JP4524598B2 - Electric shutter driving device and electric shutter opening and closing device - Google Patents

Description

  The present invention relates to an electric shutter driving device having an electric motor and an electric shutter opening / closing device that opens and closes a shutter by the electric shutter driving device.

  Patent document 1 is disclosing the electric shutter drive device integrated in an electric shutter opening / closing apparatus. The electric shutter driving device includes an electric motor, an output shaft that is connected directly or indirectly to a shutter winder capable of winding the shutter, and opens and closes the shutter by rotating the shutter winder, an electric motor and an output And a power transmission mechanism provided between the shaft and the shaft.

  According to the electric shutter driving device described above, the brake mechanism is provided between the electric motor and the output unit. The brake mechanism consists of a brake release mode that releases the brake when the electric motor is driven and the output shaft is rotated, and the rotation of the output shaft by applying a brake when a rotation input is given to the output shaft by an intruder or the like. It is possible to set the brake action mode to be suppressed.

  In a normal usage pattern, the electric motor is rotationally driven by the operation of the operation switch, the driving force is transmitted to the output shaft through the power transmission mechanism, and the shutter winder rotates. Then, the shutter is wound around the shutter winder and the shutter is opened, or the shutter is unwound from the shutter winder and the shutter is closed. In such a normal use form, the brake mechanism is in a brake release form, so that the output shaft can rotate smoothly.

On the other hand, when an intruder or the like tries to forcibly open the shutter from the outside, a rotation input is given to the output shaft by the intruder or the like. At this time, since the brake mechanism is in a braking action form, the load for opening the shutter becomes excessive, the rotation of the shutter winder is suppressed, and the opening operation of the shutter by an intruder or the like is suppressed.
JP 2002-256785 A

  By the way, in the event of an emergency such as a power failure, failure or disaster, it is required to manually open the shutter quickly. Therefore, according to Patent Document 1 described above, a brake release mechanism for releasing the brake action of the brake mechanism is provided. For this reason, in the event of a power failure or an emergency such as a disaster, if the brake action mode is released using the operating part of the brake release mechanism, the brake mechanism switches from the brake action mode to the brake release mode, and the shutter can be quickly moved manually with a small load. Can be opened.

  However, depending on the electric shutter opening / closing device, a large torque may act on the output shaft when the brake mechanism is switched. Even in this case, it is required to reduce the load for operating the operation portion of the brake release mechanism and to quickly release the brake.

  The present invention has been made in view of the above-described circumstances, and is an electric shutter that is advantageous for reducing a pulling load for releasing the engaging portion and the engaged portion, and is advantageous for quickly releasing the brake. It is an object to provide a driving device and an electric shutter opening / closing device.

(1) An electric shutter drive device according to the present invention of aspect 1 includes an electric motor, an output unit that opens and closes the shutter by rotating a shutter winder capable of winding the shutter, and an electric motor and an output unit. Provided between the power transmission mechanism that transmits the driving force of the electric motor to the output unit, and between the electric motor and the output unit, the brake is reduced when the electric motor is driven and the output unit is rotated Or a brake mechanism that can be set to a brake release form to be released and a brake action form to suppress rotation of the output unit,
A brake release mechanism for setting the brake mechanism to a brake release mode;
In an electric shutter drive device comprising an electric motor, a power transmission mechanism, a brake mechanism, and a base having a brake release mechanism,
The brake release mechanism
When the rotation input is given to the output unit, it rotates in conjunction with the rotation of the output unit and is rotated at a higher speed than the output unit, and has an engaged rotating body,
The interlocking rotating body is removably engaged with the engaged portion of the interlocking rotating body to prevent the interlocking rotating body from rotating, and the brake mechanism is set to one of the brake action mode and the brake releasing mode. An engagement portion that is separated from the engaged portion of the brake mechanism and uses the brake mechanism as one of the brake operation mode and the brake release mode ,
A speed reduction means is provided between the interlocking rotator and the output section. The speed reduction means decelerates when transmitting power from the electric motor to the output section, and transmits power from the output section to the electric motor. In this case, the speed of the interlocking rotator is increased .

(2) An electric shutter driving device according to the present invention of aspect 2 includes an electric motor,
  An output unit that opens and closes the shutter by rotating a shutter winder capable of winding the shutter;
  A power transmission mechanism that is provided between the electric motor and the output unit and transmits the driving force of the electric motor to the output unit;
  A brake release mode that is provided between the electric motor and the output unit and reduces or releases the brake when the electric motor is driven to rotate the output unit, and a brake action mode that suppresses rotation of the output unit. Possible brake mechanism,
  A brake release mechanism for setting the brake mechanism to a brake release mode;
  In an electric shutter drive device comprising an electric motor, a power transmission mechanism, a brake mechanism, and a base having a brake release mechanism,
  The brake release mechanism
  When the rotation input is given to the output unit, it rotates in conjunction with the rotation of the output unit and is rotated at a higher speed than the output unit, and has an engaged rotating body having an engaged portion;
  The interlocking rotating body is removably engaged with the engaged portion of the interlocking rotating body to prevent the interlocking rotating body from rotating, and the brake mechanism is set to one of the brake action mode and the brake releasing mode. An engagement portion that is separated from the engaged portion of the brake mechanism and uses the brake mechanism as one of the brake action mode and the brake release mode,
A speed reduction means is provided between the interlocking rotator and the output section. The speed reduction means decelerates when transmitting power from the electric motor to the output section, and transmits power from the output section to the electric motor. In this case, the speed of the interlocking rotator is increased.

( 3 ) An electric shutter opening and closing device according to the present invention according to aspect 3 includes a shutter, a shutter winder that can wind the shutter, and an electric shutter drive that rotates the shutter winder in the winding direction and the unwinding direction. In the electric shutter opening / closing apparatus comprising the apparatus, the electric shutter driving apparatus is an electric shutter driving apparatus according to the aspect 1 or 2 described above.

( 4 ) The output unit is directly or indirectly connected to a shutter winder capable of winding the shutter. In a normal usage mode, the electric motor is driven to rotate, and the driving force is transmitted to the output unit via the power transmission mechanism, the shutter winder rotates, and the shutter is wound around the shutter winder so that the shutter is The shutter is opened or the shutter is unwound from the shutter winder and the shutter is closed.

  When an intruder or the like tries to forcibly open the shutter from the outside, the brake mechanism is in the brake action form, so the load to open the shutter becomes excessive, and the rotation of the shutter winder is suppressed, Shutter opening operation by an intruder or the like can be suppressed.

  By the way, when the power transmission mechanism connects the electric motor and the output unit, the following action occurs when the shutter is manually opened. That is, in the event of an emergency such as a power failure, failure, or disaster, it is required to manually open the shutter quickly, but a brake release mechanism is provided to release the brake action of the brake mechanism. . For this reason, if the brake is released by the brake release mechanism, the brake mechanism is switched from the brake operation mode to the brake release mode, and the shutter can be quickly opened manually with a small load. However, a large torque may act on the output shaft depending on the electric shutter opening / closing device. Even in this case, the load for operating the brake release mechanism may increase.

  In this regard, according to the present invention, the brake release mechanism is engaged with the interlocking rotating body that rotates in conjunction with the rotation of the output unit and that is rotated at a higher speed than the output unit, and the engaged portion of the interlocking rotating body. And an engaging portion that removably engages. When rotation input is given to the output unit, power is also transmitted to the interlocking rotating body via the output unit. In this case, according to the present invention, the interlocking rotating body is accelerated more than the output unit. Here, the speed increase of the interlocking rotating body relative to the output unit corresponds to the torque of the interlocking rotating body being reduced more than the torque of the output unit. Since the torque of the interlocking rotator can be reduced more than the torque of the output part, the engaging part that is engaged with the engaged part of the interlocking rotator and prevents the interlocking rotator from rotating is interlocked. It is possible to reduce the extraction load that is extracted from the engaged portion of the rotating body and separated. Therefore, it is advantageous to quickly release the brake.

According to the present invention relating to each aspect , as described above, when the rotational input is given to the output unit, the interlocking rotating body is accelerated more than the output unit, so the torque of the interlocking rotating body is higher than the torque of the output unit. Can be reduced. For this reason, it is advantageous in reducing the load that separates the engaging portion that has engaged the engaged portion of the interlocking rotating body and prevented the interlocking rotating body from rotating, and the engaged portion of the interlocking rotating body. Become. Therefore, it is advantageous to quickly release the brake.

According to the present invention relating to aspect 1, the speed increasing means is provided between the interlocking rotator and the output part, and the speed increasing means is interlocked when power is transmitted from the output part to the interlocking rotator. Increase the speed of the rotating body. The speed increasing means increases the speed of the interlocking rotator in power transmission from the output section to the electric motor when a rotation input is given to the output section. Since the speed and the torque are basically opposite to each other, if the interlocking rotator is accelerated by the speed increasing means, the torque acting on the interlocking rotator can be reduced. For this reason, when the engaged part and the engaging part of the interlocking rotating body are engaged, it is advantageous to reduce the pulling load that causes the engaged part and the engaging part to be pulled out and separated.

