JP6403519B2 - Spring closed tide gate - Google Patents

Description

  The present invention relates to a spring-closed tide gate.

  Conventionally, it has been installed at the opening of a tide (breakwater) levee, etc., and it can be opened and closed manually or electrically to open the opening during normal times and close the opening during the tide to prevent intrusion of tsunami and storm surge There is a (breakwater) gate.

  Such a tide gate is one that is manually or electrically driven to open and close. In particular, a manual closing drive operation is extremely dangerous depending on the situation in the field. Moreover, there is a possibility that the electric closed drive operation cannot be performed due to the loss of the power supply accompanying the earthquake.

  Then, what closes a tide gate with the motor which uses compressed gas as a motive power source is proposed so that it may not depend on a power supply (refer patent document 1).

  Moreover, what closes a tide gate with the cylinder which uses nitrogen gas as a motive power source is proposed (refer patent document 2).

JP2013-144919A JP 2013-119742 A

  However, in any of the background arts, it is necessary to install a compressed gas cylinder and a motor, a nitrogen gas cylinder and a cylinder, and the equipment becomes large. Moreover, since these cylinders require frequent maintenance, there is a problem that the equipment cost and running cost are very high.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a spring-closed tide gate that can reduce the facility cost and running cost.

In order to solve the above-mentioned problem, the spring-closed tide gate of the present invention is provided in an opening of a tide bank or the like, and is manually opened so that the opening is normally opened and the opening is closed during tide. Or a tide gate that can be opened electrically, and a spring that automatically closes the tide gate with a spring force, and a locking member that locks the spring charged with the opening force of the tide gate; And a speed adjusting mechanism that adjusts the speed when the tide gate is driven to be closed with respect to the spring, and the locking member is any of manual operation, electric operation, and water level detection operation by float or it is one in unlocking, the speed control mechanism is provided with a crown gear coupled to said drive shaft, and a pendulum speed adjusting weights having a contact capable claw portion sawtooth of the crown gear, Serial weights Ru stopped applied in the locking member.

  According to the present invention, the opening of the tide gate can be performed manually or electrically because it is in a state where safety or power feeding is possible. The spring is charged by the opening driving force of the tide gate and is locked by the locking member.

  When the tide gate is in a safe or power-supplyable condition, the tide gate is automatically closed by spring force by simply releasing the locking member manually or electrically. Will come to be.

  On the other hand, if the manual operation is extremely dangerous due to a tsunami or storm surge, or if the power supply for electric operation is lost, even if neither manual operation nor electric operation is possible, the tsunami or storm surge water level detection operation by float The locking member is automatically unlocked. As a result, the tide gate is automatically closed by the spring force.

  Thus, the tide gate can be driven to close by the spring force of the spring charged (accumulated) by the opening driving force of the tide gate and released (released) by the locking release operation of the locking member. Therefore, basically, it is only necessary to provide a spring, so that it is not necessary to install cylinders, motors, cylinders, etc. as in the background art, and the equipment becomes very simple. Moreover, since maintenance of the spring does not need to be performed frequently, the equipment cost and running cost are very low.

Further , since the closing drive speed by the spring force of the tide gate can be adjusted and the closing drive can be performed at a relatively low speed, the safety is improved.
Further, the speed control mechanism uses a crown gear and a pendulum type speed adjustment weight with a claw, and is mechanical, so that the reliability of speed control is improved over a long period of time.

  The tide gate is a horizontal pulling gate, and can be configured to be opened and closed via a rack and a pinion, or a chain and a sprocket.

  According to this configuration, if the tide gate is a horizontal pulling gate and is opened and closed via a rack and pinion or a chain and sprocket, the reliability of the opening and closing drive can be improved over a long period of time.

  The spring may be a plurality of torsion coil springs or a spring.

  According to this configuration, if a torsion coil spring or a spring is used as the spring, the reliability of the spring force is improved over a long period of time.

  The pendulum type speed adjusting weight can be configured such that the position of the weight from the center of the pendulum can be changed.

  According to this configuration, by changing the position of the weight from the center of the pendulum, it is possible to change the closed drive speed to match the situation at the site.

  According to the present invention, by using the spring-closed tide gate, the facility cost and running cost are very low.

