JP6603387B2 - Shut-off valve - Google Patents

Description

The present invention relates to a shut-off valve provided with a brake mechanism that reduces an impact at the time of shut-off.

As a highly reliable mechanical shut-off valve, for example, there is a spring return type using a “spring spring” described in Patent Document 1. For example, as shown in FIG. 9A, this shut-off valve has a structure including a brake mechanism 1, and when the brake mechanism 1 is released in an emergency, the wound spring 2 is released and the valve is released. The body 3 is turned and blocked.
In other words, this shut-off valve is composed of the valve body 3, the drive mechanism 4 and the brake mechanism 1. The valve body 3 is a ball valve or a butterfly valve that opens and closes by rotating an output shaft (valve shaft) 5 by 90 degrees. The drive mechanism 4 includes an internal gear 7 that is rotated by driving a motor 6, a plurality of planetary gears 8 that mesh with inner peripheral teeth inside the internal gear 7, and an output shaft 5.
A sun gear 9 that is rotatably attached to the outer periphery of each planetary gear 8 and meshes with each planetary gear 8, and a flange that projects from the outer periphery of the output shaft 5 one end of the support shaft 10 that passes through each planetary gear 8 that meshes with the sun gear 9. 11 and the sun gear 9 is connected to the relay gear 13 by a sleeve 12 that passes through the output shaft 5.

  On the other hand, the brake mechanism 1 includes a winding gear 14 connected to a relay gear 13 provided on a sleeve 12, a spring 2 provided on a shaft to which the winding gear 14 is attached, and a winding gear 14 to which the spring 2 is attached. And a brake means 16 that stops the rotating shaft 15 that meshes with the brake means 16. Here, an electromagnetic clutch brake (for example, a gear that is attached to the output shaft as the rotating shaft) is used as the brake means 16. ing.

In such a shut-off valve, in the fully closed position of the valve body 3, in the case shown in FIG. 9A, the stopper bolt 18 is applied to the stopper plate 17 provided on the output shaft 5, and the output shaft 5 is rotated clockwise. In a state where the rotation is blocked and the electromagnetic clutch brake (brake means) 16 is turned off, the motor 6 is operated to rotate the internal gear 7 clockwise. Then, the planetary gear 8 is prevented from rotating clockwise by the support shaft 10 integral with the output shaft 5 and rotates, and the relay gear 13 that is interlocked with the sun gear 9 rotates. As a result, the winding gear 14 connected to the relay (intermediate) gear 13 rotates to wind the mainspring 2.

  When the winding of the mainspring 2 is completed, the clutch brake 16 is operated to hold the mainspring 2 in a pressure-accumulated (tightened) state. In this state, the hoisting gear 14, the relay gear 13, and the sun gear 9 are held so as not to rotate. Therefore, when the motor 6 is reversed and the internal gear 7 is rotated counterclockwise as shown in FIG. 9B. Since each planetary gear 8 revolves counterclockwise while rotating and pushes the support shaft 10, the output shaft 5 and the valve body 3 rotate counterclockwise to open the shut-off valve. Further, when the motor 6 is rotated forward, the output shaft 5 and the valve body 3 rotate clockwise, so that the shutoff valve can be closed. In this manner, the shutoff valve can be opened and closed by rotating the motor 6 with the mainspring 2 wound up.

On the other hand, when the energization is interrupted due to an accident or the like while the shut-off valve is in use, the electromagnetic clutch brake 16 is turned off and the wound spring 2 is released. Therefore, mainspring 2
As shown in FIG. 9C, the hoisting gear 14, the relay gear 13, and the sun gear 9 rotate in the direction opposite to that during hoisting due to the elastic restoring force (stretching force). At this time, since the internal gear 7 that engages with the motor 6 stopped due to the power failure is in a fixed state, each planetary gear 8 revolves clockwise while rotating with the rotation of the sun gear 9, and the spindle 10 Press. As a result, the output shaft 5 and the valve body 3 also rotate clockwise, and the output shaft 5 stops at a position where the rotation is blocked by the stopper bolt 18 as shown in FIG. In this way, when the energization is interrupted, the valve body 3 is automatically rotated to be interrupted.

