JP5458395B2 - Sluice opener - Google Patents

Description

  The present invention relates to a sluice gate opening and closing device for opening and closing a sluice by raising and lowering a door body.

Conventionally, various sluice gate opening and closing devices for lowering the weight of the door body for opening and closing the sluice gate have been proposed.
For example, there is a sluice gate opening and closing device configured to be provided with an electromagnetic clutch in an electric or manual power transmission path, and when the electromagnetic clutch is released, the door is lowered by a centrifugal brake so that the speed of the door body is controlled to a predetermined speed or less. It has been proposed (see Patent Document 1).

  A rotating shaft that rotates as the weight of the door that opens and closes the sluice is lowered; a differential gear device that is coupled to the rotating shaft; an output portion that extends in two directions from the differential gear device; A centrifugal brake connected to each of the parts, and at least one output part among the output parts extending from the differential gear device, and the rotational output from the rotary shaft is out of each output part of the differential gear device There has been proposed a sluice gate opening and closing device including an electromagnetic brake that is switched so as to be transmitted from one to the other or both (see Patent Document 2).

Japanese Patent No. 3668943 JP 2010-242313 A

  As described above, in the sluice gate opening and closing device according to Patent Document 1, the electromagnetic clutch is provided in the power transmission path, so that it is inevitably necessary to be wet. However, the wet type lubricates the disk with lubricating oil and is excellent in wear resistance and cooling properties, but the structure becomes complicated and expensive, and the maintainability is not good.

  Moreover, in the sluice gate opening and closing device according to Patent Document 2, an electromagnetic brake is employed to switch the rotation output from the rotation shaft so that the rotation output is transmitted from one to the other or both of the output portions of the differential gear device. This electromagnetic brake functions to optimize the descent speed of the door body according to its height, does not function to restrain or release the weight drop of the door body, and its purpose is completely different. Is.

  The present invention reduces the cost of the device main body by making the device main body compact with respect to the sluice gate opening and closing device that electrically lowers the weight of the door body. In addition, the overall cost such as installation cost and maintenance management cost is reduced. An object of the present invention is to provide a sluice opening and closing device that can reduce the amount of water.

As a means for solving the above-mentioned problems, the present invention is a sluice gate opening / closing device that lowers the weight of a door body that opens and closes the sluice gate, and rotates as the weight of the door body descends. A rotating shaft, a planetary gear connected to each planetary gear to the rotating shaft, an electromagnetic brake connected to the tip of the output shaft connected to the sun gear of the planetary gear , and a midway portion of the output shaft A centrifugal brake or an oil resistance brake is provided.
According to the first aspect of the present invention, when the door body is lowered by its own weight, the electromagnetic brake is released so that the rotational drive from the rotating shaft passes through the planetary gear, that is, each planetary gear and sun gear (ring gear is fixed). Is transmitted to the centrifugal brake (or the oil resistance brake), the door body descends at a predetermined descending speed. And by employ | adopting an electromagnetic brake, compared with the electromagnetic clutch employ | adopted conventionally, a structure can be simplified compactly and the cost of apparatus itself can be reduced.

The invention described in claim 2 is characterized in that, in the invention described in claim 1, an electric motor is connected to the ring gear of the planetary gear.
In the invention of claim 2 , in order to raise the door body, when the electric motor is driven in a state where the output shaft (sun gear of the planetary gear) is held by the electromagnetic brake, the planetary gear is rotated from the ring gear of the planetary gear. The door is raised through the rotation shaft. At this time, since the rotational torque from the electric motor is increased by the planetary gear and transmitted to the rotating shaft, the apparatus can be made compact and the cost of the apparatus itself can be reduced.
In addition, the planetary gear forms a planetary type when the door body is lowered by its own weight. The holding torque can be reduced to about 1 / 4.5. However, the number of sun gear teeth is 20, the number of planetary gear teeth is 25, and the number of ring gear teeth is 70. Thereby, since the required performance of the electromagnetic brake can be kept low, the electromagnetic brake can be made more compact, and the cost of the brake itself can be reduced.

The invention described in claim 3 is characterized in that, in the invention described in claim 2 , the electric motor, the electromagnetic brake, and the centrifugal brake or the oil resistance brake are unitized.
In the invention of claim 3 , handling becomes very good and overall costs such as installation costs can be reduced.

