JP2005248422A - Sheet shutter driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sheet shutter driving device having a simple constitution, allowing miniaturization, and having durability. <P>SOLUTION: This device has a DC brushless motor 1 and a planetary speed reducer 2. The planetary speed reducer 2 has a first sun gear 15 connected to a shaft 6 of the motor, a first internal gear 16 arranged on the outer periphery of the first sun gear 15, a plurality of first planetary gears 17 meshing with the first sun gear 15 and the first internal gear 16, a first carrier 18 for rotatably supporting the first planetary gears 17 and rotatably supported by two bearings 23 and 24 arranged at an interval in the shaft direction, and a case 10 for storing the respective gears and the first carrier 18 and fixed with the first internal gear 16. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a seat shutter driving device, and more particularly to a seat shutter driving device for driving a seat shutter that is installed at an entrance / exit of a factory or a parking lot and is frequently opened and closed.

  In a factory or the like, a sheet shutter device is installed at the entrance / exit to prevent heat from moving between the inside of the factory and the outside air, and to prevent dust and the like from entering the factory. This sheet shutter device includes a sheet shutter, a winding mechanism for raising and lowering the seat shutter to open and close the entrance and exit, and a sheet shutter driving device for driving the winding mechanism. The winding mechanism extends in the lateral direction at the upper part of the entrance and exit, and has a winding drum for winding the sheet shutter around the outer periphery. The sheet shutter is moved up and down by rotating the winding drum by a sheet shutter driving device and a winding mechanism driven thereby.

As an example of such a sheet shutter driving device, there is a device disclosed in Japanese Patent Laid-Open No. 2001-323759. This device has an electric motor and a hypocycloid speed reducer, and an inverter device for driving a motor and a seat shutter driving device are integrated.
JP 2001-323759 A

  Since the sheet shutter driving device requires a relatively large driving force, an induction motor (induction motor) is generally used as a driving source. Further, as the speed reducer, a hypocycloid speed reducer as shown in the above publication is used so that it can withstand high-frequency opening and closing work.

  However, in such a device composed of a conventional induction motor and a hypocycloid reducer, the outer diameter of the drive unit becomes large. Therefore, in particular, in the case of a pipe-in type sheet shutter device in which the drive unit is arranged inside the winding drum, the winding drum has to be enlarged because the diameter of the drive unit is large, and the entire sheet shutter device is large. There is a problem of becoming.

  Further, the hypocycloid speed reducer has a complicated structure, is very difficult to assemble, and is difficult to maintain. Further, as a reduction gear, a mechanism with less noise is required particularly in consideration of use at night.

  Therefore, it is conceivable to use a planetary speed reducer in order to simplify and reduce the size of the speed reducer. However, the planetary speed reducer has a problem that it does not have a good durability against an overload, particularly on the support structure of the carrier. That is, in the planetary gear mechanism, the carrier that supports the planetary gear generally has a floating structure (so-called structure in which the support is supported only by meshing of the gear) and is not supported by the case or the like. . In such a carrier support structure, since reliable support cannot be expected, the meshing state of each gear constituting the speed reducer is deteriorated. Therefore, if the opening and closing of the shutter is repeated for a long time in such a state, the shutter cannot be opened and closed satisfactorily.

  SUMMARY OF THE INVENTION An object of the present invention is to obtain a sheet shutter driving device that has a simple configuration, can be reduced in size, and has durability.

  Another object of the present invention is to reduce noise without increasing the size of the apparatus by using an appropriate gear for the planetary reduction gear.

  A sheet shutter driving device according to a first aspect is a device for driving a winding mechanism for opening and closing a sheet shutter provided in an opening, and an electric motor as a driving source and rotation input from the electric motor. A planetary speed reducer having an output shaft connectable to a winding mechanism; The planetary speed reducer includes a first sun gear connected to the shaft of the electric motor, a first internal gear provided on the outer periphery of the first sun gear, and a plurality of gears engaged with the first sun gear and the first internal gear. A first planetary gear, a first support that rotatably supports the first planetary gear and that is rotatably supported by two bearings that are spaced apart in the axial direction, and each gear and first support And a case to which the first internal gear is fixed.