According to the present invention relating to aspect 2, the speed reduction means is provided between the interlocking rotator and the output part, and the speed reduction means decelerates when transmitting power from the electric motor to the output part, When the power is transmitted from the output unit to the electric motor, the interlocking rotating body is accelerated. Thus, the speed reduction mechanism decelerates when transmitting power from the electric motor to the output unit. On the contrary, when the rotational input is given to the output unit, the speed reducing unit increases the speed of the interlocking rotating body in the power transmission from the output unit to the electric motor. Since the speed and the torque are basically opposite to each other, the torque acting on the interlocking rotator can be reduced if the interlocking rotator is accelerated. For this reason, when the engaged part and the engaging part of the interlocking rotating body are engaged, it is advantageous to reduce the pulling load that causes the engaged part and the engaging part to be pulled out and separated.

  An electric shutter driving device according to the present invention includes an electric motor, an output unit that opens and closes the shutter by rotating the shutter winder, a power transmission mechanism provided between the electric motor and the output unit, and an electric motor And a brake mechanism provided between the output portion and a brake release mechanism for reducing or releasing the brake. The output unit is directly or indirectly connected to a shutter winder capable of winding the shutter. The power transmission mechanism transmits the driving force of the electric motor to the output unit, and can include a reduction gear mechanism. A typical reduction gear mechanism includes a flat gear mechanism or a planetary gear mechanism.

  The brake mechanism includes a brake release mode that reduces or releases the brake when the electric motor is driven and the output unit is rotated, and a brake operation mode that suppresses the rotation of the output unit when a rotation input is given to the output unit. It can be set. The brake mechanism includes a brake cylinder body that can be set in a form that can rotate and a form that is prevented from rotating, and a brake member that can frictionally slide on the brake cylinder body. In this case, if the brake cylinder is rotatable, the brake can be released. If the brake cylinder is prevented from rotating, the brake will act. Examples of the brake material include a coil spring, a torsion coil spring, a friction material (including a lining material and a shoe), and the like.

  According to a preferred embodiment, the brake release mechanism reduces or releases the braking by the brake mechanism when the rotation input from the output unit to the electric motor through the power transmission mechanism is given to the output unit, and also via the power transmission mechanism. All power transmission is cut off. The brake release mechanism reduces or releases the brake by the brake mechanism. According to a preferred mode, the brake release mechanism can be exemplified as a mode that is set so as to cut off the power transmission from the output unit to the electric motor via the power transmission mechanism. When a rotation input from the output unit to the electric motor via the power transmission mechanism is given to the output unit, the brake is released by the brake release mechanism, so that the load for opening and closing the shutter can be reduced. Furthermore, since power transmission from the output unit to the electric motor via the power transmission mechanism is interrupted, idling of the electric motor is prevented. Therefore, the influence of the coking torque or the like of the electric motor can be suppressed. Therefore, the load for opening and closing the shutter can be further reduced. Accordingly, the shutter can be manually opened quickly in case of an emergency such as a power failure or a disaster. Here, the coking torque means a resistance force generated when the motor shaft of the electric motor rotates idly when the electric motor is not energized. This resistance force is generally said to be caused by a magnetic force between the rotor and the stator of the electric motor.

  The planetary gear mechanism described above is interposed between a sun gear operated by an electric motor, an internal gear disposed on the outer peripheral side of the sun gear, and the sun gear and the internal gear. A planetary gear and a carrier engaged with the planetary gear are provided. The planetary gear mechanism is advantageous for downsizing. The sun gear generally means a gear arranged in the central region of the planetary gear mechanism. An internal gear generally means a gear having internal teeth that mesh with a planetary gear. The carrier generally engages the planetary gear. According to the planetary gear mechanism, if any one of the sun gear, the internal gear, and the carrier is fixed and stopped, power is transmitted at a predetermined reduction ratio. Further, if the one rotation stop is released, power transmission through the planetary gear mechanism is interrupted.

  As described above, according to the present invention, the brake release mechanism includes the interlocking rotating body having the engaged portion, and the engaging portion that engages with the engaged portion of the interlocking rotating body and prevents the interlocking rotating body from rotating. Have When the engaging portion and the engaged portion are engaged, the interlocking rotating body is prevented from rotating, and the brake mechanism is set to either one of the brake operation mode and the brake release mode. Further, when the engaged portion and the engaging portion of the interlocking rotating body are separated, the brake mechanism is set to one of the brake release form and the brake release form. The engaging portion described above can be formed, for example, convex or concave. The engaged portion can be formed, for example, in a concave or convex shape so that it can be engaged with the engaging portion. Examples of the protrusion include a pin shape and a protrusion shape. Examples of the recess include a groove and a hole.

  According to the present invention, the brake release mechanism includes a component constituting the brake mechanism and a component constituting the power transmission mechanism when a rotation input from the output portion to the electric motor via the power transmission mechanism is given to the output portion. By interlocking, it is possible to exemplify a mode in which braking is reduced or released and power transmission through the power transmission mechanism is interrupted. In this case, the interlocking property of both parts can be improved. `` Synchronizing the parts constituting the brake mechanism and the parts constituting the power transmission mechanism '' may be a form in which the parts constituting the brake mechanism and the parts constituting the power transmission mechanism are interlocked by mechanical coupling, Or the form which integrally forms the component which comprises a brake mechanism and the component which comprises a power transmission mechanism may be sufficient.

  Moreover, according to this invention, the brake release mechanism can illustrate the form which has an operation part. The operation unit can switch between a mode in which the brake is reduced or released and power transmission through the power transmission mechanism is blocked and a mode in which power transmission through the power transmission mechanism is not blocked. In this case, the brake mechanism can be set to the brake action mode because the operation unit can be set to a mode in which the brake is not reduced or released and the power transmission via the power transmission mechanism is not interrupted. In this case, even if an intruder or the like tries to forcibly open the shutter from the outside, the brake of the brake mechanism acts, so the load for opening the shutter becomes excessive, and the forced opening of the shutter by the intruder or the like can be suppressed. .

  According to the present invention, the brake cylinder constituting the brake mechanism and one of the internal gear, the carrier, and the sun gear constituting the planetary gear mechanism can be exemplified as being configured to be interlocked. In this case, the brake cylinder constituting the brake mechanism and one of the internal gear, the carrier, and the sun gear constituting the planetary gear mechanism can be integrally interlocked by mechanical coupling such as uneven engagement. it can. In this case, the linkage between the brake cylinder and the internal gear (or carrier, sun gear) can be enhanced. The material of the brake cylinder and the material of the internal gear (or carrier, sun gear) can be changed. Further, in order to enhance the interlocking property, the brake cylinder constituting the brake mechanism and one of the internal gear, the carrier, and the sun gear constituting the planetary gear mechanism may be integrally formed.

  According to the present invention, preferably, the brake release mechanism includes an interlocking rotating body that interlocks with one of the brake cylinder, the internal gear, the carrier, and the sun gear, and an engagement that engages with the interlocking rotating body. The joint part is provided, and the brake cylinder, the internal gear, the carrier, and the sun gear can be prevented from rotating by the engagement between the engaging part and the interlocking rotating body. In this case, if the engagement between the engaging portion and the interlocking rotating body is released and released, the brake cylinder, the internal gear, the carrier, and the sun gear can be rotated, and the brake is released via the power transmission mechanism. Both power transmission release (disconnection) can be performed.

  According to the present invention, preferably, the brake cylinder constituting the brake mechanism and one of the internal gear, the carrier, and the sun gear constituting the planetary gear mechanism are configured to be interlocked. It can be illustrated. In this case, the brake cylinder and one of the internal gear, the carrier, and the sun gear of the planetary gear mechanism can be exemplified by being coupled and interlocked by mechanical means such as concave-convex fitting.

  Or you may shape | mold integrally the brake cylinder which comprises a brake mechanism, and the internal gear, carrier, and sun gear which comprise a planetary gear mechanism. According to the present invention, the brake release mechanism includes an engagement portion that engages with a brake cylinder, a carrier, a sun gear, and an interlocking rotary body that can be engaged with the brake cylinder, the carrier, and the sun gear. By releasing the rotation stop, it is possible to release the brake and disconnect the power transmission.

According to the present invention according to aspect 1, it is provided with a speed increasing means between the communicating dynamic rotor and the output unit, the speed increasing means, when the power transmission direction from the output portion to interlock the rotary body Increase the speed of the linked rotating body. The speed increasing means increases the speed of the interlocking rotator in power transmission from the output section to the electric motor when a rotation input is given to the output section. Since the speed and the torque are basically opposite to each other, if the interlocking rotator is accelerated by the speed increasing means, the torque acting on the interlocking rotator can be reduced. For this reason, when the engaged part and the engaging part of the interlocking rotating body are engaged, it is advantageous to reduce the pulling load that causes the engaged part and the engaging part to be pulled out and separated. As the speed increasing means, a gear mechanism such as a planetary gear mechanism or a flat gear mechanism, or another speed increasing mechanism can be employed.

