JP6966895B2 - Geared motor - Google Patents

Description

The present invention relates to a geared motor assembly technique.

In Patent Document 1 below, a filter such as a ventilation port is reciprocated by a shaft body driven by a differential gear mechanism, and a cleaning member attached to the shaft body that rotates within a predetermined angle range adheres to the filter. A filter drive device for removing foreign matter is disclosed.

Japanese Unexamined Patent Publication No. 2017-60284

Some of the gear members constituting the geared motor have a fixed arrangement angle at the time of assembly. If such a gear member is assembled without interference with other members other than the regular arrangement angle, the operator may assemble the gear member at an incorrect arrangement angle.

In view of the above problems, an object to be solved by the present invention is to provide a geared motor capable of suppressing erroneous assembly of gear members.

In order to solve the above problems, the geared motor of the present invention includes a drive gear which is a gear member and a driven gear which is a gear member meshed with the drive gear, and the drive gear has substantially the same pitch circle. The module has two spur gears, a drive-side first gear and a drive-side second gear, and the formation range of the drive-side first gear and the drive-side second gear is at least in the circumferential direction of the drive gear. The driven gear has a driven side first gear and a driven side second gear, which are two spur gears having substantially the same pitch circle but different modules, and the driven side first gear and the driven side are partially overlapped. The formation range of the second gear overlaps at least a part thereof in the circumferential direction of the driven gear, and the driving gear and the driven gear are a combination of the driving side first gear and the driven side first gear. The drive side second gear and the driven side second gear are combined, and the drive gear has the shape of the drive side reference tooth portion which is one of the teeth of the drive side first gear and the drive side. The combination with the shape of the tooth portion of the drive-side second gear at the circular pitch of the reference tooth portion is the shape of the tooth portion of the drive-side first gear at the circular pitch of the tooth portion adjacent to the drive-side reference tooth portion. It is characterized in that it is different from the combination with the shape of the tooth portion of the second drive side gear.

Two spur gears (hereinafter, also referred to as "first and second gears") having the same pitch circle but different modules are provided on the two gear members, and both the first and second gears are meshed with each other. , These gear members can be meshed only at a specific relative angle in which the tooth profiles of both the first and second gears match, and the arrangement at other angles is restricted. This makes it possible to prevent erroneous assembly of the gear member.

Further, the drive-side meshing gear, which is one of the drive-side first gear and the drive-side second gear, has a larger tooth width than the drive-side positioning gear, which is the other gear. The drive-side meshing gear is meshed with the driven-side first gear or the driven-side second gear to be combined in contact with the tooth portion, and the drive-side positioning gear after assembly is the combination thereof. It is preferable that the tooth portion does not come into contact with the driven-side first gear or the driven-side second gear. Further, the driven side meshing gear, which is one of the driven side first gear and the driven side second gear, has a larger tooth width than the driven side positioning gear, which is the other gear. The driven-side meshing gear is meshed with the driven-side first gear or the driving-side second gear to be combined in contact with the tooth portion, and the driven-side positioning gear after assembly is the combination thereof. It is preferable that the tooth portion does not come into contact with the drive-side first gear or the drive-side second gear.

By meshing with the other gear with a gear having a large tooth width, a larger torque can be stably transmitted, and a decrease in component life due to wear or breakage of the tooth portion can be suppressed.

Further, the driven gear has the shape of the driven side reference tooth portion which is one of the tooth portions of the driven side first gear and the tooth portion of the driven side second gear at the circular pitch of the driven side reference tooth portion. The combination with the shape is different from the combination of the shape of the tooth portion of the driven side first gear and the shape of the tooth portion of the driven side second gear at the circular pitch of the tooth portion adjacent to the driven side reference tooth portion. Is preferable.

Further, the geared motor of the present invention further includes a drive source and a power transmission member that transmits the driving force of the drive source to the drive gear, and the drive gear reciprocates in the circumferential direction by the power transmission member. It may be configured to be used.