The invention described in claim 4 is the invention described in any one of claims 1 to 3 , wherein the electromagnetic brake is arranged outside a housing that houses the rotating shaft and the planetary gear. Is.
In the invention of claim 4 , the maintainability becomes very good, and overall costs such as maintenance costs can be reduced.

The invention described in claim 5 is the invention described in any one of claims 1 to 4 , wherein the electromagnetic brake is of a dry type.
In the invention of claim 5 , by making the electromagnetic brake dry type, if the required holding torque is the same because the coefficient of friction is high, it can of course be configured more compactly than wet, and the cost can be reduced. Can do. Further, if the electromagnetic brake is a dry type, since the lubrication is not performed, the structure can be simplified and the maintainability is improved.

  Since the sluice gate opening and closing device of the present invention employs a planetary gear and an electromagnetic brake, the electromagnetic brake can be disposed outside the housing, so that the cost of the device main body can be reduced as compared with the conventional case including an electromagnetic clutch. In addition, overall costs such as installation costs and maintenance costs can be reduced.

FIG. 1 is a cross-sectional view of a rack-type sluice gate opening / closing device according to an embodiment of the present invention. FIG. 2 is an enlarged view of part A in FIG. 3A is a cross-sectional view of a dry non-excitation electromagnetic brake employed in the sluice gate opening / closing device, and FIG. 3B is a front view thereof. FIG. 4 is a cross-sectional view of a wire rope sluice opening and closing device according to an embodiment of the present invention. FIG. 5 is a cross-sectional view of a chain type sluice opening and closing device according to an embodiment of the present invention.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to FIGS. In the following description, for the sake of convenience, the left side of the figure will be described as one and the right side as the other.
As shown in FIG. 1, the sluice opening and closing device 1 according to the embodiment of the present invention employs a rack type that raises and lowers a rack bar 2 connected to a door body (not shown) to raise and lower the door body.

  As shown in FIG. 1, a sluice opening / closing device 1 according to an embodiment of the present invention includes a pin gear 3 meshed with a rack bar 2 coupled to a door body, and a first planet coupled to the pin gear 3. A gear 5, a manual handle 8 coupled to the first planetary gear 5, a second planetary gear 6 coupled to the first planetary gear 5, an electric motor 9 coupled to the second planetary gear 6, and a second The centrifugal brake 10 connected to the planetary gear 6, the dry non-excitation electromagnetic brake 11 connected to the second planetary gear 6, the pin gear 3, the first and second planetary gears 5, 6, etc. are accommodated, A manual handle 8, an electric motor 9, a centrifugal brake 10, and a housing 14 for unitizing a dry non-excitation electromagnetic brake 11 are provided.

  As shown in FIG. 1, the housing 14 is provided integrally with a first housing 14a in which the rack bar 2 is accommodated so as to be movable up and down, and the other end of the first housing 14a. A second housing 14b that houses a small gear 26 that meshes with the gear 25; a third housing 14c that is integrally provided on the other end of the second housing 14b and that houses the first planetary gear 5 and the like; A fourth housing 14d that is integrally connected to the other end of the third housing 14c via a support member 50 and that houses the fourth and fifth rotating shafts 20d and 20e, the bevel gears 55 and 56, and the like; A spur gear 81 with a cylindrical portion that is integrally provided on the opposite side of the manual handle 8 of the housing 14 c and is integrally fixed to a motor side shaft 80 from the motor 9, and a spur gear with a cylindrical portion that meshes with the spur gear 81. 8 Composed of the fifth housing 14e for housing a.

  As shown in FIG. 1, the rack bar 2 is disposed so as to be movable up and down in the first housing 14a. A pin gear 3 fixed to one end of the first rotating shaft 20a is engaged with the rack bar 2. The first rotating shaft 20a is rotatably supported by the first housing 14a via the bearings 21 and 21. A spur gear 25 is fixed to the other end of the first rotating shaft 20a. A small gear 26 meshes with the spur gear 25. The small gear 26 is fixed to one end of the second rotating shaft 20b. The second rotating shaft 20b extends through the third housing 14c and is rotatably supported by the third housing 14c via a bearing 21. A dust seal 22 is disposed on one end side of the bearing 21.

