JP2005233297A - Drive device of rotary valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmitting means as a drive device of a rotary valve including a clutch mechanism to be interposed between a manual drive source and a geared transmitting mechanism for shutting off the input being transmitted when the input exceeds the limit value, capable of preventing the device from being damaged by application of an excessive force by hindering the force from being transmitted, restoring the transmission of the force automatically when the input is no more larger than the limit value, and performing the drive of the valve. <P>SOLUTION: A handle wheel is installed through the clutch mechanism on a handle shaft of a manual actuator for driving the rotary valve, and when an input equal to or exceeding the specified value is applied through the handle wheel, the clutch mechanism being coupled is disengaged so that the input is not transmitted to the handle wheel, and when the input is not more than the specified value, the clutch mechanism is put in coupled condition, wherein engagement and disengagement of the clutch mechanism are conducted through balancing of the resilient force of a spring with a separating force of projections formed on the abutting surfaces of the clutch members caused by slopes. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a drive device for a rotary valve, and more particularly, includes a clutch mechanism that intermittently transmits driving force, and when a driving force exceeding a certain value is input, the driving force is interrupted and an excessive input is applied. The present invention relates to a drive device that prevents damage to the device.

  Conventionally, as a driving device for a rotary valve such as a butterfly valve or a ball valve, a manual transmission is used to interpose a gear transmission mechanism consisting of a worm and a worm gear between a manually rotated handle wheel and a valve rod, and a valve rod with a manual driving force. The rotary valve drive device that rotates the valve to open and close the valve is known, and is disclosed in, for example, Japanese Patent No. 3081820.

  In such a known driving device, it is preferable that the output torque of the gear transmission mechanism manually provided and the valve driving torque output for driving the valve body from the gear transmission mechanism are matched, In practice, the input torque to the gear transmission mechanism is usually larger than the required valve drive torque. Moreover, in a manual device in which the input source is human power, the magnitude of the input torque has a very large individual difference, and an excessive force may be applied. For this reason, there is a risk of damage to the drive device including the handle wheel, the gear transmission mechanism, the casing, and the like.

  In particular, in recent years, with the demand for resource saving and cost reduction, the drive device has been reduced in size and the unnecessary strength of the material has been reduced, and the output limit value of the drive device has been made as close to the valve drive torque as possible. However, it cannot always be said that the input limit value is observed in the field where the valve is used. An accident that breaks has occurred.

Japanese Patent No. 3081820

  In the present invention, when an input exceeding the input limit value is applied, a clutch mechanism that interrupts input transmission is interposed between the manual drive source and the gear transmission mechanism to prevent transmission of force exceeding the input limit value. Power transmission means for preventing damage to the device due to excessive force application and for automatically restoring the force transmission when the input is less than the limit value so that the valve can be driven. It is to be provided.

  The present invention attaches a handle wheel to a handle shaft of a manual actuator for driving a valve of a rotary valve via a clutch mechanism, and when an input of a predetermined value or more is applied via the handle wheel, the connection of the clutch mechanism is released. The clutch mechanism is connected when the input value is less than a predetermined value and the input / output is not transmitted to the handle shaft. This is performed by a balance with the detachment force due to the inclination angle of the protrusion protruding from the contact surface of the clutch member.

  The clutch mechanism is composed of a driven side clutch member that is coupled to the handle shaft with the rotation direction integrated, and a driving side clutch member that has an integrated handle wheel and is rotatably inserted into the driven side clutch member. At least one protrusion that meshes with each other is provided on the contact surface of the clutch member, and both clutch members are springed in the contact direction by a spring.

  The inclination angle of the inclined surface of the protrusion is in the range of 5 to 40 °, the inclined surface of the protrusion is formed from a central plane at least half the height of the protrusion, and the protrusions mesh with each other in the central plane. Inclined surfaces are formed on both side surfaces of the projection so that the clutch mechanism operates regardless of whether the direction of rotation of the handle wheel is normal or reverse.

  A spring fixing plate on which one end of the spring is stretched is fixed from the outer surface of the driving side clutch member to the tip of the handle shaft, and is connected to the driven side clutch member in a disconnected state.

  According to the rotary valve drive device of the present invention, the clutch mechanism is interposed between the manual handle wheel and the gear transmission mechanism to cut off the input torque above a predetermined value and prevent excessive torque conduction. In addition, it is possible to prevent damage to the device due to the addition of excessive torque, and when the input torque drops below a predetermined value, the clutch mechanism is automatically returned to the connected state immediately to transmit the driving force. Therefore, the operation of the clutch mechanism does not require time and can be used as a safety mechanism. Furthermore, the present invention can be applied to the existing rotary valve only by attaching the clutch mechanism of the present invention to the handle shaft instead of the existing handle wheel.