  In this apparatus, the first support is supported by two bearings. For this reason, the clearance of the part which supports the 1st support body decreases, and shakiness and inclination by clearance can be controlled. Therefore, the durability of the gear supported by the first support and the gear meshing with the first support is improved, and the durability of the seat shutter driving device is improved.

  According to a second aspect of the present invention, in the apparatus of the first aspect, the electric motor is a DC brushless motor. In this case, the motor portion can also be reduced in size and increased in speed.

  According to a third aspect of the present invention, there is provided the seat shutter driving apparatus according to the first or second aspect, wherein each of the electric motor and the planetary speed reducer has a case and the cases are directly connected to each other. In this case, the axial length can be shortened, and the size can be further reduced. In addition, since no coupling (so-called coupler) is used between the motor and the planetary speed reducer, the inertia inside the speed reducer is reduced and the cost can be reduced.

  According to a fourth aspect of the present invention, there is provided the sheet shutter driving device according to any one of the first to third aspects, wherein the winding mechanism has a cylindrical winding drum for winding the sheet shutter around the outer periphery, The planetary reducer is arranged inside the winding drum. In this case, the entire apparatus can be reduced in size.

  According to a fifth aspect of the present invention, there is provided the seat shutter driving device according to any one of the first to fourth aspects, wherein the planetary speed reducer includes a second sun gear provided at an output end of the first support, and a second sun gear. A second internal gear fixed to the case on the outer periphery, a plurality of second planetary gears meshing with the second sun gear and the second internal gear, and the second planetary gear rotatably supported and connected to the output shaft And a second support. Each gear and the second support are housed in a case, and the second support is rotatably supported by the case. One of the two bearings that support the first support supports the first support with respect to the shaft of the electric motor, and the other supports the first support with respect to the second support.

  Here, one of the first supports is supported by the case through the shaft of the electric motor and the other through the second support, and the first support is reliably supported as described above. Thus, durability can be improved.

  According to a sixth aspect of the present invention, in the apparatus of the fifth aspect, the second support and the output shaft are integrally formed. In this case, the structure becomes simple.

  According to a seventh aspect of the present invention, there is provided the seat shutter driving device according to any one of the first to sixth aspects, wherein each gear constituting the planetary reduction gear is a helical gear. In this case, calming can be achieved.

  A seat shutter driving device according to an eighth aspect is a device for driving a winding mechanism for opening and closing the seat shutter provided in the opening, and includes an electric motor as a driving source and a planetary speed reducer. . The planetary reduction gear is a planetary gear train including a helical gear whose rotation is input from an electric motor and whose output shaft can be connected to a winding mechanism and whose total meshing ratio is 3.3 or more and 3.9 or less. have.

  In a conventional planetary speed reducer in this type of device, the total meshing rate of the helical gears is set in the range of 2 to 3. However, such a conventional apparatus is noisy and hinders use at night, for example.

  Therefore, in the present invention, the total meshing rate of the gear train including the helical gears constituting the planetary reduction gear is set to 3.3 or more and 3.9 or less. By setting the total meshing rate to 3.3 or more, noise can be suppressed as compared with the conventional device. Here, with respect to noise, it is preferable to increase the total meshing rate. In order to increase the total meshing rate, it is conceivable to increase the torsion angle of the gears constituting the planetary gear train or increase the tooth width. However, when the helix angle is increased, a thrust force is generated at the time of power transmission between the gears, and it is necessary to increase the capacity of a bearing or the like that bears this thrust force. Further, when the tooth width is increased, the axial dimension becomes longer, and in any case, the downsizing of the apparatus is hindered. Therefore, by making the total meshing rate 3.9 or less, the size of the apparatus is prevented from being increased while suppressing noise. Here, the “total meshing rate” is the sum of the front meshing rate and the overlapping meshing rate of the helical gear. Note that the “front meshing rate” and the “overlapping meshing rate” are derived by equations as shown in various documents, and details thereof are omitted here.