According to the present invention according to aspect 2, is provided with a reduction mechanism between the continuous dynamic rotor and the output unit, the speed reduction means may be decelerated when the power transmission direction from the electric motor to the output section , Ru is accelerated an interlocking rotary member when the power transmission direction from the output unit to the electric motor. Reduction mechanism as this slows down when power transmission from the electric motor to the output section. On the contrary, when the rotational input is given to the output unit, the speed reducing unit increases the speed of the interlocking rotating body in the power transmission from the output unit to the electric motor. Since the speed and the torque are basically opposite to each other, the torque acting on the interlocking rotator can be reduced if the interlocking rotator is accelerated. For this reason, when the engaged part and the engaging part of the interlocking rotating body are engaged, it is advantageous to reduce the pulling load that causes the engaged part and the engaging part to be pulled out and separated. As the speed reduction means, a gear mechanism such as a planetary gear mechanism or a flat gear mechanism, or another speed reduction mechanism can be employed.

An electric shutter opening and closing device according to the present invention includes a shutter, a shutter winder that can wind the shutter, and an electric shutter driving device that rotates the shutter winder in a winding direction and an unwinding direction. The electric shutter driving device is an electric shutter driving device according to aspect 1 or 2 described above. Shutter Ri Ah in the sense of the shielding member for opening and closing the opening, but the slat is generally, in some cases, the curtain may be a curtain.

  Embodiment 1 of the present invention will be described below with reference to FIGS. FIG. 1 shows the overall concept of an electric shutter opening / closing device. This embodiment is applied to an electric shutter opening / closing device that opens and closes an opening for entering and exiting a structure. FIG. 1 schematically shows an electric shutter opening and closing device. As shown in FIG. 1, the electric shutter opening / closing device 1 is provided in a structure such as a house, a building, a factory, a vehicle (including a passenger car, a trailer, a truck, a train), a hull, etc., and a person or a vehicle enters and exits. The opening 10 is opened and closed. The electric shutter opening / closing device 1 includes two guide rails 11 that are provided in the opening 10 and run in parallel in the vertical direction. The electric shutter opening / closing device 1 is moved up and down along the guide rail 11 to open and close the opening and lower the stopper 12a. A shutter 12 as a shielding member, a non-rotating support shaft 13 fixed on the horizontal axis provided on the upper side of the guide rail 11, and a support member 13 connected to each other via a connection member (not shown). A driven wheel 14 (14a, 14b, 14c, 14d) that functions as a plurality of rotatable shutter winders, a rotatable driving wheel 15 (sprocket) that is spaced from the driven wheel 14a, and a drive An endless transmission member 16 (chain) provided between the wheel 15 and the driven wheel 14a and the electric shutter driving device 2 that rotates the driving wheel 15 are provided.As shown in FIG. 1, the driven wheel 14a has a sprocket shape, and the driven wheels 14b, 14c, and 14d have a disk shape. The shutter 12 has a slit 12c. As shown in FIG. 1, the support shaft 13, the driven wheel 14, the drive wheel 15, the transmission member 16, and the electric shutter drive device 2 are built in the case 1 c.

  The support shaft 13 is equipped with a biasing member 17 formed of a torsion coil spring. The biasing member 17 has a biasing force that always biases the shutter 12 upward. The upward biasing force of the biasing member 17 is basically set so as to balance the downward load force due to the weight of the shutter 12. For this reason, when the shutter 12 is opened, the upward biasing force of the biasing member 17 functions as an assisting force, so that the force for lifting and releasing the shutter 12 may be small. As shown in FIG. 1, the electric shutter driving device 2 is disposed along the support shaft 13 at a position separated from the support shaft 13. The diameter of the driven wheel 14 a is set larger than the diameter of the driving wheel 15, and the number of teeth of the driven wheel 14 a is set larger than the number of teeth of the driving wheel 15. For this reason, the speed reduction mechanism 19 is comprised by the driven wheel 14a, the drive wheel 15, and the transmission member 16, and the raising / lowering speed of the shutter 12 can be decelerated.

  FIG. 2 shows the inside of the electric shutter driving device 2. The electric shutter drive device 2 functions as an output unit provided in the machine room 21 of the base body 20, an electric motor 23 provided in the machine room 21 of the base body 20, and an output shaft 24 having an axis P. And a power transmission mechanism 3 provided in the machine chamber 21 of the base body 20 and a brake mechanism 6 provided in the machine chamber 21 of the base body 20. The electric motor 23, the power transmission mechanism 3, the brake mechanism 6, and the output shaft 24 are arranged in series in this order.

  The electric motor 23 (for example, a DC motor) has a motor shaft 23a. The output shaft 24 is indirectly connected to the shutter winder (driven wheels 14 a to 14 d) capable of winding the shutter 12 via the transmission member 16. When the output shaft 24 rotates, the shutter winder (driven wheels 14a to 14d) rotates, and the shutter 12 is wound or unwound. As shown in FIG. 2, the output shaft 24 is rotatably provided on a bearing 20m at the tip of the base body 20, and has a rotating body 24x at the tip. The power transmission mechanism 3 includes a reduction gear mechanism 4 that is rotated by a motor shaft 23 a of the electric motor 23 and a reduction planetary gear mechanism 5 that is connected to the reduction gear mechanism 4. The reduction gear mechanism 4 includes a first flat gear 41 that meshes with the motor shaft 23 a of the electric motor 23, a second flat gear 42 that meshes with the first flat gear 41, and a third flat gear 43 that meshes with the second flat gear 42. Provided, and the rotation of the electric motor 23 is decelerated.

  As shown in FIG. 2, the planetary gear mechanism 5 includes a sun gear 51, a ring-shaped internal gear 52 disposed on the outer peripheral side of the sun gear 51, and the sun gear 51 and the internal gear 52. A plurality of intervening planetary gears 53 and a carrier 54 engaged with the planetary gears 53 are provided. The sun gear 51 has external teeth 51u. The internal gear 52 has internal teeth 52i. The planetary gear 53 has external teeth 53u.

  According to the planetary gear mechanism 5, if any one of the sun gear 51, the internal gear 52, the planetary gear 53, and the carrier 54 is fixed and stopped, power transmission is performed at a predetermined reduction ratio. Also, if the one rotation stop is released to make it free, power transmission via the planetary gear mechanism 5 is interrupted.

  As shown in FIG. 2, the sun gear 51 is coaxially connected to the third spur gear 43 of the reduction gear mechanism 4 and is rotated by the third spur gear 43. The shaft 55 of the planetary gear 53 is engaged with the carrier 54 so as to be interlocked.

  According to the present embodiment, as shown in FIG. 2, the brake cylinder 60 (part of the brake mechanism 6) and the internal gear 52 (part of the power transmission mechanism 3) are integrally formed. It is set to work together. Alternatively, the brake cylinder 60 (part of the brake mechanism 6) and the internal gear 52 (part of the power transmission mechanism 3) are formed as separate parts and set so as to be interlocked by mechanical coupling means such as uneven fitting. You may do it.

  As shown in FIG. 4, the brake mechanism 6 includes a brake cylinder 60 that is rotatably and non-rotatable, and an inner peripheral surface of the brake cylinder 60 that is disposed substantially coaxially inside the brake cylinder 60. And a spring 62 functioning as a brake member capable of frictional sliding. The brake cylinder 60 has external teeth 60u. As shown in FIG. 4, the spring 62 includes a coil spring portion 63 whose outer diameter can be contracted, and protrusions 64 a and 64 b that are integrally formed at the tip of the coil spring portion 63. The protrusions 64 a and 64 b face the carrier 54 and the output shaft 24 through gaps 65 and 66. That is, a gap 65 is formed between the protrusions 64 a and 64 b and the carrier 54. A gap 66 is formed between the protrusions 64 a and 64 b and the output shaft 24.

  As can be understood from FIG. 4, when the electric motor 23 is stopped and the output shaft 24 rotates as the drive source in the direction of the arrow A1 around the axis P, the portion 24a of the output shaft 24 presses the protrusion 64a. The coil spring portion 63 operates in the diameter increasing direction thereof. For this reason, the force by which the coil spring part 63 presses the inner peripheral surface 60i of the brake cylinder 60 is increased, the frictional force is increased, and the brake action mode is obtained. When the portion 24a of the output shaft 24 rotates around the axis P in the direction of the arrow A2, the output shaft 24 presses the protrusion 64b and the coil spring portion 63 operates in the diameter increasing direction thereof, so that the coil spring portion 63 is The force which presses the inner peripheral surface 60i of the brake cylinder 60 is increased, the frictional force is increased, and the brake action mode is obtained. As described above, when the electric motor 23 is stopped and the output shaft 24 rotates in the arrow A1 direction or the arrow A2 direction using the drive shaft 24 as a drive source, the brake mechanism 6 is in a braking action mode.

As can be understood from FIG. 4, when the carrier 54 driven by the electric motor 23 rotates around the axis P in the direction of arrow A1, the portion 54a of the carrier 54 presses the projection 64b, and the coil spring portion 63 Operates in the direction of diameter reduction. For this reason, the force with which the coil spring portion 63 presses the inner peripheral surface 60i of the brake cylinder 60 is reduced, the frictional force is reduced, and the brake by the brake mechanism 6 is released. Further, when the carrier 54 rotates around the axis P thereof in the direction of arrow A2, the portion 54a of the carrier 54 presses the projection 64a, and the coil spring portion 63 operates in the direction of diameter reduction thereof, so the coil spring portion 63 The force that presses the inner peripheral surface 60i of the brake cylinder 60 is reduced, the frictional force is reduced, and the brake is released.