  Preferred embodiments of the present invention will be described in detail below. The present invention relates to a manual drive device for a rotary valve having a rotating valve element such as a butterfly valve, a ball valve, etc., and a manual rotation means such as a handle wheel for generating a manual input; A clutch mechanism for intermittently transmitting power is arranged between the power transmission means such as a gear transmission mechanism for transmitting the driving force of the moving means to the valve rod for opening and closing the valve, and an excessive driving force exceeding a predetermined value is provided. When transmitted, the transmission is cut off to prevent damage to the driving force transmission mechanism such as the gear transmission mechanism, the gear case, the connection portion between the handle shaft and the handle wheel, and the connection portion between the valve stem and the gear transmission mechanism. It is characterized by doing so. Further, the clutch mechanism is characterized in that when the input drops below a predetermined value, the clutch mechanism is automatically restored and the driving force is reconnected. Furthermore, the drive device according to the present invention can be realized by a simple change by simply attaching to the handle shaft instead of the existing handle wheel, and does not require any special parts, tools or tools, so that the pipe is already installed. It is also possible to easily apply to a rotary valve attached to.

  The clutch mechanism includes at least one protrusion arranged on the driving side and the driven side clutch members along the rotation locus and meshing with each other. The two clutch plates are always repelled in the direction of contact, and the surface facing the rotation direction of the protrusion is formed as an inclined surface having a predetermined inclination angle α, and the input value from the driving side clutch member is a predetermined value. When the value is exceeded, the detachment force due to the inclination angle α becomes larger than the elastic pressing force against the clutch member, so that the engagement of the protrusion is released and the driving force transmission is interrupted. Further, when the input returns to zero or below a certain value, the clutch member is pressed by the elastic force, so that the engagement of the protrusion is restored and the transmission of the driving force is restored. That is, when the input applied to the driving side is greater than or equal to a certain value or less than the certain value, the clutch is automatically engaged, and the driving force can be transmitted or disconnected. The inclination angle may be provided only on one side surface of the protrusion in the rotation direction, but by forming it on both side surfaces, the clutch can be engaged and disengaged in both forward and reverse rotation directions. .

  The driving-side clutch member is a substantially disk-shaped member integrated with the handle wheel, and is rotatably inserted into the handle shaft that is the input shaft of the gear transmission mechanism. The clutch member on the driven side is a disk-like member that is coupled so as to rotate integrally with the handle shaft. Protrusions that mesh with each other are formed on opposing contact surfaces of both clutch members. The engagement or disengagement of both clutch members is achieved by meshing or disengaging. The driving-side and driven-side clutch members receive the elastic force of the spring stretched between the two members, and are normally biased in the direction in which they abut against each other. Be ranked. When the input value exceeds a certain value, a separation force due to the inclination angle α is generated, the protrusion slides along the inclination, the meshing is released against the spring force of the spring, and both clutch members are in the non-connected state. Transition.

  As shown in FIGS. 6 to 8, at least one protrusion is arranged along a circular locus centering on the handle shaft, preferably at a predetermined angle θ, and has a certain length L in the diameter direction. The outer peripheral side is wide, and the inner peripheral side is narrow and has a trapezoidal shape. Referring to FIG. 8, the side surfaces, preferably both side surfaces, of the protrusion are formed on the inclined surface having the inclination angle α. When providing an inclination angle on both side surfaces of the protrusion, it is possible to make the input value different depending on the rotation direction by making one inclination angle different from that of the other. The inclination angle α is preferably 5 to 40 °. If the inclination angle is less than 5 °, the detachment force becomes too small to substantially achieve the detachment of the protrusion, and the clutch action cannot be obtained. On the other hand, if the angle is larger than 40 °, there is an inconvenience that the protrusion is detached even if the input is small. The number N of protrusions is about 1 to 30, and the protrusion interval angle θ is given by θ = N / (2 × 360).