  As shown in FIG.1 and FIG.2, the 1st planetary gear 5 is connected with the other end of the 2nd rotating shaft 20b. In detail, as shown in FIG. 2, the 1st carrier 30 is integrally provided in the other end of the 2nd rotating shaft 20b. The first carrier 30 includes a cylindrical part 30a and a disk-like part 30b provided integrally with the other end of the cylindrical part 30a. The cylindrical portion 30a of the first carrier 30 is rotatably supported by the third housing 14c via the bearing 21. A concave portion 30 c is formed on the other end surface of the disk-shaped portion 30 b of the first carrier 30. A plurality of pin members 31 extend toward the other side at intervals in the circumferential direction around the concave portion 30c of the disk-like portion 30b of the first carrier 30. A first planetary gear 32 is rotatably supported by each pin member 31 via each bearing 21, 21. Each first planetary gear 32 meshes with a first ring gear 33 located on the outside thereof, and meshes with a first sun gear 34 located on the inside thereof.

  As shown in FIG. 1, a manual handle 8 is provided outside the third housing 14c (downward in FIG. 1). A handle side shaft 36 connected to the manual handle 8 extends into the third housing 14c. As shown in FIGS. 1 and 2, the first ring gear 33 of the first planetary gear 5 and the handle side shaft 36 of the manual handle 8 are connected by a worm gear in the third housing 14c. Specifically, the worm wheel 37 is fixed to the first ring gear 33 of the first planetary gear 5. On the other hand, a worm (not shown) is formed at the tip of the handle side shaft 36. The worm wheel 37 of the first ring gear 33 of the first planetary gear 5 and the worm of the handle side shaft 36 of the manual handle 8 are engaged with each other. As a result, the rotational drive from the manual handle 8 is transmitted from the worm of the handle side shaft 36 to the first ring gear 33 of the first planetary gear 5 via the worm wheel 37. However, the rotational drive from the first ring gear 33 of the first planetary gear 5 is not transmitted to the worm of the handle side shaft 36. In short, unless the manual handle 8 is rotated, the first ring gear 33 of the first planetary gear 5 is not rotated (self-locking function).

  As shown in FIG. 2, a supported shaft 39 extends from one end of the first sun gear 34 of the first planetary gear 5. The supported shaft 39 is rotatably supported via a bearing 21 in a recess 30 c provided in the disc-like portion 30 b of the first carrier 30. On the other hand, from the other end of the first sun gear 34, the third rotary shaft 20c extends toward the other. The third rotary shaft 20c is inserted through the through hole 40 of the worm wheel 37 and the through hole 41 of the disk-shaped spiral bevel gear 75 described later, and the bearings 21 are inserted into the inner wall surfaces of the through holes 40 and 41, respectively. , 21 are rotatably supported. The second planetary gear 6 is connected to the tip of the third rotating shaft 20c. Specifically, a disc-shaped second carrier 45 is integrally provided at the tip of the third rotating shaft 20c. A recess 45 a is formed on the other end surface of the second carrier 45. Around the recess 45 a of the second carrier 45, a plurality of pin members 46 extend toward the other side at intervals in the circumferential direction. A second planetary gear 47 is rotatably supported by each pin member 46 via each bearing (not shown). Each second planetary gear 47 meshes with a second ring gear 48 located on the outer side thereof, and meshes with a second sun gear 49 located on the inner side thereof. As can be seen from FIG. 1, the second planetary gear 6 is disposed inside a support member 50 that integrally connects the third housing 14 c and the fourth housing 14 d.