By the way, as described above, the output shaft 5 and the gears 7, 8, 9 of the drive mechanism 4 are damaged when being blocked by the stopper bolt 18 if the rotation speed is too high. .
As one method for solving this problem, for example, as shown in FIG. 10, a weight 20 w is attached to the input shaft 19 of the electromagnetic clutch brake 16 via the one-way clutch 20 to regulate the rotation speed.
This utilizes the fact that the input shaft 19 of the electromagnetic clutch brake 16 is internally connected to a shaft connected to the hoisting gear 14.

JP 2010-38238 A

However, as described above, the weight can be attached to restrict the rotational speed to prevent damage to each gear of the output shaft and the drive mechanism. However, there is a problem with the electromagnetic clutch brake to which the weight is attached. This is because the life of the one-way clutch interposed between the weight and the clutch brake is extremely shortened by the weight of the weight.
For this reason, it is conceivable to reduce the weight of the weight, but if the weight of the weight is reduced, the speed of the output shaft increases and the output shaft and each gear of the drive mechanism are damaged.
It is also possible to attach the weight directly to the clutch brake input shaft without using the one-way clutch. However, if reverse rotation is applied, it is possible that the clutch brake bearing will be loaded and damaged.

Therefore, an object of the present invention is to prevent damage to each gear of the output shaft and the drive mechanism, and to prevent damage to the one-way clutch (clutch brake bearing).

One embodiment of this invention, a gear connected to hoisting gears on the output shaft provided with a valve body, a spiral spring which is provided on the shaft fitted with the hoisting gear, a rotary shaft which mutually chewing a gear fitted with the spiral spring a brake mechanism constituted by a brake means for stopping holds the spiral spring which is tightened by actuating the brake mechanism, the brake mechanism releases the release to tightening was the spiral spring to the emergency provides a shut-off valve that shuts off by rotating the valve body.

  In one embodiment, the shut-off valve includes a braking member provided symmetrically with respect to the rotation axis of the brake mechanism via a one-way clutch. The brake member brakes rotation of the rotary shaft when the spring spring around which the brake mechanism is tightened is released.

  In one embodiment, the braking member includes a wind receiver that is provided symmetrically with respect to the rotating shaft of the brake mechanism and receives wind when the rotating shaft rotates. The wind receiver may be provided 180 degrees symmetrical with respect to the rotation axis of the brake mechanism.
  In one embodiment, the braking member includes a telescopic member that is provided symmetrically with respect to the rotation axis of the brake mechanism and expands and contracts in a direction perpendicular to the rotation axis in accordance with the rotation of the rotation shaft.

In one embodiment, the braking member includes an elastic member that can be expanded and contracted in a direction perpendicular to the rotation axis of the brake mechanism and that pulls in a contracting direction, and a cylindrical outer member that has an open tip as a contact portion. Including.
In one embodiment, the shut-off valve has a sliding surface that is in contact with a contact portion at a tip of the outer member when the braking member is extended, and is provided around the rotating shaft of the brake mechanism. Includes a sliding ring .

In one embodiment, the brake means is a clutch brake unit in which an electromagnetic clutch and an electromagnetic brake are centered and abutted and set.

  Since the present invention is configured as described above, the life of the shutoff valve can be extended.

Structure diagram of the embodiment (A) Partial cross-sectional front view of brake mechanism, (b) Plan view of FIG. Action explanatory diagram of the embodiment Action explanatory diagram of the embodiment Action explanatory diagram of the embodiment (A), (b) Action explanatory drawing of embodiment Action explanatory diagram of the embodiment (A) The top view of Example 1, (b) The partial cross section front view of the brake mechanism of Example 1 (A), (b), (c) Action explanatory diagram of a conventional example Partial sectional front view of a conventional brake mechanism

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
The shut-off valve in FIG. 1 is similar to the conventional shut-off valves in FIGS.
And the brake mechanism 21, and the invention of the present application is applied to the brake mechanism 21. For this reason, the same reference numerals are used for the same members.