Further, it is preferable that the drive gear has a gap portion, which is a portion in which a tooth portion is not formed, between the drive side first gear and the drive side second gear in the axial direction thereof. Further, it is preferable that the driven gear has a gap portion, which is a portion in which a tooth portion is not formed, between the driven side first gear and the driven side second gear in the axial direction thereof.

By providing a gap between the first and second gears, the teeth of one of the first and second gears are prevented from interfering with the other gear, and the drive gear and the driven gear operate smoothly. Can be made to.

Further, it is preferable that at least one of the drive gear and the driven gear meshes with the other in a predetermined angle range that is not the entire circumference in the circumferential direction thereof.

By limiting the range in which the tooth portions are meshed with the total length on the pitch circles of the first and second gears, the degree of freedom in designing the pitch circles of the first and second gears and the module is increased.

Further, it is preferable that the drive side first gear and the drive side second gear are formed in a predetermined angle range which is not the entire circumference in the circumferential direction of the drive gear. Further, it is preferable that the driven gear has the driven side first gear and the driven side second gear formed within a predetermined angle range which is not the entire circumference in the circumferential direction.

By limiting the range of forming the tooth portion in the total length on the pitch circle of the first and second gears, the degree of freedom in designing the pitch circles of the first and second gears and the module is increased.

Further, in the drive gear, the combination of the shape of each tooth portion of the drive side first gear and the shape of the tooth portion of the drive side second gear at the circular pitch of each tooth portion is the drive side first. The configurations may be different for all teeth of the gear. Further, in the driven gear, the combination of the shape of each tooth portion of the driven side first gear and the shape of the tooth portion of the driven side second gear at the circular pitch of each tooth portion is the driven side first. The configurations may be different for all teeth of the gear.

Since the combination of the tooth portions of the first and second gears is unique throughout all the tooth portions, it is possible to prevent the drive gear and the driven gear from engaging with each other at a meshing angle other than the normal meshing angle.

Further, the drive gear is a perfect circular gear member in which the drive-side first gear and the drive-side second gear are formed on the entire circumference in the circumferential direction, and the number of teeth of the drive-side first gear and the number of teeth of the drive-side first gear The greatest common divisor of the number of teeth of the drive-side second gear may be two. Further, the driven gear is a perfect circular gear member in which the driven side first gear and the driven side second gear are formed on the entire circumference in the circumferential direction, and the number of teeth of the driven side first gear and the number of teeth of the driven side first gear The greatest common divisor of the number of teeth of the driven side second gear may be two.

By forming these tooth portions so that the greatest common divisor of the number of teeth of the first and second gears is 2, the tooth portions can be formed symmetrically with respect to the plane line of sight. As a result, for example, even when two geared motors made upside down are used in combination, the same gear member can be used for these geared motors, and the component efficiency of the geared motor is improved.

Further, the geared motor of the present invention further includes a first output shaft and a second output shaft, and a differential gear mechanism using a planetary gear mechanism, and the first output shaft has a configuration of the differential gear mechanism. It is connected directly to any of the members, the sun gear member, the internal gear member, and the planetary carrier member, either directly or via another gear member, and the second output shaft is another component of the differential gear mechanism. The differential gear mechanism is directly connected to the gear member or via another gear member, and the output portion of the component member is switched according to the rotational resistance of the first output shaft or the second output shaft. May be good.

As described above, according to the geared motor of the present invention, it is possible to suppress erroneous assembly of gear members.

It is a perspective view which shows the appearance of a filter drive device. It is a top view which shows the drive mechanism of a geared motor. It is a side view sectional view which shows the internal structure of a differential gear mechanism. It is a top view of the drive gear and the driven gear. It is a side view which saw the drive gear and the driven gear from the B direction of FIG. It is a partial enlarged view explaining the misassembly prevention structure of a drive gear and a driven gear by a 1st gear and a 2nd gear.