The distance P between the protrusions on the driving side and the driven side is given by the following equation when the diameter of the central circle passing through the center of the length L of the protrusion is DC.
P = πDC (θ / 360)

As shown in FIGS. 9 and 10, the protrusions are arranged at equal intervals on both the driving side and the driven side, and a gap ε is provided in the protrusion to facilitate engagement and separation of the protrusions. When the width of the protrusion is b, the gap ε is preferably about 0.05 to 0.3b. The gap ε is provided on the inclined surface and the upper surface of the protrusion. Thus, the distance P between the protrusions is a value of the following formula.
P = 2 × (b + ε)

  In order to establish the engagement and disengagement of the protrusion, the inclination angle α on both side faces of the protrusion is not raised from the upper surface of the disk at the lower end of the protrusion, but at the center above the height of the protrusion. They are formed vertically from the plane (see FIG. 8). That is, the clutch mechanism is configured to mesh on a central plane that is half the height of the protrusion including the gap ε. Accordingly, the slopes of the angle α formed on both side surfaces of the protrusion are formed upward (h−ε) and downward (h) (in the direction of the disk substrate) from the center plane. Further, the shape of the side surface due to the inclination is not radial from the center of the disk, but is parallel to the edge line of the protrusion on the center plane and the width b.

  That is, the protrusions are arranged at the interval P, and the angle β of the protrusion edge line is defined as (interval angle θ between protrusions−gap angle γ between protrusions). Since the protrusion requires thickness (height), a reference surface is required. Here, the edge line of the protrusion is placed on the reference plane, and this plane is referred to as the above-described central plane. Since the protrusion requires an inclined surface, the center plane is virtually at a height (+ h) position on the disk C. Therefore, the surface of the disk C corresponds to a ridge of the protrusion. Further, the upper surface of the projection is at a position (h−ε) from the central plane, and from the disk C is at a position (2h−ε). When forming the protrusion, the width of the protrusion (upper surface width, heel width) varies depending on where the protrusion edge line angle β is placed. For example, when β is placed on the top surface, the ridges of the protrusions are only b wider than the top surface width, and when β is placed on the heel, the top surface is narrowed by b. The protrusion alone can be set anywhere, but it is impossible to place the protrusion C on the disk C while maintaining the protrusion interval angle θ. The center plane was used.

When the inclination angle of the protrusion is α, the input limit value is F, and the required spring pressing force is Q, the engagement of the clutch is as follows. Therefore, the pressing spring force may be set equal to Q. Therefore, when the input value F is large and F1, the disengagement direction force is Q1 from Formula (1), F1 is greater than F, and Q1 is greater than Q, so the clutch disengages. Conversely, if the input is stopped (F = 0) or the input is set to F2 smaller than F, the disengagement direction force becomes Q2 smaller than Q, so that the clutch is restored to the meshing state by the spring force of the spring.
Q = F · sin (α + φ) · cos (α + φ) ---- (1)
F: Limit input value Q: Removal direction force α: Protrusion inclination angle φ: Protrusion slope friction angle

  The drawings show an example in which the drive device of the present invention is applied to a butterfly valve. However, the present invention is not limited to this, and the same applies to other rotary valves such as a ball valve, and also to the rotary portion of other general valve drive devices. It can be applied to. In the figure, (1) shows a butterfly valve, and a manual actuator (3) comprising a gear transmission mechanism is connected to the outer end of the valve stem (2). The manual actuator (3) includes a worm wheel (4) connected to the outer end of the valve stem (2) and a worm (5) meshing with the worm wheel (4). The shaft (6) is connected. The handle wheel (7) is attached to the handle shaft (6) extending outward from the casing of the actuator (3) via the clutch mechanism (8) of the present invention.

  The clutch mechanism (8) includes a driving-side clutch member (9) and a driven-side clutch member (10), and both the clutch members (9) and (10) are substantially disc-shaped members. It can contact freely. On the contact surfaces of both members, the protrusions (11) are arranged along a plurality of circular trajectories at a predetermined interval. Then, the engagement or disengagement of the clutch members (9) and (10) is achieved by the engagement or disengagement of the protrusion (11), and the clutch mechanism is intermittently connected.

  The driving side clutch member (9) is integrally provided with a handle wheel (7), has a cup shape, and a guide cylinder (12) penetrating in the front-rear direction. The driven clutch member is integrally provided with a shaft insertion cylinder (13) for inserting the handle shaft (6) at the center thereof. The inner surface of the outer end portion of the shaft insertion cylinder (13) is formed at a corner portion where the corner portion (14) of the handle shaft (6) is engaged, and the driven side clutch member ( 10) is connected to the handle shaft 6 in a non-rotating state. In addition, an L-shaped slit (17) for connecting a spring fixing plate (15), which will be described later, to a retaining state is formed at the outer end of the shaft insertion cylinder. The guide tube (12) can be freely rotatably inserted into the outer periphery of the shaft insertion tube (13).