  According to a ninth aspect of the present invention, there is provided the seat shutter driving device according to the eighth aspect, wherein the planetary speed reducer includes a first sun gear connected to the shaft of the electric motor and a first inner gear provided on the outer periphery of the first sun gear. A gear, a plurality of first planetary gears meshed with the first sun gear and the first internal gear, and the first planetary gear rotatably support the two planetary gears and are rotatably supported by two bearings arranged at intervals in the axial direction. It has a supported first support, and a case in which each gear and the first support are accommodated and the first internal gear is fixed.

  In this case, since the first support is supported by the two bearings, as in the invention according to claim 1, it is possible to suppress backlash and inclination due to the clearance of the portion that supports the first support. The durability of can be improved.

  According to a tenth aspect of the present invention, there is provided the seat shutter driving device according to the eighth or ninth aspect, wherein the planetary speed reducer further includes a planetary gear train at a subsequent stage of the planetary gear train having a total meshing ratio of 3.3 to 3.9. doing.

  Here, in order to obtain a large reduction ratio in the planetary reduction gear, the planetary gear train may be configured in two stages. At this time, in the apparatus according to the present invention, the noise caused by the meshing of the gears is greatly influenced by the high rotational speed. Therefore, in the present invention, the total meshing rate is set to 3.3 or more and 3.9 or less for the planetary gear train on the front stage side having a higher rotational speed. In this case, since it is not necessary to increase the total meshing rate of the planetary gear train on the rear stage side, the thrust force generated in the planetary gear train on the rear stage side can be reduced, and it is not necessary to increase the tooth width. Larger size can be avoided.

  As described above, according to the present invention, it is possible to obtain a sheet shutter driving device that has a simple configuration and can be miniaturized and has durability. Moreover, noise can be suppressed without increasing the size of the apparatus.

[overall structure]
FIG. 1 shows a sheet shutter driving device according to an embodiment of the present invention. The seat shutter driving device is a device for driving a winding mechanism for opening and closing a sheet shutter (not shown), and includes a DC brushless motor 1 and a planetary speed reducer 2 as driving sources. The winding mechanism is a mechanism including a winding drum (not shown) around which the sheet shutter is wound around the outer periphery, and the DC brushless motor 1 and the planetary speed reducer 2 are disposed inside the winding drum.

[DC brushless motor]
A DC brushless motor (hereinafter simply referred to as a motor) 1 includes a case 5, a permanent magnet rotor housed in the case 5, and a stator around which a coil is wound. The motor 1 is of an inner rotor type, and the rotation shaft 6 of the central rotor protrudes from the case 5 to the planetary speed reducer 2 side.

[Planet reducer]
The planetary speed reducer 2 is for decelerating the rotation input from the motor 1 and outputting it to the winding mechanism side, and has a case 10 and a planetary mechanism 11 provided inside the case 10. ing. In the case 10, a flange portion 10 a provided on the motor 1 side is directly connected to a bracket 5 a of the case 5 of the motor 1 by a plurality of bolts 12.

  As shown in detail in FIG. 2, the planetary mechanism 11 is composed of a two-stage planetary gear train, and all the gears constituting the planetary gear train are helical gears. The first-stage planetary gear train has a first sun gear 15, a first internal gear 16, a plurality of first planetary gears 17, and a first carrier (first support) 18.

  The first sun gear 15 is fixed to the rotating shaft 6 of the motor 1. That is, as described above, the rotating shaft 6 of the motor 1 extends into the planetary speed reducer 2, and the first sun gear 15 is fixed to the tip of the rotating shaft 6 with a key. The tip of the rotating shaft 6 extends through the first sun gear 15 and further inside.

  The first internal gear 16 is disposed on the outer periphery of the first sun gear 15 and is fixed to the case 10. A part of the outer periphery of the first internal gear 16 is also fitted to the case 5 (bracket 5 a) of the motor 1.

  The plurality of first planetary gears 17 are rotatably supported by carrier pins 20 fixed to the first carrier 18 via needle roller bearings 21. The plurality of first planetary gears 17 mesh with the first sun gear 15 and also mesh with the first internal gear 16. A thrust washer 22 is provided on the side surface of the first planetary gear 17 with the case 5 of the motor 1.