  When the carrier 54 driven by the electric motor 23 rotates in the arrow A1 direction or the arrow A2 direction as described above, the brake by the brake mechanism 6 is released. When the shutter 12 is opened by the electric motor 23, the carrier 54 rotates around the axis P in the direction of the arrow A1. When the shutter 12 is closed by the electric motor 23, the carrier 54 rotates in the direction of the arrow A2 around the axis P, but the present invention is not limited to this, and the reverse relationship may be set.

Next, the brake release mechanism 7 will be described with reference to FIGS. According to the present embodiment, the brake release mechanism 7 is a speed increasing function that functions as an intermediate gear having spur-shaped outer teeth 71u that mesh with spur-shaped outer teeth 60u of the brake cylinder 60, as shown in FIG. A gear 71 (speed increasing means), a continuous rotating body 72 having a disk shape functioning as an interlocking rotating body provided coaxially with respect to the speed increasing gear 71, and a cover formed on the outer periphery of the continuous rotating body 72 And a pin-like engagement portion 74 that is detachably engaged with a U-shaped groove 73 (concave portion) that functions as an engagement portion. Further, as shown in FIG. 5, the brake release mechanism 7 moves along a direction parallel to the axial length direction of the continuous rotating body 72 and exerts an operating lever 75 that exerts an operating force to disengage the engaging portion 74 from the groove 73. And a biasing spring 76 that functions as a biasing element that exerts a biasing force that engages the engaging portion 74 with the groove 73, and a stopper 77 for interlocking the engaging portion 74 when the operating lever is operated. .

  The operating lever 75 functions as an operating portion of the brake release mechanism 7 and is connected to one end 80a of a long connecting portion 80 such as a wire or a rod. The connecting portion 80 is extended on the indoor side of a structure such as a house or a building (for example, in the vicinity of the guide rail 11) so that an outside intruder or the like cannot operate. When a user or the like pulls the other end 80 b side of the connecting portion 80, the connecting portion 80 can be maintained in a tensile state by the restraining tool 100.

  As shown in FIG. 5, the urging spring 76 has a coil shape and is wound around the outer periphery of a pin-shaped engaging portion 74. As shown in FIG. 5, the base end portion 75c of the operating lever 75 is pivotally supported by a pivotal support portion 75e. A pin-shaped engaging portion 74 is located between the base end portion 75c and the tip end portion 75d of the operating lever 75. For this reason, when the pin-shaped engaging part 74 is pulled out from the groove 73, the operating lever 75 can exert a lever action, and a reduction in the pulling load can be expected.

  As shown in FIG. 6, the radius L <b> 3 of the continuous rotating body 72 is set larger than the radius L <b> 2 of the speed increasing gear 71. Since the continuous rotating body 72 can be interlocked with the brake cylinder 60 and the output shaft 24 via the speed increasing gear 71, it can function as an interlocking rotating body.

  In a normal use mode, the engaging portion 74 is moved in the direction of the arrow X2 (engagement direction) by the urging force of the urging spring 76 and is engaged with the groove 73, so the continuous rotating body 72 is prevented from rotating, As a result, the speed increasing gear 71 is prevented from rotating and the brake cylinder 60 is prevented from rotating. As a result, the internal gear 52 integral with the brake cylinder 60 is prevented from rotating. As described above, when the internal gear 52 of the planetary gear mechanism 5 is stopped from rotating, power is transmitted through the planetary gear mechanism 5 as described above.

  On the other hand, when the operation lever 75 is operated by the user or the like in the direction of the arrow X1 (engagement disengagement direction) against the biasing spring 76, the engaging portion 74 is disengaged from the groove 73. The rotation stop of the speed increasing gear 71 is released, and the rotation stop of the brake cylinder 60 is released. As a result, the rotation stop of the internal gear 52 integrated with the brake cylinder 60 is released. Is done. Therefore, the continuous rotating body 72, the speed increasing gear 71, the brake cylinder 60, and the internal gear 52 are free and can rotate. As described above, when the rotation of the internal gear 52 that has been prevented from rotating in the planetary gear mechanism 5 is released, the internal gear 52 becomes free, so that the electric motor 23 is connected to the planetary gear mechanism 5 via the planetary gear mechanism 5. Power transmission is cut off.

  Next, the operation of the electric shutter driving device 2 according to the present embodiment will be described. A normal usage mode, that is, a mode in which the shutter 12 is opened and closed by the electric motor 23 will be described. According to a normal usage pattern, the electric motor 23 is rotationally driven by the operation switch, the motor shaft 23 a is rotated, and the first flat gear 41, the second flat gear 42, and the third flat gear 43 constituting the reduction gear mechanism 4. And the sun gear 51 of the planetary gear mechanism 5 rotates. The rotation of the sun gear 51 is transmitted to the planetary gear 53. Further, the carrier 54 rotates through the internal gear 52 that is prevented from rotating. As described above, when the carrier 54 is rotated in the arrow A1 direction or the A2 direction by the electric motor 23, the spring 62 operates in a direction in which the outer diameter of the coil spring portion 63 of the spring 62 is reduced. As a result, the coil spring portion 63 of the spring 62 operates in a direction away from the inner peripheral surface 60i of the brake cylinder 60, so that the frictional sliding between the coil spring portion 63 of the spring 62 and the brake cylinder 60 is reduced. The brake mechanism 6 is in a brake release form. For this reason, the output shaft 24 is smoothly rotated by the electric motor 23, the shutter winder (driven wheel 14) is smoothly rotated, and the shutter 12 is wound or unwound well. That is, the shutter 12 is opened or closed. The carrier 54 is set to rotate in the direction of arrow A1 when the shutter 12 is opened, and the carrier 54 is set to rotate in the direction of arrow A2 when the shutter 12 is closed. Also good.

  In a normal usage pattern, an explanation will be given about the case where the intruder or the like forcibly opens the shutter 12 manually from the outside, instead of automatically driving the electric motor 23. In this case, a rotational input is given to the output shaft 24 as the shutter 12 is forcibly opened from the outside by an intruder or the like. This rotational input tends to go from the output shaft 24 to the electric motor 23 via the planetary gear mechanism 5. When the output shaft 24 tries to rotate as a drive source in this way, as described above, the spring 62 operates in the direction in which the coil spring portion 63 expands, and the spring 62 and the inner peripheral surface 60i of the brake cylinder 60 are in contact with each other. The frictional force is increased, and the brake mechanism 6 is in a brake action form. For this reason, the load for opening the shutter 12 becomes excessive. Therefore, it becomes difficult for an intruder or the like to open the shutter 12 forcibly, and the security is improved.

  Next, the operation in the brake release mode in which the brake mechanism 6 is released will be described. The release or reduction of the brake of the brake mechanism 6 as described above is generally a case where the shutter 12 is manually opened quickly in the event of an emergency such as a power failure or a disaster. First, the user pulls the connecting portion 80 to operate the operation lever 75 in the arrow X1 direction. Then, the engaging portion 74 is separated from the groove 73 against the biasing spring 76, and the rotation stop of the speed increasing gear 71 and the continuous rotating body 72 is released. Accordingly, as described above, the rotation stop of the internal gear 52 constituting the planetary gear mechanism 5 is released, and the brake cylinder 60 becomes free. Therefore, the internal gear 52 integral with the brake cylinder 60 becomes free, and the internal gear 52 rotates while releasing or reducing the brake of the brake mechanism 6. It can be opened.

  In other words, when the shutter 12 is forcibly opened, the output shaft 24 rotates as a drive source, and the spring 62, the brake cylinder 60, and the carrier 54 rotate. At this time, the rotation stop of the brake cylinder 60, that is, the internal gear 52 is released, and the internal gear 52 becomes free. For this reason, rotation is not transmitted to the sun gear 51 of the planetary gear mechanism 5. In this case, (1) the carrier 54 and the planetary gear 53 are rotated, and (2) the sun gear 51 is fixed. For this reason, the internal gear 52 rotates at a higher speed than the carrier 54 by the gear ratio. That is, in the brake mechanism 6, the brake cylinder 60 integrated with the internal gear 52 rotates at a higher speed than the carrier 54, the spring 62, and the output shaft 24. For this reason, the brake cylinder 60 relatively moves the spring 62 in the diameter reducing direction, and the brake cylinder 60 rotates while releasing or reducing the brake of the brake mechanism 6. Since the brake is released in this way, there is an advantage that the shutter 12 can be manually opened with a light load in the event of an emergency such as a power failure, failure or disaster.