  The spring fixing plate (15) has a substantially disk shape, a bolt insertion hole (16) is drilled in the center, and a square bar-shaped connecting portion (18) extends laterally from the center of the inner surface to the tip. The cylindrical body is erected, and the bolt insertion hole (16) passes through the connecting portion (18). (19) is a spring having a predetermined resilience, which is a coil spring, but is not limited thereto. The spring (19) is extrapolated to the guide tube (12) via washers (20) arranged at both ends, and one end is received inside the cup-shaped driving side clutch member (9), and the other end is It is fixed with a spring fixing plate (15).

  In order to attach the clutch mechanism (8) to the handle shaft (6), first, the driving side clutch member (9) is loosely inserted into the outer periphery of the shaft insertion cylinder (13) of the driven side clutch member (10). Combine both parts. Next, as described above, while the spring (19) is compressed by the spring fixing plate (15), the connecting portion (18) is inserted into the L-shaped slit (17) of the driven clutch member (10). Engage it and connect it to the shaft insertion tube (13) of the driven clutch member in a locked state, and then screw the connecting bolt (21) inserted from the bolt insertion hole (16) into the tip of the handle shaft (6). Conclude. Thus, the clutch mechanism (8) including the handle wheel (7) is attached to the handle shaft (6).

  When the handle wheel (7) is manually rotated with a force equal to or less than a predetermined input value, the spring force of the spring (19) pushes the driving side clutch member (9) toward the driven side clutch member (10) and Since the projections (11) formed on both members are engaged with each other because they are biased in the abutting direction, the rotational force of the handle wheel is smoothly transmitted to the actuator (3) via the handle shaft (6). The valve stem (2) is rotated.

  When the handle wheel (7) is rotated with a force greater than a predetermined input value, the disengagement force due to the inclined surface of the protrusion (11) is greater than the spring force of the spring, so the protrusions (11) of both clutch members are disengaged. In this state, the clutch members (9) and (10) are relatively slid and the input transmission is interrupted. Thereafter, when the input is removed or lowered, the protrusion automatically returns to the meshing state due to the elastic force of the spring, and the conduction of the input is restored.

  In the illustrated embodiment, the inclination angle α of the protrusion is 20 °, the height of the protrusion is 1.2 mm, the height of the central plane is 0.45 mm from the upper surface, the protrusion width b is 3.482 mm, and the number of protrusions is 15. Yes, the gap ε was 0.375 mm.

Perspective view of butterfly valve and actuator Top view with actuator casing open Sectional drawing of the clutch mechanism concerning this invention Exploded perspective view An exploded perspective view seen from a different direction from FIG. Top view of protrusion Same perspective view Side view of protrusion The figure which shows meshing of the projection of the driving side and the driven side The figure which shows the state which the driving | running | working side rotated in FIG.

Explanation of symbols

(1) Butterfly valve
(2) Valve stem
(3) Actuator
(4) Worm wheel
(5) Warm
(6) Handle shaft
(7) Steering wheel
(8) Clutch mechanism
(9) Driving side clutch member
(10) Drive side clutch member
(11) Protrusion
(12) Guide tube
(13) Shaft insertion tube
(14) Corner
(15) Spring fixing plate
(16) Bolt insertion hole
(17) L-shaped slit
(18) Square bar connection
(19) Spring
(20) Washer
(21) Bolt

In other words, the protrusions are arranged at the interval P, and the angle β of the edge line of the protrusion is (interval angle θ / 2− the gap angle γ between the protrusions). Since the protrusion requires thickness (height), a reference surface is required. Here, the edge line of the protrusion is placed on the reference plane, and this plane is referred to as the above-described central plane. Since the protrusion requires an inclined surface, the center plane is virtually at a height (+ h) position on the disk C. Therefore, the surface of the disk C corresponds to a ridge of the protrusion. Further, the upper surface of the projection is at a position (h−ε) from the central plane, and from the disk C is at a position (2h−ε). When forming the protrusion, the width of the protrusion (upper surface width, heel width) varies depending on where the protrusion edge line angle β is placed. For example, when β is placed on the top surface, the ridges of the protrusions are only b wider than the top surface width, and when β is placed on the heel, the top surface is narrowed by b. The protrusion alone can be set anywhere, but it is impossible to place the protrusion C on the disk C while maintaining the protrusion interval angle θ. The center plane was used.