  The first carrier 18 is an output part of the first-stage planetary gear train, and is supported by two ball bearings (so-called ball bearings) 23 and 24 arranged at intervals in the axial direction, as will be described later. Has been.

  The second stage planetary gear train includes a second sun gear 25, a second internal gear 26, a plurality of second planetary gears 27, and a second carrier (second support) 28.

  The second sun gear 25 is fixed to the output part of the first carrier 18. More specifically, the second sun gear 25 has a gear body 25a and shaft portions 25b and 25c formed integrally at both ends in the axial direction of the gear body 25a as shown in an enlarged view in FIG. Yes. On the other hand, the first carrier 18 has a through hole 18a at the center, and the shaft portion 25b of the second sun gear 25 is press-fitted and fixed to the hole 18a. As described above, the first carrier 18 and the second sun gear 25 are integrally formed. Of course, depending on the shape of both, it is possible to form with one member.

  The second internal gear 26 is disposed on the outer periphery of the second sun gear 25 and is fixed to the case 10. A stepped portion 10b is formed on the inner peripheral portion of the case 10, and one side surface of the second internal gear 26 is in contact with the stepped portion 10b.

  The plurality of second planetary gears 27 are rotatably supported by carrier pins 30 fixed to the second carrier 28 via needle roller bearings 31. The plurality of second planetary gears 27 mesh with the second sun gear 25 and also mesh with the second internal gear 26.

  The second carrier 28 is formed integrally with the output shaft 32 of the planetary speed reducer 2 and is rotatably supported by the case 10 by two ball bearings 33 and 34 arranged at intervals in the axial direction. Yes.

  The inner peripheral wall of the case 10 of the planetary reduction gear 2 is fitted with the second internal gear 26, the spacer 35, the ball bearing 33 supporting the second carrier 28 and the first internal gear 16 in order from the output side. The axial movement is restricted by the stepped portion 10b of the case 10 and the end surface of the case 5 of the motor 1. Oil seals 40 and 41 are provided between the rotating shaft 6 and the motor case 5 of the motor 1 and between the output shaft 32 and the speed reducer case 10, respectively, and filled in the planetary speed reducer 2. This prevents the lubricating oil from leaking outside.

  In general, the planetary speed reducer is considered to be vulnerable to overload, but in this embodiment, by using a helical gear, the surface pressure of the meshing portion of the gear is lowered, and sufficient resistance is obtained. I have it.

[Support structure of first carrier]
Next, the support structure of the first carrier 18 will be described in detail with reference to FIG. As described above, the first carrier 18 has the hole 18a penetrating through the central portion, and the stepped first and second recesses 18b and 18c on the motor 1 side. The first recess 18 b is provided to avoid interference with the first sun gear 15. Similarly, the second recess 18 c is provided to avoid interference with the first sun gear 15 and to attach a ball bearing 23 for supporting the first carrier 18. That is, the tip of the rotating shaft 6 of the motor 1 is provided to extend to the second recess 18 c, and one end side of the first carrier 18 is freely rotatable via the ball bearing 23 at the tip of the rotating shaft 6. It is supported.

  A third recess 28a is formed at the center of the end surface of the second carrier 28 on the motor 1 side. A shaft portion 25 c of the second sun gear 25 fixed integrally with the first carrier 18 is provided so as to enter the third recess 28 a, and the shaft portion 25 c is interposed via the ball bearing 24. The second carrier 28 is rotatably supported.

  In the configuration as described above, the first carrier 18 is provided by two ball bearings 23 and 24 provided at two positions spaced apart in the axial direction, that is, at the tip of the rotating shaft 6 of the motor and the second carrier 28. It will be supported. Since the second carrier 28 is supported by the case 10 by the two ball bearings 33 and 34, the first carrier 18 is supported by the case 10 at two places as a result.