  Further, according to the present embodiment, when the shutter 12 is manually opened in an emergency such as a power failure, a failure, or a disaster, a rotation input is given to the output shaft 24 by manually opening and closing the shutter 12, and the output shaft Even if 24 rotates as a drive source, power is not transmitted to the sun gear 51 of the planetary gear mechanism 5, the sun gear 51 is not rotated, and as a result, power transmission using the planetary gear mechanism 5 is interrupted. For this reason, the electric motor 23 does not rotate. Therefore, when the shutter 12 is manually opened in an emergency such as a power failure, a failure, or a disaster, the cocking torque of the electric motor 23 is not generated. Therefore, the reverse rotation torque is not increased due to the coking torque of the electric motor 23. In other words, according to the present embodiment, the brake release mechanism 7 can release or reduce the brake by the brake mechanism 6 and can block the power transmission by the power transmission mechanism 3. Therefore, the output shaft 24 can be further rotated with a lighter load, and the shutter 12 can be opened with a smaller load. According to the above-described embodiment, there can be obtained an advantage that the shutter 12 can be manually opened quickly with a light load in an emergency such as a power failure, a failure, or a disaster.

By the way, when the rotation stop of the brake cylinder 60 is released, a large torque may be applied to the output shaft 24. Namely, when the type of the shutter 12 for opening and closing the slit 12 c as shown in FIG. 1, under the closed state of the slit 12 c (upward torque of the biasing member 17 in the fully closed state will be a maximum), Only this torque acts on the output shaft 24. In this case, torque is also transmitted from the output shaft 24 to the brake cylinder 60. Here, in FIG. 6, it is assumed that torque T is applied to the brake cylinder 60. The radius of the brake cylinder 60 is L1, the radius of the speed increasing gear 71 is L2, and the radius of the continuous rotating body 72 is L3. Here, the relationship of L2 <L3 is set. The radius L3 corresponds to the radius of the position where the groove 73 is formed in the continuous rotating body 72. Thus, the radius L3 of the position where the groove 73 is formed is larger than the radius L2 of the speed increasing gear 71. If the tangential force acting on the external teeth 60u of the brake cylinder 60 is F1, F1 = T / L1 is basically established. Therefore, it is preferable to increase the radius L1 of the brake cylinder 60 in order to reduce the tangential force F1 so as to reduce the load by pulling out the engaging portion 74 as will be described later.

  Here, since the speed increasing gear 71 meshes with the external teeth 60u of the brake cylinder 60, the tangential force acting on the external teeth 71u of the speed increasing gear 71 is also F1. Here, as a comparative example, a case where a groove is formed in the outer peripheral portion of the brake cylinder 60 and the engaging portion engaged with the groove is removed will be considered. According to this comparative example, when the coefficient of friction between the brake cylinder 60 and the engagement portion is μ and the extraction load of the engagement portion is M1, the relationship of M1 = μ · F1 is basically established.

  Then, as shown in FIG. 6, assuming that the tangential force of the groove 73 on the outer peripheral portion of the continuous rotating body 72 is F2, F2 = F1 · (L2 / L3) is basically established. Therefore, when trying to remove the engaging portion 74 engaged with the groove 73 of the continuous rotating body 72 from the groove 73, the friction coefficient between the continuous rotating body 72 and the engaging portion 74 is μ, and the extraction load is Assuming M2, the relationship of M2 = μ · F2 = μ · F1 · (L2 / L3) is basically established.

  As is clear from FIG. 6, the radius L3 of the continuous rotating body 72 (corresponding to the radius of the groove 73) is larger than the radius L2 of the speed increasing gear 71 (L2 <L3). The pulling load of the engaging portion 60 is reduced ([M1 = μF1]> [M2 = μF1 (L2 / L3)]). Compared with the comparative example in which the engaging portion is removed from the groove formed in the brake cylinder 60 as described above, according to the present embodiment in which the engaging portion 74 is removed from the groove 73 of the continuous rotating body 72, the removal load is reduced. it can. For this reason, the operation of the brake release mechanism 7 can be performed with a light load, which is suitable for quick operation in an emergency such as a power failure, a failure, or a disaster.

  Here, as the value of L2 / L3 is smaller, the above-described punching load is reduced. Therefore, in order to reduce the above-described extraction load, the radius L3 of the continuous rotating body 72 may be increased and the radius L2 of the speed increasing gear 71 may be decreased. Therefore, as shown in FIG. 6, the radius L3 of the continuous rotating body 72 is set larger than the radius L2 of the speed increasing gear 71, and the outer peripheral portion 72p of the continuous rotating body 72 approaches the inner wall surface 20i of the base body 20. It has been enlarged until.

  According to the present embodiment, the engaging portion 74 is pulled out by the operating lever 75 having a lever action, and the pulling load can be reduced to some extent by the operating lever 75. However, although the length of the operating lever 75 is effective in reducing the pulling load, there is a limit to the increase in the length and stroke of the operating lever 75 due to the structure. In this regard, according to the present embodiment, as shown in FIG. 6, the continuous rotating body 72 is disposed via the speed increasing gear 71 with respect to the brake cylinder 60 having the external teeth 60 u, so that the operating lever While receiving the restriction of the length of 75, the above-described punching load can be reduced based on the value of L2 / L3. Depending on the value of L2 / L3, the operating lever 75 having a lever action may be eliminated.

  A second embodiment of the present invention will be described below with reference to FIGS. A common code | symbol is attached | subjected to a common site | part. This embodiment is applied to an electric shutter opening / closing device that opens and closes an opening for entering and exiting a structure. This electric shutter opening and closing device is provided in structures such as houses, buildings, factories, vehicles (including passenger cars, trailers, trucks, trains), hulls, etc., and opens and closes openings through which people or vehicles enter and exit. . The electric shutter opening / closing device includes a shutter as an opening / closing body and a rotatable shutter winding body, and is disposed coaxially with the support shaft 13. In this embodiment, unlike the embodiment shown in FIG. 1, the endless transmission member 16 is not provided.

  FIG. 8 shows the inside of the electric shutter driving device 2B mounted on the electric shutter opening / closing device described above. As shown in FIG. 8, the electric shutter drive device 2 </ b> B has a ring shape that functions as a base 20, an electric motor 23 provided in a machine chamber 21 of the base 20, and an output unit rotatably provided in the base 20. An output shaft 24, a power transmission mechanism 3 for deceleration provided in the machine chamber 21 of the base 20, and a brake mechanism 6 provided in the machine chamber 21 of the base 20 are provided.

  As shown in FIG. 8, the electric motor 23 has a motor shaft 23a. The power transmission mechanism 3 includes a first planetary gear mechanism 5A for reduction rotated by the motor shaft 23a, a second planetary gear mechanism 5B for reduction connected to the first planetary gear mechanism 5A, and a second planetary gear mechanism 5B. A third planetary gear mechanism 5C for reduction connected to the fourth planetary gear mechanism 5D for reduction connected to the third planetary gear mechanism 5C is provided in series. As shown in FIG. 8, the electric motor 23 → the first planetary gear mechanism 5A → the second planetary gear mechanism 5B → the third planetary gear mechanism 5C → the brake mechanism 6 → the fourth planetary gear mechanism 5D → the output shaft 24 in series. The power transmission path in the normal use form is in this order.

  As shown in FIG. 8, the first planetary gear mechanism 5A includes a ring-shaped sun gear 51A, a ring-shaped internal gear 52A arranged on the outer peripheral side of the sun gear 51A, and the sun gear 51A and the internal gear. A plurality of planetary gears 53A interposed between the gear 52A and a carrier 54A engaged with the planetary gear 53A are provided. The sun gear 51A has external teeth 51u. The internal gear 52A has internal teeth 52i. Planetary gear 53A has external teeth 53u.

  As shown in FIGS. 8 and 9, the second planetary gear mechanism 5B includes a ring-shaped sun gear 51B, a ring-shaped internal gear 52B disposed on the outer peripheral side of the sun gear 51B, and a sun gear 51B. And a plurality of planetary gears 53B interposed between the internal gear 52B and a carrier 54B engaged with the planetary gear 53B. FIG. 9 schematically shows the tooth part. The sun gear 51B has external teeth 51u. The internal gear 52B has internal teeth 52i. Planetary gear 53B has external teeth 53u. The internal gears 52A and 52B are integrated.

  As shown in FIGS. 8 and 10, the third planetary gear mechanism 5C includes a ring-shaped sun gear 51C, a ring-shaped internal gear 52C disposed on the outer peripheral side of the sun gear 51C, and a sun gear 51C. And a plurality of planetary gears 53C interposed between the internal gear 52C and a carrier 54C engaged with the planetary gear 53C. The sun gear 51C has external teeth 51u. The internal gear 52C has internal teeth 52i. Planetary gear 53C has external teeth 53u. As shown in FIG. 8, the central portion 520 of the internal gear 52C of the third planetary gear mechanism 5C is engaged with the carrier 54B of the second planetary gear mechanism 5B and is rotated by the carrier 54B.