  The present invention relates to a drive device for a rotary valve, and more particularly, includes a clutch mechanism that intermittently transmits driving force, and when a driving force exceeding a certain value is input, the driving force is interrupted and an excessive input is applied. The present invention relates to a drive device that prevents damage to the device.

  Conventionally, as a driving device for a rotary valve such as a butterfly valve or a ball valve, a manual transmission is used to interpose a gear transmission mechanism consisting of a worm and a worm gear between a manually rotated handle wheel and a valve rod, and a valve rod with a manual driving force. The rotary valve drive device that rotates the valve to open and close the valve is known, and is disclosed in, for example, Japanese Patent No. 3081820.

  In such a known driving device, it is preferable that the output torque of the gear transmission mechanism manually provided and the valve driving torque output for driving the valve body from the gear transmission mechanism are matched, In practice, the input torque to the gear transmission mechanism is usually larger than the required valve drive torque. Moreover, in a manual device in which the input source is human power, the magnitude of the input torque has a very large individual difference, and an excessive force may be applied. For this reason, there is a risk of damage to the drive device including the handle wheel, the gear transmission mechanism, the casing, and the like.

  In particular, in recent years, with the demand for resource saving and cost reduction, the drive device has been reduced in size and the unnecessary strength of the material has been reduced, and the output limit value of the drive device has been made as close to the valve drive torque as possible. However, it cannot always be said that the input limit value is observed in the field where the valve is used. An accident that breaks has occurred.

Japanese Patent No. 3081820

  In the present invention, when an input exceeding the input limit value is applied, a clutch mechanism that interrupts input transmission is interposed between the manual drive source and the gear transmission mechanism to prevent transmission of force exceeding the input limit value. Power transmission means for preventing damage to the device due to excessive force application and for automatically restoring the force transmission when the input is less than the limit value so that the valve can be driven. It is to be provided.

The present invention relates to a driven side clutch member integrally connected to a handle shaft of a valve drive manual actuator of a rotary valve and a driving wheel integrally having a handle wheel and rotatably inserted into the driven side clutch member. constitute a clutch mechanism in the side clutch member, both clutches member formed in a substantially disk shape, projecting a projection that meshes with each other physician abutment surfaces of both clutch members, 該Tokki the center of the circle (O) has a trapezoidal cross section in the center circle (DC) extending radially from (O) and having a flat upper surface (A) and inclined surfaces (E) on both sides. , the balance between the separation force due to the resilient force of the spring and the collision force inclination angle (alpha), the input of more than Tokoro value is released coupling clutch mechanism when it is added via a hand wheel, the input value conversely The clutch mechanism is activated by the spring force of Held in sintered state, wherein the projection is a circle passing through the half the length of the radial direction centered yen projections (DC), height and gap of the protrusions from the bottom surface of the projection (C) Total of (epsilon) A plane that passes through the intersection of at least half the position and the center circle (DC) and is parallel to the bottom surface (C) is defined as a center plane (B), and the tilt angle (α) is tilted up and down from the center plane (B). The surface (E) is formed, and the inclined surface (E) is projected from the intersection of the center circle (DC) and the center plane (B) to the outer diameter (OD) side and inner diameter (ID) side (length direction) of the protrusion. And a gap (ε) between the inclined surfaces and the upper surface of the driving side and driven side projections .

The spring fixing plate is connected to the driven-side clutch member in a locked state by a square bar-shaped connecting portion that is detachably engageable with the L-shaped slit .

  According to the rotary valve drive device of the present invention, the clutch mechanism is interposed between the manual steering wheel and the gear transmission mechanism, so that the input torque exceeding a predetermined value is cut off to prevent excessive torque conduction. In addition, it is possible to prevent damage to the device due to the addition of excessive torque, and when the input torque drops below a predetermined value, the clutch mechanism is automatically returned to the connected state immediately to transmit the driving force. Therefore, the operation of the clutch mechanism does not require time and can be used as a safety mechanism. Furthermore, the present invention can be applied to the existing rotary valve only by attaching the clutch mechanism of the present invention to the handle shaft instead of the existing handle wheel.