  As shown in FIG. 2, a supported shaft 39 extends from one end of the second sun gear 49 of the second planetary gear 6. The supported shaft 39 is rotatably supported by the recess 45 a of the second carrier 45 via the bearing 21. On the other hand, from the other end of the second sun gear 49, a fourth rotating shaft (output shaft) 20d extends in the fourth housing 14d toward the other. As shown in FIG. 1, the fourth rotating shaft 20d is rotatably supported by the fourth housing 14d via a bearing 21, and is further formed on the wall of the fourth housing 14d facing the dry non-excitation electromagnetic brake 11. A fixed support plate 51 is rotatably supported via a bearing 21. The tip of the fourth rotating shaft 20d is connected to a dry non-excitation electromagnetic brake 11 that is fixed to the outer surface of the fourth housing 14d (right side in FIG. 1). Specifically, referring also to FIG. 3A, the tip of the fourth rotating shaft 20d is attached to the boss portion 62 of the dry non-excitation electromagnetic brake 11 so as not to be relatively rotatable. Further, as shown in FIG. 1, a spur gear 52 is integrally fixed to the fourth rotating shaft 20d in the fourth housing 14d. Further, a fifth rotation shaft 20e is provided in the fourth housing 14d in parallel with the fourth rotation shaft 20d, and both ends of the fifth rotation shaft 20e are rotatable through the bearings 21 and 21, respectively. It is supported by the housing 14d. A spur gear 53 that meshes with a spur gear 52 fixed to the fourth rotation shaft 20d is integrally fixed to one side of the fifth rotation shaft 20e. A bevel gear 55 is integrally fixed to the other side of the fifth rotation shaft 20e.

  As shown in FIG. 3, the dry non-excitation electromagnetic brake 11 includes a disc-shaped brake magnet 60 having a flange portion 60 c, a coil (not shown) disposed in the brake magnet 60, and the brake magnet 60. A hub having an armature 61 disposed at the bottom of the second recess 60b and a boss portion 62 provided on one end side of the armature 61 and attached to the tip of the fourth rotating shaft 20d (see FIG. 1) so as not to be relatively rotatable. 63, a lining 64 integrally attached to the hub 63, a friction flange 65 provided on one end side of the lining 64, and a brake magnet 60, and constantly urges the lining 64 toward the friction flange 65. And a spring (not shown).

  The brake magnet 60 is provided with a first recess 60a into which the boss portion 62 is inserted at one end surface thereof, and a hub 63 having a larger diameter than the first recess 60a and in which the armature 61 and the lining 64 are integrated. 2 recesses 60b are formed. The armature 61 is supported at the bottom of the second recess 60 b of the brake magnet 60 by a bolt 66 so as to be movable in the axial direction. The friction flange 65 has a through hole 65a through which the fourth rotating shaft 20d is inserted. The friction flange 65 is connected to the flange portion 60 c of the brake magnet 60 so as to close the second recess 60 b and to be close to the lining 64 integrated with the hub 63. The dry non-excitation electromagnetic brake 11 is a waterproof type.

When the coil in the brake magnet 60 is energized via the electric wire 67, a magnetic flux is generated, and a magnetic circuit is formed between the brake magnet 60 and the armature 61. As a result, the armature 61 is pulled toward the brake magnet 60 against the biasing force of the spring in the brake magnet 60, the lining 64 is separated from the friction flange 65, and the fourth rotating shaft 20d is opened.
On the other hand, when the power supply to the coil in the brake magnet 60 is cut off, the magnetic flux disappears, and the armature 61 presses the lining 64 against the friction flange 65 by the urging force of the spring in the brake magnet 60. The rotation of the fourth rotating shaft 20d is restricted and held.

  As shown in FIG. 3, the dry non-excitation operation electromagnetic brake 11 is provided with a manual release lever 70. When the manual release lever 70 is pulled forward, the armature 61 is pulled toward the brake magnet 60 against the urging force of the spring, so that the lining 64 is separated from the friction flange 65 and the fourth rotating shaft 20d is opened. Is done. As described above, since the dry type non-excitation electromagnetic brake 11 is provided with the manual release lever 70, even if it cannot be energized in an emergency, the fourth rotary shaft can be operated by operating the manual release lever 70. 20d can be opened, and the door can be lowered at a predetermined lowering speed by its own weight.

  Moreover, as shown in FIG. 1, the centrifugal brake 10 is arrange | positioned by the outer surface of the 4th housing 14d at the side of the electric motor 9. As shown in FIG. A shaft 71 from the centrifugal brake 10 extends into the fourth housing 14d. A bevel gear 56 is integrally fixed to the tip of the centrifugal brake side shaft 71. The bevel gear 55 of the fifth rotating shaft 20e and the bevel gear 56 of the centrifugal brake side shaft 71 are engaged with each other. As a result, the rotational drive of the second planetary gear 6 from the fourth rotating shaft 20d extending from the second sun gear 49 is transmitted to the fifth rotating shaft 20e via the spur gears 52, 53 and via the bevel gears 55, 56. Input to the centrifugal brake 10.