[Outline of configuration]
(overall structure)
Hereinafter, embodiments of the present invention will be described with reference to the drawings. The following embodiment is an example of a filter drive device to which the geared motor of the present invention is applied (hereinafter, also referred to as “this example”). In the following description, "upper" and "lower" refer to directions parallel to the z-axis of the coordinate axis display drawn in FIG. 1, the + z side is referred to as "upper", and the -z side is referred to as "lower". do. Similarly, the direction parallel to the x-axis of the same coordinate axis display is the front and back of the filter drive device, and the direction parallel to the y-axis is the left and right of the filter drive device.

FIG. 1 is a perspective view showing the appearance of the filter driving device 9. The filter drive device 9 of this example includes a geared motor 1, a first output shaft 16, a second output shaft 17, and a rotating shaft 18, which are shaft bodies connected to the geared motor 1. The geared motor 1 rotates the first output shaft 16 and the second output shaft 17 in opposite directions, and reciprocates the rotation shaft 18 within a predetermined angle range. The geared motor 1 has a case 10 composed of case halves 11 and 12 divided into upper and lower parts. The first output shaft 16, the second output shaft 17, and the rotation shaft 18 of this example are connected to the lower surface of the case 10 and extend downward.

The first output shaft 16 and the second output shaft 17 are connected to a filter (not shown) provided at an intake port or an air outlet of a ventilation device, an air conditioner, or the like. A cleaning member (not shown) for this filter is attached to the rotating shaft 18. The geared motor 1 of this example alternately drives the first output shaft 16 and the second output shaft 17, which rotate in opposite directions, to reciprocate the filter in the directions of arrows A1 and A2 shown in FIG. Then, by bringing the cleaning member of the rotating shaft 18 into contact with the moving filter, foreign matter adhering to the filter is removed.

(Overview of drive mechanism)
FIG. 2 is a plan view showing the drive mechanism of the geared motor 1. The drive mechanism of the geared motor 1 is mainly a motor 20 as a drive source, a plurality of power transmission members 30 for decelerating and transmitting the rotation of the motor 20, a differential gear mechanism 40 connected to the power transmission member 30, and a drive. It is composed of a gear 50, a first output shaft drive gear 36 driven by a differential gear mechanism 40, a second output shaft drive gear 37, and a driven gear 60 driven by the drive gear 50. The first output shaft 16 is connected to the first output shaft drive gear 36. The second output shaft 17 is connected to the second output shaft drive gear 37. A rotating shaft 18 is connected to the driven gear 60.

The geared motor 1 has a connector portion 25 having a plurality of power feeding terminals 251, and the connector portion 25 is exposed to the outside of the case 10. The electric power supplied from the outside via the connector portion 25 is input to the motor 20 by a flat cable (not shown) connecting the power supply terminal 251 and the motor 20.

The power transmission member 30 of this example is composed of a first reduction gear 31, a second reduction gear 32, a third reduction gear 33, a link drive gear 34, and a link member 35.

The first reduction gear 31, the second reduction gear 32, and the third transmission gear 33 are composite gears in which large diameter gears and small diameter gears, which are two spur gears having different pitch circles, are stacked in the axial direction. The pinion gear 21 of the motor 20 meshes with the large-diameter gear 311 of the first reduction gear 31, and the small-diameter gear 312 of the first reduction gear 31 meshes with the large-diameter gear 321 of the second reduction gear 32. Similarly, the small diameter gear 322 of the second reduction gear 32 meshes with the large diameter gear 331 of the third transmission gear 33. The large-diameter gear portion 331 of the third transmission gear 33 meshes with the sun gear member 41 of the differential gear mechanism 40, and the small-diameter gear portion 331 of the third transmission gear 33 meshes with the link drive gear 34. As a result, the rotation of the pinion gear 21 is decelerated and transmitted to the differential gear mechanism 40 and the link drive gear 34.

(Swing mechanism)
A boss 341 protruding upward is formed on the upper surface of the link drive gear 34. The link member 35 has a rod-shaped arm having shaft holes formed at both ends in the longitudinal direction thereof, and a boss 341 of a link drive gear 34 is inserted into one of the shaft holes 351. Similarly, a boss 58 projecting upward is formed on the upper surface of the drive gear 50, and the boss 58 of the drive gear 50 is inserted into the other shaft hole 352 of the link member 35. The rotary motion of the link drive gear 34 is converted into a swing motion by the link member 35, whereby the drive gear 50 reciprocates within a predetermined angular range in its circumferential direction. Details of the structures of the drive gear 50 and the driven gear 60 will be described later.