BRIEF DESCRIPTION OF THE DRAWINGS It is a tide bank provided with the spring closed drive type tide gate concerning this invention, (a) is a top view, (b) is a front view. (A) is a side view of FIG.1 (b), (b) is a plane sectional view of a torsion coil spring part. It is a top view of a drive device. It is a front view of a drive device. (A) is the II sectional view taken on the line of FIG. 4, (b) is the II-II sectional view taken on the line of (a). It is a speed control mechanism, (a) is a rear view, (b) is a side view. (A) is a top view which shows pendulum-like turning of a weight, and movement position adjustment, (b) is a top view which shows the relationship between the serrated gear part of a crown gear, an upper nail | claw, and a lower claw. (A)-(c) is a top view for demonstrating the relationship between the serrated gear part of a crown gear, an upper nail | claw, and a lower nail | claw, and a relationship with a weight. (A) (b) is a top view for demonstrating the relationship between the sawtooth-shaped gear part of a crown gear, an upper nail | claw, and a lower nail | claw, and a relationship with a weight. (A) (b) is a side view explaining operation which cancels | releases the latching of the weight by a latching member manually. (A) (b) is a side view explaining operation which cancels | releases latching of the weight by a latching member electrically. (A) (b) is a side view explaining operation which cancels | releases locking of the weight by a locking member by water level detection.

  Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings. FIG. 1 shows a tide bank provided with a spring-closed tide gate, where (a) is a plan view and (b) is a front view. FIG. 2A is a side view of FIG.

  The seawall 1 is provided with an opening 2 that leads to the sea side and the land side, and people, cars, and the like can freely come and go through the opening 2 in normal times.

  A depression 1a extending in the length direction of the tide embankment 1 is formed on the sea side of the tide embankment 1, and a horizontally extending gate 3 that opens and closes the opening 2 can be traversed in the depression 1a. Has been placed.

  Wheels 4 that roll along rails 7 [see FIG. 2 (a)] laid on the lower surface of the seawall 1 are respectively provided at the lower portions on both sides of the transverse gate 3 in the transverse direction. A rack 5 extending over the entire length is attached to the upper surface of the horizontal pulling gate 3.

  A plurality of guide rollers 6 that hold both side surfaces of the rack 5 of the horizontal pulling gate 3 are attached to the upper surface 1 b of the seawall 1. The guide roller 6 is in a closed position of the horizontal pulling gate 3 (see the solid line in FIG. 1), and holds two sides in the transverse direction, and an open position of the horizontal pulling gate 3 (see the two-dot chain line in FIG. 1). ) And are attached to a total of four locations, including two locations that hold both sides in the transverse direction.

  The lateral pulling gate 3 is smoothly traversed by the wheels 4 and the rails 7, the rack 5 and the guide rollers 6 to open and close the opening 2.

  A driving device 10 for the horizontal pulling gate 3 is installed on the upper surface 1b of the seawall 1 corresponding to approximately the middle of the open / closed position of the horizontal pulling gate 3.

  FIG. 3 is a plan view of the driving device 10, and FIG. 4 is a front view of the driving device 10. FIG. 5A is a cross-sectional view taken along the line II of FIG.

  A front panel 12a and a rear panel 12b are erected in parallel on a substrate 11 installed on the upper surface 1b of the seawall 1, and a drive shaft 14 is supported by bearings 13a and 13b of both panels 12a and 12b. .

  A pinion 15 that meshes with the rack 5 is attached to the front end of the drive shaft 14, and the pinion 15 is rotated about the hour hand a in FIG. Driven open. On the contrary, the horizontal pulling gate 3 is driven to be closed via the rack 5 by being rotated around the counter hour hand b. Instead of opening / closing driving by the rack 5 and the pinion 15, opening / closing driving by a chain and a sprocket can be used.

  An electric motor 16 having a speed reducer 17 is installed on the upper surface 1 b of the seawall 1 located on the right side of the substrate 11. An electric / manual switching device 18 is interposed between the speed reducer 17 and the electric motor 16, and a manual handle 19 is attached to the electric / manual switching device 18.

  A sprocket 21 is attached to the output shaft 17 a of the speed reducer 17 via a one-way clutch 20, and the sprocket 21 and the sprocket 22 of the drive shaft 14 are connected by a chain 23.