  Preferred embodiments of the present invention will be described in detail below. The present invention relates to a manual drive device for a rotary valve having a rotating valve element such as a butterfly valve, a ball valve, etc., and a manual rotation means such as a handle wheel for generating a manual input; A clutch mechanism for intermittently transmitting power is arranged between the power transmission means such as a gear transmission mechanism for transmitting the driving force of the moving means to the valve rod for opening and closing the valve, and an excessive driving force exceeding a predetermined value is provided. When transmitted, the transmission is cut off to prevent damage to the driving force transmission mechanism such as the gear transmission mechanism, the gear case, the connection portion between the handle shaft and the handle wheel, and the connection portion between the valve stem and the gear transmission mechanism. It is characterized by doing so. Further, the clutch mechanism is characterized in that when the input drops below a predetermined value, the clutch mechanism is automatically restored and the driving force is reconnected. Furthermore, the drive device according to the present invention can be realized by a simple change by simply attaching to the handle shaft instead of the existing handle wheel, and does not require any special parts, tools or tools, so that the pipe is already installed. It is also possible to easily apply to a rotary valve attached to.

  The clutch mechanism includes at least one protrusion arranged on the driving side and the driven side clutch members along the rotation locus and meshing with each other. The two clutch plates are always repelled in the direction of contact, and the surface facing the rotation direction of the protrusion is formed as an inclined surface having a predetermined inclination angle α, and the input value from the driving side clutch member is a predetermined value. When the value is exceeded, the detachment force due to the inclination angle α becomes larger than the elastic pressing force against the clutch member, so that the engagement of the protrusion is released and the driving force transmission is interrupted. Further, when the input returns to zero or below a certain value, the clutch member is pressed by the elastic force, so that the engagement of the protrusion is restored and the transmission of the driving force is restored. That is, when the input applied to the driving side is greater than or equal to a certain value or less than the certain value, the clutch is automatically engaged, and the driving force can be transmitted or disconnected. The inclination angle may be provided only on one side surface of the protrusion in the rotation direction, but by forming it on both side surfaces, the clutch can be engaged and disengaged in both forward and reverse rotation directions. .

  The driving-side clutch member is a substantially disk-shaped member integrated with the handle wheel, and is rotatably inserted into the handle shaft that is the input shaft of the gear transmission mechanism. The clutch member on the driven side is a disk-like member that is coupled so as to rotate integrally with the handle shaft. Protrusions that mesh with each other are formed on opposing contact surfaces of both clutch members. The engagement or disengagement of both clutch members is achieved by meshing or disengaging. The driving-side and driven-side clutch members receive the elastic force of the spring stretched between the two members, and are normally biased in the direction in which they abut against each other. Be ranked. When the input value exceeds a certain value, a separation force due to the inclination angle α is generated, the protrusion slides along the inclination, the meshing is released against the spring force of the spring, and both clutch members are in the non-connected state. Transition.

As shown in FIGS. 6 to 8, at least one protrusion is arranged along a circular locus centering on the handle shaft, preferably at a predetermined angle θ, and has a certain length L in the diameter direction. The outer peripheral side is wide, and the inner peripheral side is narrow and has a trapezoidal shape. Referring to FIG. 8, the side surfaces, preferably both side surfaces, of the protrusion are formed on the inclined surface having the inclination angle α. When providing an inclination angle on both side surfaces of the protrusion, it is possible to make the input value different according to the rotation direction by making one inclination angle different from that of the other. The inclination angle α is preferably 5 to 40 °. If the inclination angle is less than 5 °, the detachment force becomes too small to substantially achieve the detachment of the protrusion, and the clutch action cannot be obtained. On the other hand, if the angle is larger than 40 °, there is an inconvenience that the protrusion is detached even if the input is small. The number N of protrusions is about 1 to 30, and the protrusion interval angle θ is given by θ = 360 / N.

The distance P between the protrusions on the driving side and the driven side is given by the following equation when the diameter of the central circle passing through the center of the length L of the protrusion is DC.

P = πDC / 2N

As shown in FIGS. 9 and 10, protrusions are arranged at equal intervals on both the driving side and the driven side, and a gap ε is provided in the protrusions shown in FIG. 8 in order to facilitate engagement and disengagement of the protrusions. When the width of the protrusion is b, the gap ε is preferably about 0.05 to 0.3b. The gap ε is provided on the inclined surface and the upper surface of the protrusion. Thus, the distance P between the protrusions is a value of the following formula.

P = 2 × (b + ε)

In order to establish the engagement and disengagement of the protrusion, the inclination angle α on both side faces of the protrusion is not raised from the upper surface of the disk at the lower end of the protrusion, but at the center above the height of the protrusion. They are formed vertically from the plane (see FIG. 8). That is, the clutch mechanism is configured to mesh on a central plane that is half the height of the protrusion including the gap ε. Therefore, the slopes of the angle α formed on both side surfaces of the protrusion are formed upward (h−ε) and downward (h) (in the direction of the disk substrate) from the center plane. Further, the shape of the side surface due to the inclination is not radial from the center of the disk, but is parallel with the ridge line angle (β) of the protrusion on the center plane and the width b.