(Differential gear mechanism)
FIG. 3 is a side sectional view showing the internal structure of the differential gear mechanism 40. The differential gear mechanism 40 is a mechanism that rotates the first output shaft 16 and the second output shaft 17 in opposite directions and alternately by using a planetary gear mechanism. The differential gear mechanism 40 has a sun gear member 41, an internal gear member 42, a plurality of planetary gears 43, and a planetary carrier member 44 as constituent members thereof.

The sun gear member 41 is a gear member having a substantially cylindrical shaft portion 41a and a flange portion 41c extending radially outward from the upper end of the shaft portion 41a. A shaft hole 41b penetrating vertically is formed at the radial center of the shaft portion 41a. A fixed shaft 13 provided in the case 10 is inserted into the shaft hole 41b. The sun gear member 41 is placed on the internal gear member 42 arranged below the sun gear member 41, and the upper case half body 11 is placed on the sun gear member 41. A sun gear 411 that meshes with the planetary gear 43 is formed on the outer peripheral surface of the shaft portion 41a. An input gear 412 that meshes with the large-diameter gear 331 of the third reduction gear 33 is formed on the outer peripheral surface of the flange portion 41c. As a result, the sun gear member 41 rotates the sun gear 411 in conjunction with the rotation of the third reduction gear 33, and rotates the planetary gear 43 with which the sun gear 411 meshes.

The internal gear member 42 is a gear member having a substantially bottomed cylinder shape. The bottom portion 42a of the internal gear member 42 is formed with a shaft hole 42b penetrating vertically at the center in the radial direction thereof. Similar to the sun gear member 41, the fixed shaft 13 is inserted into the shaft hole 42b. The internal gear member 42 is mounted on the lower case half body 12, and the sun gear member 41 is mounted on the internal gear member 42. An internal gear 421 that meshes with the planetary gear 43 is formed on the inner peripheral surface of the tubular portion 42c of the internal gear member 42, and a first output gear 422 that meshes with the first output shaft drive gear 36 is formed on the outer peripheral surface thereof. It is formed in. That is, when the planetary gear 43 does not revolve and the internal gear 421 rotates, the first output shaft drive gear 36 and the first output shaft 16 rotate in conjunction with this.

The planetary gears 43 are supported by the planetary carrier member 44, which will be described later, so as to be able to rotate and revolve. In this example, three planetary gears 43 are arranged at equal intervals in the circumferential direction of the planetary carrier member 44.

The planet carrier member 44 is a gear member having a substantially covered cylinder shape. The lid portion 44a of the planetary carrier member 44 is formed with a shaft hole 44b penetrating vertically at the center thereof in the radial direction. The shaft portion 41a of the sun gear member 41 is inserted into the shaft hole 44b. The planet carrier member 44 is arranged so as to be sandwiched between the sun gear member 41 and the internal gear member 42. The planetary carrier member 44 has a support shaft 44d that rotatably supports the planetary gear 43, and rotates with the revolution of the planetary gear 43. A second output gear 441 that meshes with the second output shaft drive gear 37 is formed on the outer peripheral surface of the tubular portion 44c of the planet carrier member 44. That is, when the arrangement angle of the internal gear 421 is fixed and the planetary gear 43 revolves, that is, when the planet carrier member 44 rotates, the second output shaft drive gear 37 and the second output shaft 17 rotate in conjunction with this. Will be done.