  Then, the electric / manual switching device 18 is switched to “electric”, and the sprocket 21 of the output shaft 17a of the speed reducer 17 is rotated around the hour hand a in FIG. As a result, the pinion 15 is rotated around the hour hand a via the chain 23 and the sprocket 22, and the horizontal pulling gate 3 is driven to open leftward by the electric force via the rack 5. At this time, the drive shaft 14 is also rotated around the hour hand a together with the pinion 15.

  Further, the electric / manual switching device 18 is switched to “manual”, and the sprocket 21 of the output shaft 17 a of the speed reducer 17 is rotated around the hour hand a by the manual handle 19. As a result, the pinion 15 is rotated around the hour hand a via the chain 23 and the sprocket 22, and the horizontal pulling gate 3 is driven to open leftward by manual force via the rack 5. At this time, the drive shaft 14 is also rotated around the hour hand a together with the pinion 15.

  Here, the one-way clutch 20 can rotate the sprocket 21 of the output shaft 17a of the speed reducer 17 around the hour hand a by the electric force of the electric motor 16 or the manual force of the manual handle 19, that is, the lateral pulling gate 3 can be driven to open. Is set to As will be described later, when the pinion 15 is rotated together with the drive shaft 14 around the counter-clockwise hand b in FIG. 3B, the sprocket 21 is idled with respect to the output shaft 17a via the sprocket 22 and the chain 23. Is set to

  Spring shafts 27 are supported at a plurality of locations (four locations in this example) around the drive shaft 14 of the substrate 11 by bearings 26a and 26b of the front panel 12a and the rear panel 12b. Gears 29 that engage with the gears 28 of the drive shaft 14 are attached to the front ends of the spring shafts 27 as shown in FIG.

  A torsion coil spring 30 is wound around each spring shaft 27, and as shown in FIG. 2B, the rear end 30a of each torsion coil spring 30 is locked in the hole of the rear panel 12b, and the front end 30b. Is locked in the hole of the gear 29. It is also possible to use a spring spring in place of the torsion coil spring 30.

  When the pinion 15 is rotated around the hour hand a by the electric force or the manual force described above and the horizontal pulling gate 3 is driven to open, the drive shaft 14 is also rotated around the hour hand a by the rotation of the pinion 15. The At this time, as shown in FIG. 5B, the gears 28 of the drive shaft 14 are rotated by the gears 28 of the spring shaft 27 around the counter-clockwise hand b so that the spring force of each torsion coil spring 30 is charged (stored). ).

  On the side of the spring shaft 27 of the substrate 11, the speed control shaft 33 of the speed control mechanism 31 is supported by the bearings 32 a and 32 b of the front panel 12 a and the rear panel 12 b.

  6A and 6B show the speed adjusting mechanism 31, in which FIG. 6A is a rear view and FIG. 6B is a side view of FIG. A small diameter gear 34 is attached to the rear portion of the speed control shaft 33, and this gear 34 meshes with a large diameter gear 35 at the rear end of the drive shaft 14. The gear ratio between the small diameter gear 34 and the large diameter gear 35 is set to, for example, 1: 2, and the small diameter gear 34 is doubled with respect to the large diameter gear 35. The speed increase may be three times or more.

  A large-diameter crown gear 39 is attached to the rear end of the speed control shaft 33, and a plurality of (11 odd-numbered in this example) sawtooth gear portions 39 a are formed on the rear surface of the crown gear 39. ing.

  As shown in FIG. 6A, when the gear 35 of the drive shaft 14 is rotated around the hour hand a, the gear 34 of the speed adjusting shaft 33 is rotated around the counter hour hand b. As shown in FIG. 7B, the sawtooth gear portion 39a of the crown gear 39 that rotates together with the speed adjusting shaft 33 has a sawtooth shape such that the rising end surface portion 39c precedes and the inclined surface portion 39b follows the counterclockwise hand rotation b. The shape is set.

  A claw vertical shaft 36 facing the sawtooth gear portion 39a of the crown gear 39 is supported by upper and lower bearings 37a and 37b. The claw vertical shaft 36 is engaged with the upper claw 38 a that engages with the serrated gear portion 39 a at the top of the crown gear 39, and is engaged with the serrated gear portion 39 a at the lower portion of the crown gear 39. A lower claw 38b is attached.