  8 and 13 schematically show the tooth portion. As shown in FIG. 13, in the electric shutter drive device 2B, the fourth planetary gear mechanism 5D arranged at the final stage includes a sun gear 51D having a ring shape and an internal arranged on the outer peripheral side of the sun gear 51D. A ring-shaped output shaft 24 also serving as a gear, a plurality of planetary gears 53D interposed between the sun gear 51D and the output shaft 24, and a carrier 54D engaged with the planetary gear 53D via a shaft 55 (see FIG. 8) And. The carrier 54 </ b> D is prevented from rotating and is fixed to the base body 20. The output shaft 24, the sun gear 51D, and the planetary gear 53D are rotatable. The carrier 54D is engaged with the planetary gear 53D via the shaft 55. The sun gear 51D has external teeth 51u. Planetary gear 53D has external teeth 53u.

  As shown in FIG. 8, the center hole of the carrier 54C of the third planetary gear mechanism 5C is connected to the intermediate shaft 58, and coaxially with the sun gear 51D of the fourth planetary gear mechanism 5D via the intermediate shaft 58. The sun gear 51D is interlocked and rotated via the planetary gear 53D.

  As shown in FIG. 13, the output shaft 24 also serves as an internal gear of the fourth planetary gear mechanism 5D, and has a plurality of concave portions 25 as engaging portions on the outer peripheral portion. The concave portion 25 and the convex portion 27 of the mating member 26 are engaged. Here, when the output shaft 24 is rotated around the axis P by the electric motor 23, the counterpart member 26 is rotated, and the shutter winder is rotated, and the shutter 12 is wound or unwound. Is opened or closed.

  As shown in FIGS. 8 and 10, the brake mechanism 6 includes a ring-shaped sun gear 51C that also serves as a brake cylinder, a continuous rotating body 67 that can function as an interlocking rotating body connected to the sun gear 51C, and a sun gear. A spring 62 that functions as a brake member that is frictionally slidable is provided on the inner peripheral surface 510 of the sun gear 51C. The continuous rotating body 67 has a diameter larger than that of the sun gear 51C, and is integrally and coaxially connected to the sun gear 51C. According to the present embodiment, the sun gear 51C (part of the power transmission mechanism) of the third planetary gear mechanism 5C also serves as the brake cylinder (part of the brake mechanism) of the brake mechanism 6, and the number of parts can be reduced. It can be planned. As shown in FIG. 11, a U-shaped groove 73 (engaged portion) is formed on the outer peripheral portion of the continuous rotating body 67. A radius L5 from the center of the continuous rotating body 67 to the groove 73 is larger than a radius L6 of the sun gear 51C. In this case, as will be described later, it is possible to reduce the extraction load (detachment load) for separating the engaging portion 74 from the groove 73 as much as possible.

  As shown in FIG. 10, the spring 62 includes a coil spring portion 63 whose outer diameter can be contracted, and protrusions 64 a and 64 b that are integral with the coil spring portion 63. The protrusions 64a and 64b face the carrier 54 and the output shaft 24 through a gap. A gap 65 is formed between the protrusions 64 a and 64 b and the intermediate shaft 58. A gap 66 is formed between the protrusions 64a and 64b and the carrier 54C.

  As can be understood from FIG. 10, when the intermediate shaft 58 driven by the output shaft 24 rotates around the axis P in the direction of the arrow A1, the portion 58a of the intermediate shaft 58 presses the protrusion 64a, and the coil spring portion 63 Therefore, the friction force generated by the frictional sliding of the coil spring portion 63 on the inner peripheral surface 510 of the sun gear 51C (also serving as a brake cylinder) increases, and the brake mechanism 6 Become. Further, when the portion 58a of the intermediate shaft 58 driven by the output shaft 24 rotates in the arrow A2 direction around the axis P, the projection 64b is pressed, and the coil spring portion 63 operates in the diameter increasing direction thereof. The frictional force by which the coil spring portion 63 frictionally slides on the inner peripheral surface 510 of the sun gear 51C (also serving as a brake cylinder) increases, and the brake action form is obtained.

  As can be understood from FIG. 10, when the portion 540 of the carrier 54C driven by the electric motor 23 rotates around the axis P in the direction of the arrow A1, the portion 540 of the carrier 54C presses the protrusion 64b, and the coil spring portion. Since 63 operates in the diameter reducing direction thereof, the frictional force with which the coil spring portion 63 rubs against the inner peripheral surface 510 of the sun gear 51C is reduced, and the brake mechanism 6 is in a brake release mode. Further, when the carrier 54C driven by the electric motor 23 rotates around the axis P in the direction of arrow A2, the portion 541 of the carrier 54C presses the protrusion 64a, and the coil spring portion 63 operates in the direction of reducing the diameter thereof. The frictional force with which the coil spring portion 63 rubs against the inner peripheral surface 510 of the sun gear 51C is reduced, and the brake mechanism 6 is in a brake release mode.

  Next, the brake release mechanism 7 will be described with reference to FIGS. 8, 10, 11, and 12. According to this embodiment, as shown in FIG. 8, the brake release mechanism 7 is engaged with a U-shaped groove 73 formed on the outer periphery of the continuous rotating body 67 so as to be detachably engaged. And an actuating rod 78 that can function as an operating portion that exerts an operating force to disengage the engaging portion 74 from the groove 73, and a biasing force that biases the engaging portion 74 to engage the engaging portion 74 with the groove 73. An urging spring 76 which is an urging element to be exerted is provided. The other end 78c of the actuating rod 78 can be operated by a user in the room, but cannot be operated by an intruder or the like existing outside the shutter 12 (for example, in the vicinity of the guide rail 11) such as a house or a building. It is extended to. When the user or the like pulls the other end 78 c side of the operating rod 78, the operating rod 78 can be maintained in a tensile state by the restraining tool 100. As shown in FIG. 11, the engaging portion 74 is connected to the first engaging portion 74 a that engages with the groove 73 of the continuous rotating body 67, the first engaging portion 74 a, and the continuous rotating body 67. And an extending portion 74c extending on the outer peripheral surface.

  As shown in FIG. 12, one end portion 78 w of the operating rod 78 is bent in a U shape and is coupled to the engaging portion 74.

  When the operating rod 78 is not operated in the arrow X1 direction, the engaging portion 74 is engaged with the groove 73 by the biasing force of the biasing spring 76 in the arrow X2 direction (engagement direction). For this reason, rotation stop of the continuous rotary body 67 is performed. Since the continuous rotating body 67 and the sun gear 51C are integrally connected, the rotation of the sun gear 51C that also serves as a brake cylinder is stopped. When the rotation of the sun gear 51C of the third planetary gear mechanism 5C is thus stopped, the third planetary gear mechanism 5C can function as a power transmission mechanism, and power transmission via the third planetary gear mechanism 5C can be performed. The driving force of the electric motor 23 is transmitted to the output shaft 24 at a predetermined reduction ratio.

  On the other hand, when the operating rod 78 is pulled in the direction of the arrow X1 against the biasing spring 76 by a user or the like, the engaging portion 74 is detached from the groove 73 of the continuous rotating body 67 so as to go to the space 79. . For this reason, the rotation stopping of the continuous rotating body 67 is released, and consequently the rotation stopping of the sun gear 51C of the third planetary gear mechanism 5C is released. As described above, when the rotation of the sun gear 51C of the third planetary gear mechanism 5C is released and the sun gear 51C becomes free, the power transmission through the third planetary gear mechanism 5C is interrupted.

  Next, the operation of the electric shutter driving device 2 will be described. In a normal use form, a form in which the shutter 12 is opened by the electric motor 23 will be described. According to the normal usage mode, as described above, the engaging portion 74 is engaged with the groove 73 by the biasing spring 76, so that the rotation of the continuous rotating body 67, that is, the third planetary gear mechanism 5C is stopped. The rotation of the sun gear 51C is stopped. Therefore, the third planetary gear mechanism 5C can transmit power. In this state, when the electric motor 23 is driven to rotate in one direction by the operation switch, the motor shaft 23a rotates, the first planetary gear mechanism 5A for reduction rotates, and the second planetary gear mechanism 5B for reduction rotates. The decelerating third planetary gear mechanism 5C rotates, the decelerating fourth planetary gear mechanism 5E rotates, the output shaft 24 rotates in the arrow A1 direction, and the counterpart member 26 rotates in the arrow A1 direction. As a result, the shutter 12 is opened by the electric motor 23.

  Next, a mode in which the shutter 12 is closed by the electric motor 23 in a normal usage mode will be described. In this case, when the electric motor 23 is driven to rotate in the reverse direction by the operation switch, the motor shaft 23a rotates in the reverse direction, and the first planetary gear mechanism 5B for reduction, the second planetary gear mechanism 5B for reduction, Through the third planetary gear mechanism 5C, the fourth planetary gear mechanism 5E rotates in the opposite direction to that described above, the output shaft 24 rotates in the arrow A2 direction, and the mating member 26 rotates in the arrow A2 direction. As a result, the shutter 12 is closed by the electric motor 23.