As a feature of the planetary gear mechanism, the rotation direction of the internal gear and the revolution direction of the planetary gear (rotation direction of the planetary carrier) are opposite to each other. Due to this property, the first output shaft drive gear 36 and the first output shaft 16 meshed with the internal gear member 42 and the second output shaft drive gear 37 and the second output shaft 17 meshed with the planetary carrier member 44 are mutually exclusive. Rotate in the opposite direction. Further, in this example, the reduction ratio for rotating the first output shaft drive gear 36 and the reduction ratio for rotating the second output shaft drive gear 37 are designed to be substantially the same. That is, almost the same torque is required to drive either of the drive gears 36 and 37.

The geared motor 1 of this example includes the differential gear mechanism 40, so that when the geared motor 1 is started, the geared motor 1 rotates whichever of the first output shaft 16 and the second output shaft 17 has the smaller rotational resistance. At this time, the constituent member meshing with the drive gears 36 and 37 of the other output shafts 16 and 17 acts as a fixed portion whose rotation is restricted. Then, when the filter has reached a dead end, the magnitude of the rotational resistance of the output shafts 16 and 17 is reversed, so that the other output shafts 16 and 17 start to rotate. By switching the output unit of the differential gear mechanism 40 in this way, the filter reciprocates in the directions of arrows A1 and A2 shown in FIG.

[Misassembly prevention structure]
(Double spur gear structure)
Hereinafter, the erroneous assembly prevention structure of the drive gear 50 and the driven gear 60 of this example will be described. FIG. 4 is a plan view of the drive gear 50 and the driven gear 60. FIG. 5 is a side view of the drive gear 50 and the driven gear 60 as viewed from the B direction of FIG.

The drive gear 50 is a gear member having a substantially oval shape in a plan view. The drive gear 50 is formed with a shaft hole 59, which is a through hole through which a support shaft 14 fixed to the case 10 is inserted. The drive gear 50 has a perfect circle portion 50a, which is a perfect circle range centered on the shaft hole 59, and a diameter-expanded portion, which is a portion of the perfect circle portion 50a that is extended radially outward from a part in the circumferential direction. It has 50b and. A part of the boss 58 is formed on the enlarged diameter portion 50b, whereby the rotation range of the drive gear 50 by the link member 35 is adjusted.

The drive gear 50 is formed with a drive-side first gear 51 and a drive-side second gear 52, which are two spur gears having the same pitch circle d1 but different modules, in a range excluding the enlarged diameter portion 50b from the entire circumference thereof. Has been done. The drive-side first gear 51 and the drive-side second gear 52 are arranged side by side in the axial direction of the drive gear 50. The module of the drive-side first gear 51 is smaller than the module of the drive-side second gear 52 (the module of the drive-side second gear 52 is larger than the module of the drive-side first gear 51), and the drive-side first gear 51 is The upper side and the drive side second gear 52 are arranged so as to be on the lower side. Further, the tooth tip of the drive-side second gear 52 extends radially outward from the tooth tip of the drive-side first gear 51. In this example, the diameter of the pitch circle of the drive-side first gear 51 and the diameter of the pitch circle of the drive-side second gear 52 are the same, but they can be absorbed by the backlash and the apex of the gears 51 and 52. If so, these gears 51 and 52 may be gears having different pitch circles.

Further, the drive-side second gear 52 of this example is a drive-side meshing gear having a tooth width larger than that of the drive-side first gear 51. The drive-side second gear 52 is in contact with the combined driven-side second gear 52 and meshes with the tooth portion. On the other hand, the drive-side first gear 51 is a drive-side positioning gear that is exclusively used for positioning with the driven gear 60, and the drive-side first gear 51 after assembly is the driven-side first gear 61. There is almost no contact with the teeth.

The driven gear 60 is a gear member having a substantially circular shape in a plan view. A shaft hole 69, which is a through hole through which the support shaft 15 is inserted, is formed at the radial center of the driven gear 60. On the lower surface of the driven gear 60, a key shaft 63 extending downward and connected to the rotating shaft 18 is formed (see FIG. 5). At the tip of the key shaft 63, a key portion 631 is formed which integrally rotates the rotary shaft 18 and the driven gear 60 by engaging with the rotary shaft 18 in the circumferential direction.