  Since the sawtooth gear portion 39a is set to an odd number, when the upper claw 38a comes into contact with the rising end surface portion 39c of the sawtooth gear portion 39a (see FIG. 8A), the lower claw 38b has a sawtooth shape. It will be in the state which removed from the standup end face part 39c of gear part 39a. Conversely, when the lower claw 38b comes into contact with the rising end surface portion 39c of the sawtooth gear portion 39a (see FIG. 8C), the upper claw 38a is in a state of being disengaged from the rising end surface portion 39c of the sawtooth gear portion 39a.

  Therefore, as shown in FIGS. 8A to 9A, when the crown gear 39 rotates around the counterclockwise hand b, the upper claw 38a and the lower claw 38b are formed on the rising end surface portion 39c of the sawtooth gear portion 39a. It will contact alternately. Thus, the claw vertical shaft 36 is reciprocally rotated c and d in small increments.

  Further, when the claw vertical shaft 36 is manually rotated by approximately 90 degrees (neutral position N) as shown by an arrow e in FIG. 9B, both the upper claw 38a and the lower claw 38b are sawtooth gear portions 39a. It does not come into contact with the rising end surface portion 39c.

  A weight shaft 40 is attached to the upper end of the claw vertical shaft 36 in a direction orthogonal to the axis, and a sleeve-like pendulum type speed adjusting weight (weight) 41 is movable in the axial direction on both shaft portions of the weight shaft 40. Is fitted. As indicated by a two-dot chain line in FIG. 7A, the claw vertical shaft 36 rotates while rotating each weight 41 in a pendulum shape.

  As each weight 41 is moved outward from the center (pendulum center) of the weight shaft 40 as shown in FIG. 7 (a), the rotational force of the vertical nail shaft 36 becomes heavier, and the more it moves inward, The rotational force of the nail vertical shaft 36 is reduced. As will be described later, when the rotational force of the claw vertical shaft 36 becomes heavy, the crown gear 39 is adjusted so as to slow down the rotation, and when the rotational force of the claw vertical shaft 36 becomes lighter, the rotation of the crown gear 39 rotates. Will be controlled to become faster.

  Each weight 41 is fixed to the weight shaft 40 with a bolt or the like at that position after adjusting the moving position in relation to the closing speed of the horizontal pulling gate 3.

  As shown in FIGS. 6A and 6B, an intermediate portion of an inverted L-shaped locking member 43 is attached to the horizontal panel 12 c of the substrate 11 so as to be rotatable up and down by a support shaft 44. The distal end portion 43a of the locking member 43 extends in the direction of the weight 41 on one side (left side in FIG. 1), and stops the weight 41 when rotating upward. As a result, the claw vertical shaft 36 cannot reciprocate c and d.

  As shown in FIGS. 10A and 10B, an upper limit stopper 42a for restricting the upper rotation position of the locking member 42 and a lower limit stopper 42b for restricting the lower rotation position are provided. Further, a lower limit stopper 42c of a float locking member 46 described later is provided.

  In this state, as shown in FIG. 3A, either the upper claw 38a or the lower claw 38b locks the rising end surface portion 39c of the sawtooth gear portion 39a of the crown gear 39. 39 also cannot rotate around the counter hour hand b.

  The upper end portion of the locking member 43 is a manual operation portion 43b. When the manual operation portion 43b is rotated counterclockwise as shown by an arrow f as shown in FIGS. 10 (a) and 10 (b), the weight 41 by the distal end portion 43a. Will be released.

  On the support shaft 44 of the locking member 43, an electric locking member 45 is attached on the inner side of the locking member 43, and a float locking member 46 is coaxially attached to the outer side so as to be rotatable up and down.

  The electric locking member 45 is formed with a hook portion 45 a that protrudes to the left in plan view of FIG. 3 and faces the upper edge of the distal end portion 43 a of the locking member 43. As shown in FIGS. 11A and 11B, an electric cylinder 47 is connected to the electric locking member 45. When the electric locking member 45 is rotated counterclockwise by the driving of the electric cylinder 47, the hook portion 45a rotates the locking member 43 counterclockwise as shown by the arrow f, so that the weight 41 is not locked by the distal end portion 43a. Become so.