[Gear meshing rate]
Next, the total meshing rate of the first stage planetary gear train will be described. In designing a planetary reduction gear, there is a method of increasing the total meshing rate of the gears as a method for suppressing noise. As a method of increasing the total meshing rate, there is a method of increasing the helix angle of the helical gear if the same module is used. However, as the helix angle of the helical gear is increased, the thrust force generated when the power is transmitted between the gears increases, and countermeasures against this thrust force are required. For example, the capacity of the bearing that receives the thrust force is increased. Further, the total meshing rate can be increased by increasing the tooth width, but the axial dimension becomes longer by increasing the tooth width. Therefore, there is a limit in increasing the total meshing rate, and it is necessary to set appropriate gear design conditions.

  Therefore, the present inventors measured the noise at that time while changing the total meshing rate by setting various torsion angles and tooth widths of the helical gears constituting the planetary reduction gear. The experimental results at this time are shown in FIG.

  FIG. 4A shows measured values, and FIG. 4B shows characteristics based on the measured values. The measurement conditions at this time were a load factor of 100% (54.8 Nm), and measurement was performed at a position 500 mm from the side of the planetary speed reducer (axial center). Further, the input rotational speed is 3000 rpm, the reduction ratio is “7” in the front stage, “3” in the rear stage, and the total reduction ratio is “21”. In FIG. 4A, “SG-PG” is the total meshing rate of the sun gear and the planetary gear, “PG-IG” is the total meshing rate of the planetary gear and the internal gear, and “Ave” is the average. The total meshing rate of each is shown. “CW” indicates that the rotation direction is clockwise, and “CCW” indicates that the rotation direction is counterclockwise. Further, in FIG. 4B, the horizontal axis represents the total meshing rate, and the vertical axis represents the noise value (dB-A).

  As is clear from FIG. 4B, the noise value is stabilized when the total meshing rate is 3.3 or more. That is, even if the total meshing rate is increased, the noise reduction effect is not obtained so much. Further, when the total meshing ratio exceeds 4, the noise value is remarkably lowered, but the thrust force and the tooth width are increased as described above. Therefore, in this embodiment, the helical angle of each helical gear is set to 25 °, and the total meshing rate is set to 3.3 or more and 3.9 or less. Further, by selecting a flat region in the characteristics shown in FIG. 4B, variations among products can be suppressed.

[Operation]
The operation will be briefly described. The rotation of the motor 1 is input from the rotating shaft 6 to the first sun gear 15 of the planetary reduction gear 2. The rotation input to the first sun gear 15 is transmitted to the first internal gear 16 via the plurality of first planetary gears 17, and is decelerated by a reduction ratio determined by the number of teeth and output to the first carrier 18. The Since the second sun gear 25 is integrally fixed to the first carrier 18, it is determined by the number of teeth of the second sun gear 25, the plurality of second planetary gears 27, and the second internal gear 26 in the same manner as described above. It is decelerated by the reduction ratio and output to the output shaft 32.

  A winding mechanism (not shown) is connected to the output shaft 32, and the winding drum rotates via the winding mechanism, whereby the sheet shutter is wound on or taken out from the winding drum and opened and closed. The Rukoto.

[Effect of the embodiment]
Here, a DC brushless motor is used as a driving source, and a planetary reduction gear having a helical gear type planetary gear train is used as a reduction gear. Furthermore, calming can be realized. In addition, the planetary speed reducer has a simple configuration, facilitates assembly, and facilitates maintenance. Since the motor 1 and the planetary speed reducer 2 are directly connected to each other's cases 5 and 10, the axial length can be shortened and the inertia inside the speed reducer can be reduced.

  In addition, since the first carrier 18 is supported by the two ball bearings 23 and 24 that are arranged at an interval in the axial direction, rattling and inclination of the first carrier 18 can be suppressed. Therefore, the durability of the first planetary gear 17 supported by the first carrier 18 and each gear meshing with the first planetary gear 17 is improved. In particular, in the present embodiment, a planetary speed reducer that is generally considered to be weak against overload is adopted as the speed reducer, and thus the durability deterioration is suppressed by the support structure of the first carrier 18.