That is, the protrusions are arranged at the interval P, and the angle of the ridge line of the protrusion is β . Since the protrusion requires thickness (height), a reference surface is required. Here, the ridge line of the protrusion is placed on the reference plane, and this plane is referred to as the above-described central plane. Since the protrusion requires an inclined surface, the center plane is virtually at a height (+ h) position on the disk C. Therefore, the surface of the disk C corresponds to a ridge of the protrusion. Further, the upper surface of the projection is at a position (h−ε) from the central plane, and from the disk C is at a position (2h−ε). When forming the protrusion, the width of the protrusion (upper surface width, heel width) varies depending on where the protrusion ridge line angle β is placed. For example, placing the β on the upper surface, the foot of the projection becomes large as b from the upper surface width, top placing the β at the foot is b only narrow. The projections alone, but where it is possible at a reference to, to place while maintaining the projection interval angle θ on a circle plate C are the possible with top or foot basis, the formation criterion projection ridge The center plane was used.

When the inclination angle of the protrusion is α, the input limit value is F, and the required spring pressing force is Q, the engagement of the clutch is as follows. Therefore, the pressing spring force may be set equal to Q. Therefore, when the input value F becomes large F _1, removing direction force from equation (1) is Q1 becomes, F ₁ is larger than F, Q ₁ is to become larger than Q, the clutch is disengaged. Conversely, if the input is stopped (F = 0) or the input is set to F ₂ smaller than F, the disengagement direction force becomes Q ₂ smaller than Q, so the clutch is restored to the meshing state by the spring force of the spring. To do.

Q = F · sin (α + φ) · cos (α + φ) ---- (1)

F: Limit input value Q: Removal direction force α: Protrusion inclination angle φ: Protrusion slope friction angle

  The drawings show an example in which the drive device of the present invention is applied to a butterfly valve. However, the present invention is not limited to this, and the same applies to other rotary valves such as a ball valve, and also to the rotary portion of other general valve drive devices. It can be applied to. In the figure, (1) shows a butterfly valve, and a manual actuator (3) comprising a gear transmission mechanism is connected to the outer end of the valve stem (2). The manual actuator (3) includes a worm wheel (4) connected to the outer end of the valve stem (2) and a worm (5) meshing with the worm wheel (4). The shaft (6) is connected. The handle wheel (7) is attached to the handle shaft (6) extending outward from the casing of the actuator (3) via the clutch mechanism (8) of the present invention.

  The clutch mechanism (8) includes a driving-side clutch member (9) and a driven-side clutch member (10), and both the clutch members (9) and (10) are substantially disc-shaped members. It can contact freely. On the contact surfaces of both members, the protrusions (11) are arranged along a plurality of circular trajectories at a predetermined interval. Then, the engagement or disengagement of the clutch members (9) and (10) is achieved by the engagement or disengagement of the protrusion (11), and the clutch mechanism is intermittently connected.

  The driving side clutch member (9) is integrally provided with a handle wheel (7), has a cup shape, and a guide cylinder (12) penetrating in the front-rear direction. The driven clutch member is integrally provided with a shaft insertion cylinder (13) for inserting the handle shaft (6) at the center thereof. The inner surface of the outer end portion of the shaft insertion cylinder (13) is formed at a corner portion where the corner portion (14) of the handle shaft (6) is engaged, and the driven side clutch member ( 10) is connected to the handle shaft 6 in a non-rotating state. In addition, an L-shaped slit (17) for connecting a spring fixing plate (15), which will be described later, to a retaining state is formed at the outer end of the shaft insertion cylinder. The guide tube (12) can be freely rotatably inserted into the outer periphery of the shaft insertion tube (13).

  The spring fixing plate (15) has a substantially disk shape, a bolt insertion hole (16) is drilled in the center, and a square bar-shaped connecting portion (18) extends laterally from the center of the inner surface to the tip. The cylindrical body is erected, and the bolt insertion hole (16) passes through the connecting portion (18). (19) is a spring having a predetermined resilience, which is a coil spring, but is not limited thereto. The spring (19) is extrapolated to the guide tube (12) via washers (20) arranged at both ends, and one end is received inside the cup-shaped driving side clutch member (9), and the other end is It is fixed with a spring fixing plate (15).