  The float locking member 46 is formed with a hook portion 46 a that protrudes rightward in a plan view of FIG. 3 and faces the upper edge of the distal end portion 43 a of the locking member 43. As shown in FIGS. 12A and 12B, the float locking member 46 is connected to a float 48 of a seawater channel 50 communicating with the sea side. When the water level L2 rises from the normal water level L1 due to a storm surge or a tsunami, the float 48 naturally rises. Along with this, when the float locking member 46 is rotated counterclockwise via the rod 49, the hook portion 46a rotates the locking member 43 counterclockwise as indicated by the arrow f, so that the weight 41 is stopped by the tip portion 43a. Will be released.

  As described above, the weight 41 is stopped by the locking member 43 by any one of a manual operation of the locking member 43, an electric operation of the locking member 43 by the electric cylinder 47, and a water level detection operation of the locking member 43 by the float 48. The lock can be released with only one.

  In the case of the spring-closed tide gate as described above, the laterally-driven gate (tide tide gate) 1 is open safely or in a power-supplyable state, so it is manually operated by the manual handle 19 or by the electric motor 16. It can be done electrically.

  When the lateral pulling gate 3 is driven to open through the pinion 15 and the rack 5, the spring of each torsion coil spring 30 is driven through the gear 28 of the drive shaft 14 of the pinion 15 and the gear 29 of the spring shaft 27. Power is charged.

  At this time, the crown gear 39 is also rotated together with the speed control shaft 33 via the large diameter gear 35 of the drive shaft 14 and the small diameter gear 34 of the speed control shaft 33. At this time, as shown in FIG. 9B, the weight 41 is pushed as shown by an arrow e, and the nail vertical shaft 36 is temporarily held at the neutral position N rotated by approximately 90 degrees. Thereby, since both the upper claw 38a and the lower claw 38b do not contact the rising end surface portion 39c of the sawtooth gear portion 39a, the crown gear 39 rotates smoothly.

  When the horizontal pulling gate 3 is fully opened, the torsion coil spring 30 is fully charged by this opening driving force.

  Thereafter, the nail vertical shaft 36 temporarily held at the neutral position N is rotated back to the position shown in FIG. 8B in the opposite direction at approximately 90 degrees by pushing back the weight 41. At this position, the locking member 43 is rotated. Rotate up. Thereby, since the front-end | tip part 43a of the latching member 43 stops the weight 41, the vertical axis | shaft 36 for nail | claws stops.

  Here, when the open driving of the horizontal pulling gate (tide gate) 1 by manual or electric operation is stopped, the horizontal pulling gate (tide gate) 1 is moved through the pinion 15 and the rack 5 by the spring force of the torsion coil spring 30. It tries to be closed.

  However, since the tip 43a of the locking member 43 stops the weight 41 and the claw vertical shaft 36 does not rotate, either the upper claw 38a or the lower claw 38b is brought into contact with the rising end surface 39c of the sawtooth gear 39a. It comes into contact. Accordingly, since the rotation of the crown gear 39 is prevented, the rotation of the drive shaft 14 of the pinion 15 is also prevented, so that the lateral pulling gate 3 is not driven to be closed. That is, the torsion coil spring 30 is charged by the opening driving force of the lateral pulling gate 3 and is locked by the locking member 43.

  Then, when the lateral pulling type gate 3 is in a safe or power-supplyable state, if the manual operation portion 43b of the locking member 43 is manually turned counterclockwise as shown in FIG. The holding of the weight 41 due to is released.

  As a result, the crown gear 39 can be rotated, so that the driving shaft 14 rotates counterclockwise b by the spring force of the torsion coil spring 30, and the lateral pulling gate 3 is spring-loaded through the pinion 15 and the rack 5. It is automatically closed by force.

  Further, when the electric cylinder 47 is driven by a remote operation or the like, the electric locking member 45 is rotated left and the locking member 43 is rotated left. In this manner, similarly, the weight 41 is released from being stopped, and the lateral pulling gate 3 is automatically driven to close by the spring force.

  On the other hand, if manual operation is extremely dangerous due to a tsunami or storm surge, or if the power source for electric operation is lost, either manual or electric operation may not be possible.