The centrifugal brake 10 receives a rotational drive (not shown) disposed in a drum (not shown), for example, from the fifth rotating shaft 20e via the bevel gears 55 and 56 and is input to the centrifugal brake side shaft 71. By transmitting to the both ends of the rotating shaft and the friction coefficient between the both ends of the rotating shaft and the inner wall surface of the drum, the rotational speed of the centrifugal brake side shaft 71 is reduced to a predetermined speed or less. It is something to control.
In this embodiment, the centrifugal brake 10 is employed. However, an oil resistance brake may be employed in which oil is charged and the rotational speed is controlled to be equal to or lower than a constant speed by stirring resistance.

Further, as shown in FIG. 2, the second ring gear 48 of the second planetary gear 6 includes a small-diameter cylindrical portion 48a located on one side, a large-diameter cylindrical portion 48b located on the other side, a small-diameter cylindrical portion 48a, and a large-diameter cylindrical portion 48a. And a conical cylinder portion 48c connecting the diameter cylindrical portion 48b. A large number of internal teeth are formed on the inner peripheral surface of the large-diameter cylindrical portion 48b of the second ring gear 48, and the second planetary gears 47 are engaged with these internal teeth.
As shown in FIGS. 1 and 2, the support member 50 that connects the third housing 14c and the fourth housing 14d includes a small-diameter cylindrical portion 50a provided on one side and a large-diameter cylindrical portion 50b provided on the other side. And a frustoconical cylindrical body that is integrally connected to each other. The support member 50 is arranged so as to be parallel to the second rotation shaft 20b extending in the third housing 14c and so as to surround the second planetary gear 6, and the large-diameter cylindrical portion 50b of the support member 50 is disposed. The third housing 14c and the fourth housing 14d are connected to each other.

  As shown in FIG. 2, the small diameter cylindrical portion 48 a of the second ring gear 48 of the second planetary gear 6 is rotatably supported by the small diameter cylindrical portion 50 a of the support member 50 via the bearing 21. A disc-shaped spiral bevel gear 75 is fixed to one end face of the small-diameter cylindrical portion 48a of the second ring gear 48 so that the tooth portion faces one side. As described above, the third rotating shaft 20c extending in the third housing 14c is inserted through the through hole 40 of the worm wheel 37 and the through hole 41 of the disc-shaped spiral bevel gear 75, and the respective through holes are inserted. The inner walls of the holes 40 and 41 are rotatably supported via the bearings 21 and 21, respectively.

  As shown in FIGS. 1 and 2, the electric motor 9 is disposed on the outer surface of the fifth housing 14 e on the side opposite to the manual handle 8. An electric motor side shaft 80 from the electric motor 9 extends into the fifth housing 14 e, and a spur gear 81 with a cylindrical portion is integrally fixed to the electric motor side shaft 80. The spur gear 81 meshes with a spur gear 82 with a cylindrical portion in the fifth housing 14e. A driving shaft 83 is integrally fixed to the spur gear 82. The drive shaft 83 extends into the third housing 14 c and is rotatably supported by the third and fifth housings 14 c and 14 e via a pair of roller bearings 21 and 21. A spiral bevel gear 76 is integrally fixed to the tip of the drive shaft 83.

  As shown in FIG. 2, the spiral bevel gear 76 on the drive shaft 83 side and the disc-shaped spiral bevel gear 75 on the second ring gear 48 side of the second planetary gear 6 intersect with each other. It is configured as a hypoid gear (registered trademark) that meshes so as not to engage. As a result, the rotational drive from the drive shaft 83 of the electric motor 9 is transmitted to the second ring gear 48 of the second planetary gear 6 via the hypoid gears 75 and 76, but the rotation of the second planetary gear 6 from the second ring gear 48 is performed. The drive is not transmitted to the drive shaft 83 side. In short, unless the electric motor 9 is driven, the second ring gear 48 of the second planetary gear 6 is not rotated (self-locking function).