The driven gear 60 is formed with a driven side first gear 61 and a driven side second gear 62, which are two spur gears having the same pitch circle d2 but different modules, in a range excluding a part of the entire circumference thereof. .. The driven side first gear 61 and the driven side second gear 62 are arranged side by side in the axial direction of the driven gear 60. The module of the driven side first gear 61 is smaller than the module of the driven side second gear 62 (the module of the driven side second gear 52 is larger than the module of the driven side first gear 51), and the driven side first gear 61 is The upper side and the driven side second gear 62 are arranged so as to be on the lower side. Further, the tooth tip of the driven side second gear 62 extends radially outward from the tooth tip of the driven side first gear 61. In this example, the diameter of the pitch circle of the driven side first gear 61 and the diameter of the pitch circle of the driven side second gear 62 are the same, but they can be absorbed by the backlash and the apex of the gears 61 and 62. If so, these gears 61 and 62 may be gears having different pitch circles.

Further, the driven side second gear 62 of this example is a driven side meshing gear having a tooth width larger than that of the driven side first gear 61. The driven side second gear 62 meshes with the combined driven side second gear in contact with the tooth portion. On the other hand, the driven side first gear 61 is a driven side positioning gear which is a gear used exclusively for positioning with the drive gear 50, and the driven side first gear 61 after assembly is the drive side first gear 51. There is almost no contact with the teeth.

The modules of the drive-side first gear 51 and the driven-side first gear 61 are the same, and the modules of the drive-side second gear 52 and the driven-side second gear 62 are the same. The drive-side first gear 51 is meshed with the driven-side first gear 61, and the drive-side second gear 52 is meshed with the driven-side second gear 62. Hereinafter, the drive-side first gear 51 and the driven-side first gear 61 are collectively referred to as "first gears 51, 61", and the driven-side first gear 61 and the driven-side second gear 62 are collectively referred to as "second". Also called "gears 52, 62".

As described above, the drive gear 50 of this example is not a gear member that continuously rotates in the circumferential direction, but an irregularly shaped gear designed to reciprocate within a predetermined angle range by a link member 35. It is a member. Further, the tooth portion of the drive gear 50 is formed in the range of the perfect circular portion 50a. Further, in the driven gear 60 of this example, a part of the tooth portion in the circumferential direction thereof is omitted, and the range in which the driven gear 60 can be meshed with the drive gear 50 is limited. That is, in the drive gear 50 and the driven gear 60, the first gear 51, 61 and the second gear 52, 62 are formed within a predetermined angle range that is not the entire circumference in the circumferential direction thereof. For this reason, the drive gear 50 and the driven gear 60 of this example have a relative arrangement angle when they are assembled.

The drive gear 50 and the driven gear 60 of this example have first gears 51, 61 and second gears 52, 62, which are two spur gears having the same pitch circle but different modules, and these first gears 51. , 61 and both the second gears 52 and 62 are arranged to mesh with each other. As a result, the drive gear 50 and the driven gear 60 can be meshed only at a specific relative angle in which the unevenness of the teeth of both the first gears 51 and 61 and the second gears 52 and 62 match. Arrangement at angles is restricted. As a result, erroneous assembly of the drive gear 50 and the driven gear 60 is suppressed.

In addition, when two types of spur gears with different modules are formed on the same pitch circle over the entire circumference, there are cases where design restrictions become strict and the module size and pitch circle diameter must be compromised. be. On the other hand, the drive gear 50 and the driven gear 60 of this example have a pitch circle of the first gears 51 and 61 and the second gears 52 and 62 because the range in which the tooth portions are meshed is limited in the entire circumference thereof. The degree of freedom in module design is increased.

FIG. 6 is a partially enlarged view illustrating a structure for preventing erroneous assembly of the drive gear 50 and the driven gear 60 by the first gears 51 and 61 and the second gears 52 and 62.

The drive gear 50 and the driven gear 60 of FIG. 4 are meshed in the manner shown in FIG. 6 (a). FIG. 6A shows how both the first gears 51 and 61 and the second gears 52 and 62 of the drive gear 50 and the driven gear 60 are properly meshed.