That is, the valve body 3 is a ball valve or a butterfly valve that opens and closes by rotating the output shaft (valve shaft) 5 by 90 degrees, and the drive mechanism 4 uses a planetary gear mechanism.
Therefore, the drive mechanism 4 is rotatable to the outer periphery of the output shaft 5 and the internal gear 7 that is rotated by driving of the motor 6, the plurality of planetary gears 8 that mesh with the inner peripheral teeth of the internal gear 7. A sun gear 9 which is attached and meshes with each planetary gear 8 is arranged, one end of a support shaft 10 penetrating each planetary gear 8 is connected to a flange 11 projecting from the outer periphery of the output shaft 5, and the output shaft 5
The sun gear 9 is connected to the relay (intermediate) gear 13 by a sleeve 12 that passes through.
Further, the output shaft 5 is provided with a stopper plate 17 below the flange portion 11.
7 abuts on the stopper bolt 18 to restrict the rotation range of the output shaft 5 to 90 degrees.

The brake mechanism 21 includes a winding gear 14 that is gear-connected to the relay gear 13, a mainspring 2 provided on a shaft to which the winding gear 14 is attached, and a rotary shaft 15 that is gear-connected to the winding gear 14 to which the mainspring 2 is attached. The brake means 22 is configured to stop.
Here, the brake means 22 uses an electromagnetic clutch brake, and FIG.
As shown in (b), the output shaft 23 of the electromagnetic clutch brake (brake means) 22 is used as the rotation shaft 15 and a gear is attached. The electromagnetic clutch brake 22 is a clutch brake unit in which the electromagnetic clutch and the electromagnetic brake are aligned and abutted against each other. Here, only the electromagnetic brake is used, and the electromagnetic clutch is turned off without energization (the clutch is connected). Used). Further, as described above, a gear connected to the winding gear 14 via a gear is attached to the output shaft 23.
In addition to such a brake mechanism 21, a brake member 25 is provided on the input shaft 24 of the electromagnetic clutch brake, and a sliding ring 26 provided with the input shaft 24 as the center of the ring is provided. Yes.

The braking member 25 includes an elastic member 27 that can extend and contract in a direction perpendicular to the input shaft 24 of the electromagnetic clutch brake 22 and that pulls in the reduction direction, and is provided symmetrically with respect to the input shaft 24. Yes. In this embodiment, the braking member 25 is as shown in FIGS. 2 (a) and 2 (b).
The elastic member 30 includes an inner rod 28, an outer member 29, an elastic member spring 27, and a hub 31 that supports the elastic member 30.

The inner rod 28 has a T-shaped cross section with a spring stopper 32 formed at the tip, and is inserted into a cylindrical (including a square tube) outer member 29. The cylindrical outer member 29 is configured such that the tip is open and the open tip is a contact portion (brake shoe) 38.
On the other hand, the rear end portion of the outer member 29 is closed, and has a shape in which an insertion hole for inserting the inner rod 28 is provided in the center. The inserted inner rod 28 is inserted from the rod side, and the inserted rod is attached to the hub 31 through the insertion hole. For this reason, the outer member 29 of the elastic member 30 attached to the hub 31 is pulled in the direction of contraction due to the extension of the spring 27.

The hub 31 has a cylindrical shape and is provided with a mounting hole for the elastic member 30 at the top. Further, the mounting holes are provided symmetrically by 180 degrees, so that the pair of elastic members 30 are mounted in a balanced manner. The cylindrical hub 31 has an input shaft 24 of the electromagnetic clutch brake 22.
The through-hole which inserts is formed. As shown in FIG. 2A, the through hole is formed with an insertion port 33 having a diameter larger than that of the input shaft 24 of the electromagnetic clutch brake 22. The insertion port 33 is formed from the insertion end to about half the length of the through hole, and is adapted to fit the one-way clutch 34.
As shown in FIG. 2A, the braking member 25 configured as described above is provided with the electromagnetic clutch brake 2.
The one-way clutch 34 is inserted into the second input shaft 24, the hub 31 is inserted, and the C-type retaining ring 35 is attached. Then, the rotation when the mainspring spring 2 is wound up is not transmitted to the braking member 25 by the one-way clutch 34, as will be described later.
In addition, although what described here attached one set of the expansion-contraction member 30, it described the expansion-contraction member 3
The number of sets of 0 is not limited to one set. The number of sets is appropriately set according to the braking situation.