  According to the above normal usage pattern, when the carrier 54C of the third planetary gear mechanism 5C is rotated by the electric motor 23, as described above, the spring 62 is reduced in the direction in which the outer diameter of the coil spring portion 63 of the spring 62 is reduced. Works. As a result, the coil spring portion 63 of the spring 62 operates in a direction in which the pressing force to the inner peripheral surface 510 of the sun gear 51C (brake cylinder) decreases, and therefore the friction between the coil spring portion 63 of the spring 62 and the sun gear 51C. Sliding is reduced, and as a result, the brake mechanism 6 is in a brake release configuration. When the carrier 54C of the third planetary gear mechanism 5C rotates in the direction of the arrow A1 or when it rotates in the direction of the arrow A2, the frictional sliding between the coil spring portion 63 of the spring 62 and the sun gear 51C (brake cylinder). The movement is reduced, and the brake mechanism 6 is in a brake release mode. Therefore, the output shaft 24 of the fourth planetary gear mechanism 5D functioning as the output shaft 24 rotates smoothly, the shutter winder smoothly rotates, and the shutter 12 is wound or unwound well.

  Next, a description will be given of a case where an intruder or the like forcibly opens the shutter 12 manually from the outside, instead of driving the electric motor 23. In this case, the engaging portion 74 is engaged with the groove 73. As the intruder or the like forcibly opens the shutter 12, a rotation input is given to the output shaft 24. The rotational input given to the output shaft 24 tends to go to the electric motor 23. Here, when the output shaft 24 tries to rotate as a drive source when the electric motor 23 is not driven, as described above, the coil spring portion 63 of the spring 62 operates in the direction of expanding the diameter, and the sun of the planetary gear mechanism 5C. The frictional force between the inner peripheral surface 510 of the gear 51C and the spring 62 is increased, and the brake mechanism 6 is in a braking action mode. For this reason, when an intruder or the like tries to forcibly open the shutter 12, an excessive load is required, making it difficult for the intruder or the like to open the shutter 12 and securing the safety.

  Next, the operation in the brake release mode in which the brake mechanism 6 is released will be described. When the release of the brake mechanism 6 is requested, it is generally an emergency when it is desired to manually open the shutter 12, such as during a power failure, failure, disaster, or failure. First, when a user or the like pulls and operates the operating rod 78 in the direction of the arrow X1, the engaging portion 74 separates from the groove 73 against the biasing spring 76, and the rotation stop of the continuous rotating body 67 is released. The continuous rotating body 67 is free. Therefore, the rotation stop of the sun gear 51C (brake cylinder) constituting the planetary gear mechanism 5C connected to the continuous rotating body 67 is released, and the sun gear 51C becomes free. Therefore, the brake is released and the power transmission by the third planetary gear mechanism 5C is interrupted. In this case, as the shutter 12 is manually opened, the output shaft 24 rotates, and the spring 62, the sun gear 51C, and the carrier 54C rotate.

  Since the sun gear 51C, which has been stopped as described above, rotates as described above, the power transmission through the third planetary gear mechanism 5C is interrupted. Therefore, even if the intermediate shaft 58, the carrier 54C, and the planetary gear 53C are rotated by the rotation input from the output shaft 24, the rotation is not transmitted to the internal gear 52C of the third planetary gear mechanism 5, and the internal gear 52C is non- It becomes rotation.

  In this case, (1) the planetary gear 53C is rotated and (2) the internal gear 52C is fixed. For this reason, the sun gear 51C rotates at a higher speed than the carrier 54C by the gear ratio. That is, the sun gear 51 </ b> C that also serves as the brake cylinder rotates at a higher speed than the carrier 54 </ b> C, the spring 62, and the output shaft 24. As a result, the spring 62 is relatively moved in the diameter reducing direction, and the sun gear 51 </ b> C rotates while releasing or reducing the brake of the brake mechanism 6. As described above, there is an advantage that the shutter 12 can be manually opened with a light load while releasing or reducing the brake of the brake mechanism 6 in an emergency such as a power failure, a failure, or a disaster.

  Further, as described above, when releasing or reducing the brake of the brake mechanism 6 and manually releasing the shutter 12 with a light load, it is assumed that the intermediate shaft 58, the carrier 54C, and the planetary gear 53C are rotated by the rotation input from the output shaft 24. However, since the internal gear 52C of the third planetary gear mechanism 5C is non-rotating, the power transmission via the third planetary gear mechanism 5C is interrupted, the power transmission path to the electric motor 23 is interrupted, and the electric motor 23 does not idle. Therefore, the problem of increasing the reverse torque due to the coking torque of the electric motor 23 is solved. That is, the shutter 12 can be quickly opened with a smaller load, which is suitable when the shutter 12 is to be manually opened at an early stage, such as in the event of a power failure, failure or disaster. As described above, according to the embodiment, the shutter 12 can be quickly opened with a light load manually by an emergency such as a power failure, a failure, or a disaster.

By the way, when releasing the rotation stop of the sun gear 51 </ b> C that also serves as a brake cylinder, a large torque may be applied to the output shaft 24. That is, if the type of the shutter 12 for opening and closing the slit 12 c as shown in FIG. 1, under the closed state of the slit 12 c (upward torque of the biasing member 17 in a fully closed state is maximized), the torque Only acts on the output shaft 24. In this case, a large torque T acts on the sun gear 51 </ b> C and the continuous rotating body 67 from the output shaft 24. In this case, since the frictional force between the wall surface of the groove 73 and the engaging portion 74 increases, the engaging portion 74 may not easily come off from the groove 73 of the continuous rotating body 67.

  In this regard, according to the present embodiment, the fourth planetary gear mechanism 5D (deceleration means) for deceleration is provided between the output shaft 24 and the continuous rotating body 67 (sun gear 51C). When power is transmitted in the order of the electric motor 23 → the planetary gear mechanisms 5A, 5B, 5C → the fourth planetary gear mechanism 5D → the output shaft 24, the fourth planetary gear mechanism 5D has a speed reducing action. However, when power is transmitted in the reverse direction, that is, the output shaft 24 → the fourth planetary gear mechanism 5D → the continuous rotating body 67 (sun gear 51C), the fourth planetary gear mechanism 5D has a reverse action, that is, a speed increasing action. That is, if the rotational speed of the output shaft 24 is N5 [rpm] and the rotational speed of the continuous rotating body 67 (sun gear 51C) is N6 [rpm], N6> N5. Accordingly, when power is transmitted from the output shaft 24 to the fourth planetary gear mechanism 5D to the continuous rotating body 67, the torque of the output shaft 24 is transmitted to the sun gear 51C and the continuous rotating body 67 as a small torque. For this reason, even when a large torque acts on the output shaft 24, the torque acting on the sun gear 51C and the continuous rotating body 67 is reduced by the amount corresponding to the speed increasing ratio by the fourth planetary gear mechanism 5D. For this reason, the tangential force F6 (refer FIG. 11) which acts on the groove | channel 73 of the continuous rotary body 67 can be made small.

  As a result, when the engagement portion 74 is to be removed from the groove 73 of the continuous rotating body 67, the removal load (detachment load) when the engagement portion 74 is removed from the groove 73 can be reduced. Therefore, it is possible to pull out the engaging portion 74 from the groove 73 by pulling the operating rod 78 which is an operation portion for operating the brake release mechanism 7 with a light load, and quickly in an emergency such as a power failure, failure, disaster, etc. Suitable for operation. Further, as shown in FIG. 11, since the radius L5 (corresponding to the radius of the groove 73) of the continuous rotating body 67 is set larger than the radius L6 of the sun gear 51C, it is advantageous for further reducing the tangential force F4. This is more advantageous for reducing the above-described punching load.

  According to the present embodiment, the fourth planetary gear mechanism 5D that is coaxially provided with the sun gear 51D and the carrier 54D is utilized, which is advantageous for downsizing the brake release mechanism 7. Also in this embodiment, if necessary, an operating lever using the lever principle can be used as in the first embodiment.

  A third embodiment of the present invention will be described below with reference to FIG. This embodiment has basically the same configuration as that of the second embodiment shown in FIG. 8, and has basically the same functions and effects as the second embodiment. A common code | symbol is attached | subjected to a common site | part. In the following, different parts will be mainly described. In the electric shutter drive device 2C according to the present embodiment, the brake cylinder 60 constituting the brake mechanism 6 is integrated with the carrier 54C. When the operating rod 78 is not operated, the engaging body 74 is engaged with the groove 73 by the biasing force of the biasing spring 76. For this reason, the rotation of the carrier 54C of the third planetary gear mechanism 5C is executed, and the rotation of the brake cylinder 60 integrated with the carrier 54C is executed. When the rotation of the carrier 54C of the third planetary gear mechanism 5C is thus stopped, the third planetary gear mechanism 5C can function as a power transmission mechanism, and power transmission via the third planetary gear mechanism 5C is predetermined. The driving force of the electric motor 23 is transmitted to the output shaft 24. On the other hand, when the operating rod 78 is pulled against the biasing spring 76 by the user or the like, the engaging body 74 is detached from the groove 73. Therefore, the rotation stop of the carrier 54C constituting the third planetary gear mechanism 5C is released. When the carrier 54C becomes free in this way, power transmission through the third planetary gear mechanism 5C is interrupted.