Next, the operation of the sluice gate opening / closing device 1 according to the embodiment of the present invention will be described.
First, the operation of the sluice gate opening and closing device 1 when the door body is lowered by its own weight will be described.
Then, by energizing the dry non-excitation electromagnetic brake 11, as described above, the fourth rotating shaft 20d is opened.
Then, the door body begins to descend due to its own weight. The rack bar 2 moves downward and the pin gear 3 rotates as the door body descends. The rotational drive of the pin gear 3 is transmitted from the first rotating shaft 20a to the first planetary gear 5 through the spur gear 25, the small gear 26 and the second rotating shaft 20b. The rotational drive transmitted to the first planetary gear 5 is such that the first planetary gear 32 (first carrier 30) is used as the first sun gear because the first ring gear 33 is fixed by the worm gear in the first planetary gear 5. 34 and transmitted to the third rotating shaft 20c. At this time, the rotational drive transmitted to the third rotary shaft 20c is transmitted with the rotational speed increased by the first planetary gear 5 and the rotational torque decreased.

  Subsequently, the rotational drive transmitted to the third rotary shaft 20 c is transmitted to the second planetary gear 6. The rotational drive transmitted to the second planetary gear 6 is transmitted from the second planetary gear 47 (second carrier 45) to the second because the second ring gear 48 of the second planetary gear 6 is fixed by hypoid gears 75 and 76. It is transmitted to the fourth rotating shaft 20d through the sun gear 49. Here, the rotational drive transmitted to the fourth rotary shaft 20d is transmitted with the rotational speed further increased by the second planetary gear 6 and the rotational torque further decreased. Subsequently, the rotational drive transmitted to the fourth rotating shaft 20d is transmitted to the fifth rotating shaft 20e via the spur gears 52 and 53, and input to the centrifugal brake 10 via the bevel gears 55 and 56. The As a result, the door body is controlled to a predetermined speed and lowered by its own weight.

Next, the operation of the sluice gate opening and closing device 1 when the door body is raised by the electric motor 9 will be described.
First, the energization to the dry type non-excitation electromagnetic brake 11 is cut off, so that the fourth rotating shaft 20d is held in a restrained state as described above.
Next, the electric motor 9 is rotationally driven in a direction in which the door body is raised. Then, the rotational drive is transmitted from the motor side shaft 80 to the second planetary gear 6 via the spur gears 81 and 82 and the hypoid gears 75 and 76. At this time, the rotational drive transmitted to the second planetary gear 6 is transmitted with the rotational speed being greatly reduced by the hypoid gear 75.76 and the rotational torque being greatly increased. Subsequently, the rotational drive transmitted to the second planetary gear 6 is that the second sun gear 49 (fourth rotary shaft 20d) is fixed by the dry non-excitation electromagnetic brake 11 in the second planetary gear 6. It is transmitted from the second ring gear 48 to the third rotary shaft 20c via the second planetary gears 47 (second carrier 45). Here again, the rotational drive transmitted to the third rotary shaft 20c is transmitted with the rotational speed further reduced and the rotational torque further increased by the second planetary gear 6.

  Subsequently, the rotational drive transmitted from the third rotating shaft 20c to the first planetary gear 5 has the first ring gear 33 fixed by the worm gear in the first planetary gear 5, so It is transmitted to the second rotating shaft 20b through one planetary gear 32 (first carrier 30). Here, the rotational drive transmitted to the second rotating shaft 20b is further reduced in speed by the first planetary gear 5 and further transmitted in the rotational torque. Subsequently, the rotational drive transmitted from the first planetary gear 5 to the second rotation shaft 20 b is transmitted to the first rotation shaft 20 a and the pin gear 3 through the small gear 26 and the spur gear 25. As a result, the rack bar 2 meshed with the pin gear 3 is raised and the door body is raised.

  As described above, the sluice gate opening / closing device 1 according to the embodiment of the present invention is the sluice gate opening / closing device 1 that lowers the weight of the door, and in particular, employs the second planetary gear 6 and the dry non-excitation electromagnetic brake 11. As a result, the dry type non-excitation electromagnetic brake 11 can be disposed outside the housing 14, that is, fixed to the outer surface of the housing 14, so that a conventional electromagnetic clutch is provided in the middle of the power transmission path. As a result, the cost of the main body of the apparatus can be reduced, and the overall costs such as installation costs and maintenance costs can be reduced.