As shown in FIG. 2B, the sliding ring 26 is attached to a case of the electromagnetic clutch brake 22 with a column 36 so that the input shaft 24 of the electromagnetic clutch brake 22 is at the center of the ring 26. A sliding surface 37 is formed on the inner periphery of the sliding ring 26, and the sliding surface 3
7, the diameter of the sliding ring 26 and the height of the column 36 are determined so as to contact the contact portion 38 at the tip when the braking member 25 is extended.

This configuration is configured as described above, and in this shut-off valve, the mainspring 2 is wound (wound up) during use.
That is, as shown in FIG. 3, the stopper bolt 18 is attached to the stopper plate 17 of the output shaft 5 of the shut-off valve.
To prevent the output shaft 5 from turning clockwise. Next, with the electromagnetic clutch brake 22 turned off (electromagnetic brake), the motor 6 is operated to rotate the internal gear 7 clockwise. Then, the planetary gear 8 is rotated by being prevented from rotating clockwise by the support shaft 10 integrated with the output shaft 5. As a result, the relay gear 13 interlocked with the sun gear 9 rotates, and the winding gear 14 geared to the relay gear 13 rotates to wind up the spring 2. At this time, the output shaft 23 of the electromagnetic clutch brake 22 that meshes with the hoisting gear 14 also rotates. However, the braking member 25 attached to the electromagnetic clutch brake 22 does not rotate because the rotation is not transmitted by the one-way clutch 34.
When the winding of the mainspring 2 is completed, the electromagnetic clutch brake 22 is operated to stop the rotation of the gear meshing with the winding gear 14, so that the mainspring 2 is held in a pressure-accumulated (rolled) state. At this time, the relay gear 13 and the sun gear 9 meshing with the winding gear 14 are also held so as not to rotate. Therefore, when the internal gear 7 is rotated counterclockwise by rotating the motor 6 in the reverse direction as shown in FIG. 4, each planetary gear 8 revolves counterclockwise while rotating and pushes the support shaft 10. Therefore, the output shaft 5 and the valve body 3 rotate counterclockwise, and the shutoff valve can be opened. Further, when the motor 6 is rotated forward, the output shaft 5 and the valve body 3 can rotate clockwise to close the shutoff valve. In this way, the shutoff valve can be opened and closed using the motor 6.

On the other hand, when the energization is interrupted due to an accident or the like during use of the shut-off valve, the electromagnetic clutch brake 22 is turned off and the wound spring 2 is released as shown in FIG. For this reason, the winding gear 14, the relay gear 13,
The sun gear 9 rotates in the direction opposite to that at the time of winding. At this time, the output shaft 23 of the electromagnetic clutch brake 22 that meshes with the hoisting gear 14 rotates in the direction opposite to that at the time of hoisting, so that the rotation is transmitted by the one-way clutch 34 to rotate the braking member 25.

When the braking member 25 starts to rotate, centrifugal force acts on the expansion / contraction member 30 provided in a direction perpendicular to the input shaft 24 of the electromagnetic clutch brake 22. At this time, the braking member 25 is connected to the input shaft 24.
Therefore, there is no “shake” and no load is applied to the input shaft 24.
Further, since the centrifugal force acts outward in a direction away from the input shaft 24, the outer member 29 extends against the spring 27, which is an elastic member. Therefore, when the spring 27 ≧ centrifugal force, the outer member 29 is in a contracted state as shown in FIG. On the other hand, when the spring 27 <centrifugal force, it extends as shown in FIG.