(Other examples)
According to the first embodiment described above, the brake mechanism 6 frictionally slides the spring 62 functioning as a brake member on the inner peripheral surface 60i of the brake cylinder 60. However, the invention is not limited thereto, and the spring 62 is connected to the brake cylinder 60. You may make it friction-slide to the outer peripheral surface. According to the first embodiment described above, the engaging portion 74 engaged with the groove 73 of the continuous rotating body 72 is pulled out from the groove 73 to be detached, but this is not limiting. A method may be adopted in which the mating portion 74 is pressed and removed from the groove 73. According to the first embodiment described above, the continuous rotating body 72 is provided, but instead of this, a gear having a tooth portion may be used as the continuous rotating body. According to the first embodiment described above, the groove 73 is provided as the engaged portion, but it may be a hole. Further, the engaging portion 74 is pin-shaped and the engaged portion is a groove 73. However, the present invention is not limited to this, and the engaging portion is a groove or a hole, and the engaged portion is a pin-shaped or a protruding shape. You can also

  According to the second embodiment described above, the fourth planetary gear mechanism 5D for reduction is provided between the output shaft 24 and the continuous rotating body 67 (sun gear 51C). However, the present invention is not limited to the planetary gear mechanism. A reduction mechanism such as a reduction gear mechanism such as a flat gear may be used. According to the above-described first and second embodiments, the planetary gear mechanisms 5, 5A, 5B, and 5C are used, but other reduction gear mechanisms can be employed.

  The first and second embodiments described above are suitable for opening and closing the shutter in the event of an emergency such as a power failure, failure, or disaster. However, the present invention is not limited to this, and an appropriate user who is not an intruder uses the electric motor 23. It is also suitable when it is desired to manually open and close the shutter. In addition, the present invention is not limited to the embodiments described above and shown in the drawings, and can be implemented with appropriate modifications within a range not departing from the gist.

  INDUSTRIAL APPLICABILITY The present invention can be used for an electric shutter opening / closing device installed in a structure such as a house, a building, a factory, a vehicle, and a hull.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view schematically showing an electric shutter opening / closing device having an electric shutter driving device according to a first embodiment. FIG. 3 is a cross-sectional view illustrating an internal structure of the electric shutter driving device according to the first embodiment. FIG. 3 is an arrow view along the line III-III in FIG. 2 according to the first embodiment. FIG. 4 is an arrow view along the IV-IV line in FIG. 2 according to the first embodiment. FIG. 3 is a cross-sectional view illustrating an internal structure of the electric shutter driving device according to the first embodiment. FIG. 6 is an arrow view along the VI-VI line in FIG. 5 according to the first embodiment. FIG. 7 is an arrow view along the line VII-VII in FIG. 2 according to the first embodiment. FIG. 10 is a cross-sectional view illustrating an internal structure of the electric shutter driving device according to the second embodiment. FIG. 9 is an arrow view along the line IX-IX in FIG. 8 according to the second embodiment. FIG. 9 is an arrow view along the line XX in FIG. 8 according to the second embodiment. FIG. 9 is an arrow view along the line XI-XI in FIG. 8 according to the second embodiment. FIG. 10 is an arrow view showing a state in which the engaging portion is coupled to the distal end portion of the operating rod according to the second embodiment. FIG. 9 is an arrow view along the line XIII-XIII in FIG. 8 according to the second embodiment. FIG. 10 is a cross-sectional view illustrating an internal structure of the electric shutter driving device according to the third embodiment.

  14 is a driven shaft (shutter winding body), 2 is an electric shutter drive device, 20 is a base, 23 is an electric motor, 24 is an output shaft (output unit), 3 is a power transmission mechanism, 4 is a reduction gear mechanism, and 5 is Planetary gear mechanism, 5D is a fourth planetary gear mechanism (reduction means), 51 is a sun gear, 52 is an internal gear (part of a power transmission mechanism), 53 is a planetary gear, 54 is a carrier, 6 is a brake mechanism, and 60 is a brake. Cylindrical body (part of brake mechanism), 62 is a spring, 64a and 64b are protrusions, 67 is a continuous rotating body (continuously interlocking rotating body), 7 is a brake releasing mechanism, 71 is a speed increasing gear (speed increasing means), 72 is Continuous rotating body (interlocking rotating body), 73 is a groove (engaged portion), 74 is an engaging portion, 75 is an operating lever (operating portion), 76 is a biasing spring, and 78 is an operating rod (operating portion). .

Claims (10)

An electric motor;
An output unit that opens and closes the shutter by rotating a shutter winder capable of winding the shutter; and
Provided between the electric motor and the output portion, and a power transmission mechanism for transmitting the driving force of the electric motor to the output unit,
Wherein provided between the electric motor and the output portion, and the brake release form to reduce or release the brake when the output unit the electric motor is driven is rotated to suppress the rotation of the output unit brake A brake mechanism that can be set to an action mode;
A brake release mechanism for setting the brake mechanism in a brake release mode;
In the electric shutter drive device comprising the electric motor, the power transmission mechanism, the brake mechanism, and a base body having the brake release mechanism,
The brake release mechanism is
When the rotation input is given to the output unit, it rotates in conjunction with the rotation of the output unit and is rotated at a higher speed than the output unit, and has an engaged part,
By engaging with the engaged portion of the interlocking rotator in a detachable manner, the interlocking rotator is prevented from rotating, and the brake mechanism is set to one of the brake action mode and the brake release mode. And an engagement portion that is detached from the engaged portion of the interlocking rotating body and uses the brake mechanism as the other of the brake action mode and the brake release mode ,
Speed increasing means is provided between the interlocking rotating body and the output unit, and the speed increasing means increases the interlocking rotating body when transmitting power from the output unit to the interlocking rotating body. An electric shutter driving device characterized in that it is accelerated . An electric motor;
An output unit that opens and closes the shutter by rotating a shutter winder capable of winding the shutter; and
A power transmission mechanism provided between the electric motor and the output unit, and transmitting a driving force of the electric motor to the output unit;
A brake release mode that is provided between the electric motor and the output unit and reduces or releases a brake when the electric motor is driven to rotate the output unit, and a brake that suppresses rotation of the output unit A brake mechanism that can be set to an action mode;
A brake release mechanism for setting the brake mechanism in a brake release mode;
In the electric shutter drive device comprising the electric motor, the power transmission mechanism, the brake mechanism, and a base body having the brake release mechanism,
The brake release mechanism is
When the rotation input is given to the output unit, it rotates in conjunction with the rotation of the output unit and is rotated at a higher speed than the output unit, and has an engaged part,
By engaging with the engaged portion of the interlocking rotator in a detachable manner, the interlocking rotator is prevented from rotating, and the brake mechanism is set to one of the brake action mode and the brake release mode. And an engagement portion that is detached from the engaged portion of the interlocking rotating body and uses the brake mechanism as the other of the brake action mode and the brake release mode,
A speed reduction means is provided between the interlocking rotator and the output unit, and the speed reduction means decelerates when power is transmitted from the electric motor to the output unit, and from the output unit to the output unit. An electric shutter driving device characterized in that when the power is transmitted toward an electric motor, the interlocking rotating body is accelerated. 3. The brake release mechanism according to claim 1, wherein the brake release mechanism includes a component constituting the brake mechanism and the power when a rotation input from the output unit to the electric motor is applied to the output unit via the power transmission mechanism. An electric shutter drive device characterized by reducing or releasing a brake and interlocking power transmission through the power transmission mechanism by interlocking with components constituting the transmission mechanism. 4. The electric shutter driving device according to claim 3 , wherein the parts constituting the brake mechanism and the parts constituting the power transmission mechanism are mechanically connected or integrally formed. In any one of claims 1 to 4, wherein the power transmission mechanism includes a planetary gear mechanism, the planetary gear mechanism, the sun gear and the internal gear arranged on the outer peripheral side of the sun gear And a planetary gear interposed between the sun gear and the internal gear, and a carrier engaged with the planetary gear. 6. The speed increasing gear linked to the internal gear of the planetary gear mechanism is provided as the speed increasing means according to claim 5 , and the interlocking rotating body is set to rotate in conjunction with the speed increasing gear. And
The electric shutter driving device according to claim 1, wherein a radius of the engaged portion formed on the interlocking rotating body is set larger than a radius of the speed increasing gear. 6. The electric shutter driving device according to claim 5 , wherein the interlocking rotating body is set to rotate in conjunction with the sun gear of the planetary gear mechanism. In Claim 7 , the radius of the interlocking rotating body is set larger than the radius of the sun gear, and the radius of the engaged part formed in the interlocking rotating body is larger than the radius of the sun gear. An electric shutter driving device characterized by being set large. In any one of claims 1 to claim 8, wherein the brake mechanism includes a mounted for retaining rotatably and rotating the brake cylinder body, which can be frictionally slid to the brake cylinder which is rotation stop A brake member,
The brake member is provided so as to be settable to a brake action mode in which the brake cylinder is frictionally slid to the rotation-stopped brake cylinder body and a brake is released to prevent frictional sliding on the brake cylinder body. The electric shutter drive device characterized by the above-mentioned. Shutter,
A shutter winder capable of winding the shutter;
In an electric shutter opening and closing device comprising an electric shutter driving device that rotates the shutter winding body in a winding direction and an unwinding direction,
The electric shutter driving device according to any one of claims 1 to 9 , wherein the electric shutter driving device is an electric shutter driving device.

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