  Furthermore, in this embodiment, in the planetary speed reducer, the total meshing rate of the gears constituting the upstream planetary gear train having a high rotational speed is 3.3 or more and 3.9 or less, so that the thrust force is suppressed, and Noise can be suppressed without increasing the tooth width.

[Other Embodiments]
In the embodiment, the first carrier 18 is supported by the rotating shaft 6 and the second carrier 28 of the motor. However, the first carrier 18 may be supported by the case and the second carrier.

1 is a configuration diagram of a sheet shutter driving device according to an embodiment of the present invention. FIG. The cross-sectional block diagram of the planetary reduction gear of the said apparatus. FIG. 3 is an enlarged partial view of FIG. 2. The figure which shows the noise measurement value at the time of changing the total meshing rate of each helical gear of a reduction gear, and the characteristic of relationship of both.

Explanation of symbols

1 DC brushless motor 2 planetary speed reducer 5 motor case 10 planetary speed reducer case 11 planetary mechanism 15 first sun gear 16 first internal gear 17 first planetary gear 18 first carrier 23, 24, 33, 34 ball bearing 25 Second sun gear 26 Second internal gear 27 Second planetary gear 28 Second carrier 32 Output shaft

Claims (10)

A sheet shutter driving device for driving a winding mechanism for opening and closing a sheet shutter provided in an opening,
An electric motor as a drive source;
A planetary speed reducer with rotation input from the electric motor and an output shaft connectable to the winding mechanism;
The planetary reducer is
A first sun gear coupled to the shaft of the electric motor;
A first internal gear provided on the outer periphery of the first sun gear;
A plurality of first planetary gears meshing with the first sun gear and the first internal gear;
A first support that rotatably supports the first planetary gear and that is rotatably supported by two bearings that are spaced apart in the axial direction;
A case in which each of the gears and the first support body is accommodated and the first internal gear is fixed;
Sheet shutter driving device.   The sheet shutter driving device according to claim 1, wherein the electric motor is a DC brushless motor.   The seat shutter driving device according to claim 1, wherein each of the electric motor and the planetary speed reducer has a case, and the cases are directly connected to each other. The winding mechanism has a cylindrical winding drum for winding the shutter around the outer periphery;
The electric motor and the planetary speed reducer are arranged inside the winding drum,
The sheet shutter drive device according to claim 1. The planetary speed reducer includes a second sun gear provided at an output end of the first support, a second internal gear fixed to the case on an outer periphery of the second sun gear, and the second sun gear. And a plurality of second planetary gears meshed with the second internal gear, and a second support body rotatably supporting the second planetary gear and coupled to the output shaft,
The gears and the second support are accommodated in the case, and the second support is rotatably supported by the case.
One of the two bearings supporting the first support supports the first support with respect to the shaft of the electric motor, and the other supports the first support with respect to the second support. ,
The sheet shutter drive device according to any one of claims 1 to 4.   The sheet shutter driving device according to claim 5, wherein the second support body and the output shaft are integrally formed.   The sheet shutter drive device according to any one of claims 1 to 6, wherein each of the gears constituting the planetary reduction gear is a helical gear. A sheet shutter driving device for driving a winding mechanism for opening and closing a sheet shutter provided in an opening,
An electric motor as a drive source;
A planet having a planetary gear train including a helical gear whose rotation is input from the electric motor and whose output shaft is connectable to the hoisting mechanism and whose total meshing ratio is 3.3 or more and 3.9 or less. A reducer,
A sheet shutter drive device comprising: The planetary reducer is
A first sun gear coupled to the shaft of the electric motor;
A first internal gear provided on the outer periphery of the first sun gear;
A plurality of first planetary gears meshing with the first sun gear and the first internal gear;
A first support that rotatably supports the first planetary gear and that is rotatably supported by two bearings that are spaced apart in the axial direction;
A case in which each of the gears and the first support body is accommodated and the first internal gear is fixed;
The sheet shutter driving device according to claim 8.   10. The seat shutter drive device according to claim 8, wherein the planetary speed reducer further includes a planetary gear train at a subsequent stage of the planetary gear train having a total meshing ratio of 3.3 to 3.9.

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