That is, the centrifugal force T is
T = mα = mRω ² = mR (2πn) ² = 4π ² mRn ²
Indicated by
Here, the repulsive force P of the spring (spring) 27 is
P = −κx
It is. Therefore, when T> P when the rotational speed of the input shaft is n> n1, the outer member 29 moves in a direction away from the input shaft 24 and contacts the sliding ring 26 to act as a brake.
The frictional force F at this time is
F = −μ (TP) = braking force.
Where m is the mass of the outer member,
R: distance from the input shaft to the center of mass (center of gravity) of the outer member,
ω: angular velocity of input shaft, n: rotational speed of input shaft,
n1: Maximum rotation speed of input shaft, α: Centrifugal acceleration,
P: spring repulsion, κ: spring constant,
x: compression distance of the spring,
μ: coefficient of friction (contact portion of outer member and sliding surface of sliding ring),
F: Friction force (between the contact portion of the outer member and the sliding surface of the sliding ring)
It is.
For this reason, if the extension amount with respect to the rotational speed of the braking member 25 is adjusted by changing the spring 27 provided in the braking member 25, the speed to be regulated can be easily adjusted regardless of the weight.

This operation will be described with reference to the graph of FIG.
As shown in graph A of FIG. 7, when the shut-off valve starts shut-off, the released spring 2 is released.
, The rotational speed of the input shaft 24 of the electromagnetic clutch brake 22 gradually increases. When the rotational speed n reaches n1, the outer member 29 expands against the repulsive force of the spring 27 due to centrifugal force, and the extended outer member 29 contacts the sliding surface 37 on the inner side of the sliding ring 26. . Then, a frictional force F is generated between the sliding surface 37 and the contact portion 38 of the outer member 29, the rotation is braked, and the rotation speed n decreases. Thus, since the centrifugal force is also reduced when the rotational speed n is reduced, the outer member 29 is reduced. Further, when the outer member 29 is reduced, the contact portion 38 of the outer member 29 and the sliding surface 37 of the sliding ring 26 are separated from each other, the brake is not applied, and the centrifugal force increases. Therefore, the outer member 29 extends against the repulsive force of the spring 27 and comes into contact with the sliding surface 37 on the inner side of the sliding ring 26. And since frictional force F generate | occur | produces between the sliding surface 37 and the outer side member 29, and a rotation is braked, the rotation speed n falls and the outer side member 29 shrinks.
As described above, the outer member 29 repeats the extending and contracting operations, whereby the rotational speed of the input shaft 24 of the electromagnetic clutch brake 22 can be kept constant.
As a result, since the rotational speed of the output shaft 5 of the shut-off valve is regulated to be constant via the winding gear 14 that meshes with the output shaft 23 of the electromagnetic clutch brake 22, the stopper plate 17 of the shut-off valve output shaft 5 stops the stopper when the shut-off is completed. The impact hitting the bolt 18 can be reduced.

Incidentally, when the conventional weight 20w is used, as shown in the graph B plotted with a one-dot chain line in FIG. 7, the rotation speed increases until the completion of the interruption, and in some cases increases to the maximum rotation speed n2.
Therefore, it is not possible to mitigate the impact when the stopper plate 17 of the output shaft 5 of the shutoff valve hits the stopper bolt 18 when the shutoff is completed. In addition, since n2> n1, the electromagnetic clutch brake 22 using the weight 20w that is heavier than that of the present application is a bearing or one-way clutch 34.
Damage due to large inertia.

In the first embodiment, as shown in FIGS. 8A and 8B, the brake member 25 provided with the wind receiver 40 will be described.
The wind receiver 40 is provided with vertical wings such as Darrieus wind turbines below the braking member 25, and is provided 180 degrees symmetrical like the telescopic member 30. Such a wind receiver 40 is provided, and the brake is applied by receiving the wind during rotation.
Therefore, if the brake by the wind receiver 40 is used together, the brake load of the braking member 25 can be reduced accordingly. As a result, the service life of the brake member 25 and the sliding ring 26 can be extended, and the structure of the brake member 25 and the slide ring 26 can be easily reduced in weight to reduce the load on the shaft and extend the service life of the brake mechanism.