  In order to attach the clutch mechanism (8) to the handle shaft (6), first, the driving side clutch member (9) is loosely inserted into the outer periphery of the shaft insertion cylinder (13) of the driven side clutch member (10). Combine both parts. Next, as described above, while the spring (19) is compressed by the spring fixing plate (15), the connecting portion (18) is inserted into the L-shaped slit (17) of the driven clutch member (10). Engage it and connect it to the shaft insertion tube (13) of the driven clutch member in a locked state, and then screw the connecting bolt (21) inserted from the bolt insertion hole (16) into the tip of the handle shaft (6). Conclude. Thus, the clutch mechanism (8) including the handle wheel (7) is attached to the handle shaft (6).

  When the handle wheel (7) is manually rotated with a force equal to or less than a predetermined input value, the spring force of the spring (19) pushes the driving side clutch member (9) toward the driven side clutch member (10) and Since the projections (11) formed on both members are engaged with each other because they are biased in the abutting direction, the rotational force of the handle wheel is smoothly transmitted to the actuator (3) via the handle shaft (6). The valve stem (2) is rotated.

  When the handle wheel (7) is rotated with a force greater than a predetermined input value, the disengagement force due to the inclined surface of the protrusion (11) is greater than the spring force of the spring, so the protrusions (11) of both clutch members are disengaged. In this state, the clutch members (9) and (10) are relatively slid and the input transmission is interrupted. Thereafter, when the input is removed or lowered, the protrusion automatically returns to the meshing state due to the elastic force of the spring, and the conduction of the input is restored.

In the illustrated embodiment, the inclination angle α of the protrusion is 20 °, the height of the protrusion is 1.2 mm, the height of the central plane is 0.75 mm from the bottom , the width b of the protrusion is 3.482 mm, and the number of protrusions is 15. And the gap ε was set to 0.3 mm.

Perspective view of butterfly valve and actuator Top view with actuator casing open Sectional drawing of the clutch mechanism concerning this invention Exploded perspective view An exploded perspective view seen from a different direction from FIG. Top view of protrusion Same perspective view Side view of protrusion The figure which shows meshing of the projection of the driving side and the driven side The figure which shows the state which the driving | running | working side rotated in FIG.

Explanation of symbols

(1) Butterfly valve
(2) Valve stem
(3) Actuator
(4) Worm wheel
(5) Warm
(6) Handle shaft
(7) Steering wheel
(8) Clutch mechanism
(9) Driving side clutch member
(10) Drive side clutch member
(11) Protrusion
(12) Guide tube
(13) Shaft insertion tube
(14) Corner
(15) Spring fixing plate
(16) Bolt insertion hole
(17) L-shaped slit
(18) Square bar connection
(19) Spring
(20) Washer
(21) Bolt

Claims (8)

  When the handle wheel is attached to the handle shaft of the manual actuator for driving the valve of the rotary valve via the clutch mechanism and an input exceeding a predetermined value is added via the handle wheel, the clutch mechanism is disconnected and the input is The rotary valve driving device is characterized in that the clutch mechanism is in a connected state when the input value is less than or equal to a predetermined value so as not to be transmitted to the shaft.   2. The driving device according to claim 1, wherein the clutch mechanism is intermittently engaged by a balance between a spring repulsive force and a disengagement force due to an inclination angle of a protrusion formed on a contact surface of both clutch members. .   The clutch mechanism is composed of a driven side clutch member that is coupled to the handle shaft with the rotation direction integrated, and a driving side clutch member that has an integrated handle wheel and is rotatably inserted into the driven side clutch member. 3. The drive device according to claim 1, wherein at least one engaging meshing projection is provided on the contact surface of the clutch member, and both clutch members are springed in the contact direction by a spring.   4. The driving device according to claim 1, wherein an inclination angle of the inclined surface of the protrusion is in a range of 5 to 40 [deg.].   5. The driving device according to claim 1, wherein the inclined surface of the protrusion is formed from a central plane that is at least half of the height of the protrusion, and the protrusions mesh with each other in the central plane. .   4. The driving apparatus according to claim 3, wherein a spring fixing plate on which one end of the spring is stretched is fixed from the outer surface of the driving side clutch member to the tip of the handle shaft.   7. The driving apparatus according to claim 6, wherein the spring fixing plate is connected to the driven clutch member in a non-stop state. 8. The driving device according to claim 1, wherein the inclined surface of the protrusion is formed on both side surfaces of the protrusion so that the clutch mechanism operates regardless of whether the steering wheel is rotated in the forward or reverse direction.

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