load on the drive means because of the high differential pressure that can be restored and opened, and the drive means is worn and locked because no oblique load is generated when the valve is opened. In addition, it has a high differential pressure cancellation effect and high reliability, such as a low possibility of permanent deformation of the fluid seal part of the valve seat. It can also be used for applications such as control valves and manual control valves.

  Further, the valve device having the second valve seat is effective not only for the self-holding electromagnetic solenoid but also for the actuator having the latch mechanism.

Sectional drawing of the valve opening state of the shutoff valve in Embodiment 1 of this invention Sectional view of the shut-off valve closed Sectional view when the shut-off valve is opened Perspective view of combination of valve seat partial cross section and holding member of same shut-off valve The graph which showed the relationship of the load required in order to raise the torque at the time of reset valve opening operation | movement of the valve apparatus in the reference example 1 of this invention, and a holding member, and the position of a holding member Sectional drawing of the valve opening state of the shutoff valve in Embodiment 2 of this invention Assembly schematic diagram of valve body of shut-off valve in Reference Example 2 of the present invention Sectional drawing of the open state of the shut-off valve in the reference example 3 of this invention Sectional view when the shut-off valve is opened Sectional drawing of the valve opening state of the valve apparatus in the reference example 4 of this invention Sectional view of the valve device when the valve is opened (A) Cross-sectional view of the valve portion of the shut-off valve of the first conventional example in the closed state (b) Cross-sectional view during the return valve opening operation of the valve portion of the shut-off valve (A) Cross-sectional view of the valve portion of the shut-off valve of the second conventional example in the closed state (b) Cross-sectional view during the return valve opening operation of the valve portion of the shut-off valve Sectional drawing of the valve part of the shut-off valve of the 3rd prior art example

31, 81, 101 Flow path 32, 82, 102 Valve seat 33, 63, 73, 83, 103 Valve seat 33a Valve seat contact portion 33b, 83b, 103b Entrainment portion 33c Air gap 34, 64, 74, 84, 104 Holding Member 35 Stepping motor (drive means)
36, 66, 76, 86, 106 Engaging means 37 Cavity 38 Concave part 39 Convex part 40 Crevice 42 Lead screw (linear mechanism)
43 Lead nut (Linear mechanism)
44 Slit (Linear mechanism)
47 Engagement Claw (Linear Mechanism)
85 Electromagnetic solenoid 87 Moving body 88 Connecting means 89 Spring (biasing body)
90 Clearance 105 Self-holding electromagnetic solenoid 112 Second valve seat 115 Seal member

Claims (2)

A circular valve seat made of a flexible body capable of coming into contact with the valve seat formed in the flow path, and a holding member disposed on the back surface of the valve seat contacting portion where the valve seat comes into contact with the valve seat; A winding portion extending from the outer periphery of the valve seat and including the holding member, and a driving means for linearly moving the holding member in the valve closing direction and the valve opening direction; and the holding member Engaging means for latching the valve seat, and the engaging means is equal to a rotationally symmetric position around the engaging portion with the driving means on the outer peripheral side from the valve seat abutting portion. A shut-off valve formed in a protruding shape with the same height in the valve opening direction. A circular valve seat made of a flexible body capable of abutting against a valve seat formed in the flow path, and a holding member disposed on the back surface of the valve seat abutting portion where the valve seat abuts on the valve seat; , a cylindrical portion from the outer peripheral portion is extended outside of the holding member of said valve seat, and a plurality of lateral holes opened in the side surface of the cylindrical portion, thereby linearly moving the holding member in the closing direction and the opening direction drive And an engaging means that is formed on the holding member and latches the valve seat, and the engaging means is in a rotationally symmetric and uniform position around the engaging portion with the driving means, and A shutoff valve formed into a plurality of protrusions that can be inserted into the lateral hole of the holding member.

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