  Moreover, in the sluice gate opening and closing device 1 according to the embodiment of the present invention, the manual handle 8, the electric motor 9, the centrifugal brake 10 and the dry non-excitation electromagnetic brake 11 are configured as a unit, so that handling becomes very good. Installation costs can be reduced.

Furthermore, in the sluice gate opening and closing device 1 according to the embodiment of the present invention, the rotational speed of the pin gear 3 when the door body is lowered by its own weight is, in particular, via the first and second planetary gears 5 and 6. Since the rotational speed is increased and the rotational torque is sufficiently reduced and input to the centrifugal brake 10, the required specifications of the centrifugal brake 10 can be kept low, and the cost of the centrifugal brake itself can be reduced. . On the other hand, the rotational drive from the electric motor 9 at the time of raising the door body, in particular, through the hypoid gears 75 and 76 and the first and second planetary gears 5 and 6, the rotational speed thereof is highly reduced and the rotational torque thereof. Is greatly increased and input to the pin gear 3, so that it is not necessary to provide a large number of spur gears, shafts, bearings, and the like for speed reduction, and the apparatus 1 can be made compact, and the cost of the apparatus 1 itself Can be reduced.
Further, when the door body is lowered by its own weight, the second planetary gear 6 (with 20 sun gear teeth, 25 each planetary gear teeth, and 70 ring gear teeth) constitutes a planetary type. When regulating (when holding the position of the door in the height direction), with respect to the rotational torque of each second planetary gear 47 (second carrier 45) of the second planetary gear 6 required for the dry non-excitation electromagnetic brake 11 The holding torque of the fourth rotating shaft 20d (second sun gear 49) can be reduced to about 1 / 4.5. Thereby, since the required performance of the dry non-excitation electromagnetic brake 11 can be kept low, the dry non-excitation electromagnetic brake 11 can be made more compact, and the cost of the dry non-excitation electromagnetic brake 11 itself can be reduced. .

  In addition, although the rack type is employ | adopted as the sluice gate opening / closing apparatus 1 which concerns on this Embodiment, you may employ | adopt as a wire rope type as shown in FIG. That is, in the wire rope sluice gate opening and closing device 1, the first rotating shaft 20a extends to the outside of the first housing 14a so as to cross the inside of the first housing 14a, and the drum 90 is provided at one end of the first rotating shaft 20a. It is fixed integrally. And the wire rope 91 connected with the door body is wound around the drum 90, and the door body is moved up and down. Further, as shown in FIG. 5, a chain-type sluice gate opening / closing device 1 may be employed. That is, in the chain type sluice opening and closing device 1, the chain 95 is connected to the door body, and the chain 95 is engaged with the sprocket 3 so as to raise and lower the door body.

  DESCRIPTION OF SYMBOLS 1 Lock gate opening / closing device, 2 Rack rod, 3 pin gear, 6 2nd planetary gear (planetary gear), 9 Electric motor, 10 Centrifugal brake, 11 Dry type non-excitation electromagnetic brake, 14 Housing, 20a 1st rotating shaft, 20b 2nd Rotating shaft, 20c 3rd rotating shaft, 20d 4th rotating shaft (output shaft), 20e 5th rotating shaft, 47 2nd planetary gear, 48 2nd ring gear, 49 2nd sun gear

Claims (5)

A sluice opening and closing device that lowers the weight of the door that opens and closes the sluice,
A rotating shaft that rotates as the door body descends;
Planetary gears in which each planetary gear is connected to the rotating shaft;
An electromagnetic brake connected to the tip of the output shaft connected to the sun gear of the planetary gear;
A centrifugal brake or an oil resistance brake connected to a midway portion of the output shaft;
A sluice opening and closing device comprising: The sluice opening and closing device according to claim 1, wherein an electric motor is connected to the ring gear of the planetary gear. The sluice gate opening and closing device according to claim 2 , wherein the electric motor, the electromagnetic brake, and the centrifugal brake or the oil resistance brake are unitized. Wherein the electromagnetic brake, sluice opening and closing device according to any one of claims 1 to 3, wherein it is located outside the housing for accommodating the rotary shaft and the planetary gear. The sluice gate opening and closing device according to any one of claims 1 to 4 , wherein the electromagnetic brake is a dry type.

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