In the embodiment, a spring is used for the elastic member 27, but the elastic member 27 is not limited to this. For example, an elastic member 27 such as rubber or resin can be used.
In the embodiment, the spring in the extension direction is used, but conversely, a mechanism using a spring in the reduction direction can be used.
Note that reference numeral 50 in the figure is a sensor mechanism that includes a microswitch and a cam and detects the opening and closing of the shut-off valve.
Examples of features that can be extracted from this specification and the accompanying drawings are described below.
1. A winding gear that is gear-connected to an output shaft provided with a valve body, a spring that is provided on the shaft to which the winding gear is attached, and a brake means that stops a rotating shaft that meshes with the gear to which the spring is attached. A shut-off valve that has a brake mechanism and operates the brake mechanism to hold the tightened spring spring, releases the brake mechanism to release the wound spring spring in an emergency, and turns the valve body to shut it off. There,
The brake mechanism includes an elastic member that can be expanded and contracted in a direction perpendicular to the rotation axis of the brake mechanism and that pulls in a contraction direction, and a cylindrical outer member that has an open tip as a contact portion. A braking member provided symmetrically with respect to the rotation axis of
A shut-off valve comprising a sliding ring that is formed on the inner periphery of the ring with a sliding surface that comes into contact with the contact portion at the tip of the outer member when the braking member is extended.
By adopting such a configuration, when the mainspring is released and the rotating shaft of the brake mechanism rotates, the braking member provided to extend and contract in a direction perpendicular to the shaft by the centrifugal force due to the rotation extends. Then, the tip of the extended braking member comes into contact with the inner sliding surface of the sliding ring to regulate the rotational speed. As a result, the rotational speed of the output shaft of the shut-off valve is regulated via a winding gear that meshes with the rotating shaft of the brake mechanism. At that time, the braking member regulates the rotation speed to be constant by repeating expansion and contraction by regulating the speed. At this time, since the braking member is provided symmetrically with respect to the axis, it does not “shake”. Further, the extension amount of the braking member with respect to the rotational speed can be changed by adjusting an elastic member provided in the braking member. For this reason, the speed to be regulated can be adjusted regardless of the weight of the weight, so that no load is applied to the shaft.
2. Item 5. The shutoff valve according to Item 1, wherein the brake member is provided with a wind receiver that receives wind during rotation.
By adopting such a configuration, if a brake by windshield is used together, the load of the brake by the sliding ring can be reduced accordingly. As a result, the service life of the brake member and the sliding ring can be extended, and the structure of the brake member and the slide ring can be easily reduced in weight to reduce the load on the shaft. Therefore, the life of the brake mechanism can be extended.
3. Item 3. The shutoff valve according to Item 1 or 2, wherein the brake mechanism is a clutch brake unit in which an electromagnetic clutch and an electromagnetic brake are centered and abutted and set.

DESCRIPTION OF SYMBOLS 1 Brake mechanism 2 Spring spring 3 Valve body 5 Output shaft 14 Hoisting gear 15 Rotating shaft 16 Brake means 19 Input shaft 21 Brake mechanism 22 Electromagnetic clutch brake 23 Output shaft 24 Input shaft 25 Brake member 26 Sliding ring 27 Spring 30 Extendable member 34 One way Clutch 37 sliding surface

Claims (3)

A winding gear that is gear-connected to an output shaft provided with a valve body, a spring spring provided on a shaft to which the winding gear is attached, and a brake means that stops a rotating shaft that meshes with the gear to which the spring spring is attached. A brake mechanism, operating the brake mechanism to hold the wound spring, and releasing the wound spring by releasing the brake mechanism in an emergency to rotate the valve body A shut-off valve for shutting off,
Including a braking member that is provided symmetrically with respect to the rotating shaft of the brake mechanism via a one-way clutch, and that brakes the rotation of the rotating shaft when the spring mechanism that has been wound is released.
The braking member is provided symmetrically with respect to the rotation axis of the brake mechanism, and extends and contracts in a direction perpendicular to the rotation axis according to the rotation of the rotation shaft, and the rotation axis of the brake mechanism. provided symmetrically against, and a wind receiving for receiving the wind during rotation of the rotary shaft, the shut-off valve.   The shut-off valve according to claim 1, wherein the wind receiver is provided symmetrically with respect to a rotation axis of the brake mechanism. The shut-off valve according to claim 1 or 2 , wherein the brake means is a clutch brake unit in which an electromagnetic clutch and an electromagnetic brake are set to face each other.

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