On the other hand, in FIG. 6B, although the first gears 51 and 61 are arranged at relative angles that allow meshing as in FIG. 6A, the tooth portions of the second gears 52 and 62 match. However, these second gears 52 and 62 interfere with each other. Therefore, the drive gear 50 and the driven gear 60 are separated from each other from the normal relative positions. In this state, the support shafts 14 and 15 cannot be inserted through the drive gear 50 and the driven gear 60. That is, it is prevented that the drive gear 50 and the driven gear 60 are assembled to the geared motor 1 at an erroneous angle.

As shown in FIG. 4, the drive gear 50 of this example has the shape of each tooth portion of the drive side first gear 51 and the shape of the tooth portion of the drive side second gear 52 at the circular pitch of each tooth portion. The combination is different in all the teeth of the first gear 51 on the drive side. More specifically, for example, when the tooth portion 51a of the drive-side first gear 51 is used as the drive-side reference tooth portion, the shape of the tooth portion 51a and the drive-side second gear 52 at the circular pitch p1 of the tooth portion 51a. The combination with the shape of the tooth portion is designed to be unique in all the tooth portions of the first gear 51 on the drive side.

On the other hand, in the driven gear 60 of this example, for example, when the tooth portion 61a of the driven side first gear 61 is used as the driven side reference tooth portion, the shape of the tooth portion 61a and the driven side first in the circular pitch p2 of the tooth portion 61a. Combinations with the shape of the tooth portions of the two gears 62 are provided at three locations in all the tooth portions of the driven side first gear 61. Depending on the tooth portion of the driven side first gear 61, the combination of the above-mentioned shapes may be provided at four locations in all the tooth portions.

Even in the form of the driven gear 60 of this example, it is possible to suppress the risk of erroneous assembly of the driven gear 50 and the driven gear 60. For example, all the teeth of the driven side first gear 61 and the circles of these tooth portions. The combination with the shape of the tooth part of the driven side second gear 62 in the pitch is different over the entire circumference, and the apex gap and backlash of the first gears 51 and 61 and the second gears 52 and 62 are made smaller than in this example. You may. By doing so, the drive gear 50 and the driven gear 60 can be meshed only at one relative angle to the other at one arrangement angle. That is, it cannot be meshed except at the normal meshing angle. This makes it possible to more reliably prevent erroneous assembly of the drive gear 50 and the driven gear 60.

(Interference prevention structure)
As shown in FIG. 5, in the drive gear 50 of this example, a gap portion 53, which is a portion in which a tooth portion is not formed, is provided between the drive side first gear 51 and the drive side second gear 52. ing. By providing the gap 53, it is possible to prevent the tooth portion of one gear of the drive side first gear 51 and the drive side second gear 52 from interfering with the other gear, and the drive gear 50 and the driven gear 60 are smooth. Operation is guaranteed. The gap 53 does not have to be provided on the drive gear 50 side at all times, and may be provided on the driven gear 60 side. Alternatively, it may be provided on both the drive gear 50 and the driven gear 60.

(Reversible structure)
Further, as shown in FIG. 4, the drive gear 50 of this example is formed in a shape that is line-symmetrical with respect to the center line r1. Similarly, the driven gear 60 is also formed in a shape that is line-symmetrical with respect to the center line r2. That is, it is the same when manufacturing the geared motor 1 in which only the front and back (up and down (z direction)) are turned upside down while keeping the positional relationship of the front and rear (x direction) and left and right (y direction) of each part constituting the geared motor 1. It is possible to reuse the drive gear 50 and the driven gear 60.

More specifically, the tooth portion 51a of the drive gear 50 mentioned in the previous example is arranged at the position of the tooth portion 51b by turning the drive gear 50 upside down, and the tooth portion 61a of the driven gear 60 is the driven gear. By turning 60 upside down, it is arranged at the position of the tooth portion 61b. In this way, even if the front and back sides are reversed, the drive gear 50 and the driven gear 60 can be meshed in the same state as in this example.