  In such a case, when the water level L2 rises from the normal water level L1 due to a storm surge or tsunami, the float 48 naturally floats, and the float locking member 46 is rotated counterclockwise via the rod 49. Then, the locking member 43 is rotated counterclockwise. In this manner, similarly, the weight 41 is released from being stopped, and the lateral pulling gate 3 is automatically driven to close by the spring force.

  In this way, the lateral pulling gate 3 is charged (accumulated) by the opening driving force of the lateral pulling gate 3 and released (released) by the unlocking operation of the locking member 43 by the spring force of the torsion coil spring 30. Can be driven to close. Therefore, basically, it is only necessary to provide the torsion coil spring 30, so that installation of cylinders, motors, cylinders and the like as in the background art becomes unnecessary, and the facility becomes extremely simple. In addition, since the maintenance of the torsion coil spring 30 does not need to be performed frequently, the equipment cost and running cost are very low.

  Further, a speed adjusting mechanism 31 is provided for the torsion coil spring 30 to adjust the speed when the lateral pulling gate 3 is driven to close.

  That is, when the crown gear 39 is rotated counterclockwise by the spring force b, the upper claw 38a and the lower claw 38b are alternately brought into contact with the rising end surface portion 39c of the serrated gear portion 39a, whereby the claw vertical shaft 36 Is reciprocally rotated c and d in small increments.

  At this time, the claw vertical shaft 36 reciprocates c and d while turning the respective weights 41, so that resistance is imparted to the rotation of the crown gear 39. Therefore, the closing drive speed by the spring force of the lateral pulling gate 3 is adjusted, and the closing drive can be performed at a relatively low speed, so that safety is improved.

  Moreover, the pendulum type speed adjustment weight 41 can be adjusted so that the rotation of the crown gear 39 is slow or fast by changing the position of the weight 41 from the pendulum center which is the center of the weight shaft 40. . Therefore, it is possible to change the lateral pulling gate 3 to a closed drive speed that matches the situation at the site. The speed control mechanism 31 is not limited to such a model, and may be a speed control mechanism using a centrifugal brake, a fan brake, or the like.

  Further, if the tide gate is a horizontal pulling gate 3 and is opened and closed via the rack 5 and the pinion 15 or the chain and the sprocket, the reliability of the opening and closing drive can be improved over a long period of time.

  Further, if the torsion coil spring 30 or the mainspring spring is used as the spring, the reliability of the spring force is improved over a long period of time.

  Further, if the crown gear 39 and the pendulum type speed adjustment weight 41 with the claw portions 38a and 38b are used as the speed control mechanism 31, since it is a mechanical type, the reliability of the speed control is improved over a long period of time. Will come to do.

1 Breakwater 2 Opening 3 Horizontal pulling gate (tide gate)
5 rack 10 drive device 14 drive shaft 15 pinion 16 electric motor 18 electric / manual switching device 19 manual handle 27 spring shaft 30 torsion coil spring 31 speed control mechanism 33 speed control shaft 36 claw vertical shaft 38a upper claw 38b lower claw 39 crown gear 40 Weight shaft 41 Weight 43 Locking member 45 Electric locking member 46 Floating locking member 47 Electric cylinder 48 Float

Claims (4)

A tide gate that can be opened manually or electrically to open the opening during normal times and close the opening during tide.
A spring for automatically closing and driving the tide gate with a spring force;
A locking member for locking the spring charged by the opening driving force of the tide gate ;
A speed regulating mechanism for regulating the speed when the tide gate is driven to be closed with respect to the spring , and
The locking member is unlocked by any one of manual operation, electric operation, or water level detection operation by float ,
The speed control mechanism includes a crown gear coupled to the drive shaft, and a pendulum type speed adjustment weight having a claw portion capable of abutting against a saw tooth of the crown gear, and the weight is applied by the locking member. spring closing driven tide gate to stop being characterized Rukoto. 2. The spring-closed tide gate according to claim 1, wherein the tide gate is a horizontal pulling gate, and is driven to open and close via a rack and a pinion, or a chain and a sprocket. 3. The spring-closed drive type tide gate according to claim 1, wherein the spring is a plurality of torsion coil springs or a spring. The pendulum speed adjusting weights, spring closed driven tide gate according to any one of claims 1 to 3, characterized in that it is capable of changing the position of the weight from the pendulum center.

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