In addition, for example, when the drive gear is a perfect circular gear member and teeth are formed on the entire circumference thereof, the greatest common divisor of the number of teeth of the drive side first gear and the drive side second gear is The tooth portion may be formed so as to be 2. By doing so, the tooth portions of the drive gear can be formed symmetrically with respect to the plane line of sight. As a result, as in the case of the drive gear 50 of this example, the risk of erroneous assembly can be suppressed while increasing the component efficiency of the drive gear. This also applies to the driven gear. The "true circle" here means a perfect circle that is not an ellipse or an ellipse like the drive gear 50.

Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various modifications can be made without departing from the gist of the present invention.

9 Filter drive device 1 Geared motor 16 1st output shaft 17 2nd output shaft 20 Motor (drive source)
30 Power transmission member 40 Differential gear mechanism 41 Sun gear member 42 Internal gear member 422 First output gear (output unit)
44 Planetary carrier member 441 Second output gear (output section)
50 Drive gear 51 Drive side first gear (drive side positioning gear)
51a Tooth (drive side reference tooth)
52 Drive-side second gear (drive-side meshing gear)
53 Gap 60 Driven gear 61 Driven side first gear (driven side positioning gear)
61a Tooth (driven reference tooth)
62 Driven side second gear (driven side meshing gear)
d1, d2 pitch circle p1, p2 circle pitch

Claims (15)

The drive gear, which is a gear member,
A driven gear, which is a gear member meshed with the drive gear, is provided.
The drive gear has a drive-side first gear and a drive-side second gear, which are two spur gears having substantially the same pitch circle but different modules.
The forming range of the drive-side first gear and the drive-side second gear overlaps at least a part thereof in the circumferential direction of the drive gear.
The driven gear has a driven side first gear and a driven side second gear, which are two spur gears having substantially the same pitch circle but different modules.
The forming range of the driven side first gear and the driven side second gear overlaps at least a part thereof in the circumferential direction of the driven gear.
In the driving gear and the driven gear, the driving side first gear and the driven side first gear are combined, and the driving side second gear and the driven side second gear are combined .
The drive gear has the shape of the drive-side reference tooth portion which is one of the teeth of the drive-side first gear and the shape of the tooth portion of the drive-side second gear at the circular pitch of the drive-side reference tooth. Is different from the combination of the shape of the tooth portion of the drive side first gear and the shape of the tooth portion of the drive side second gear at the circular pitch of the tooth portion adjacent to the drive side reference tooth portion. A geared motor that features that. The drive-side meshing gear, which is one of the drive-side first gear and the drive-side second gear, has a larger tooth width than the drive-side positioning gear, which is the other gear. ,
The drive-side meshing gear is meshed with the driven-side first gear or the driven-side second gear to be combined by bringing the tooth portion into contact with the tooth portion.
The geared motor according to claim 1, wherein the drive-side positioning gear after assembly is such that the tooth portion does not come into contact with the driven-side first gear or the driven-side second gear to be combined. Of the driven-side first gear and the driven-side second gear, the driven-side meshing gear, which is one of the gears, has a larger tooth width than the driven-side positioning gear, which is the other gear. ,
The driven side meshing gear is meshed with the driven side first gear or the driving side second gear to be combined by bringing the tooth portion into contact with the tooth portion.
The first or second aspect of the present invention, wherein the driven side positioning gear after assembly is not in contact with the drive side first gear or the drive side second gear to be combined with the tooth portion. Geared motor. The driven gear has the shape of the driven side reference tooth portion which is one of the tooth portions of the driven side first gear and the shape of the tooth portion of the driven side second gear at the circular pitch of the driven side reference tooth portion. Is different from the combination of the shape of the tooth portion of the driven side first gear and the shape of the tooth portion of the driven side second gear at the circular pitch of the tooth portion adjacent to the driven side reference tooth portion. The geared motor according to any one of claims 1 to 3 , wherein the geared motor is characterized in that. With the drive source
A power transmission member that transmits the driving force of the driving source to the driving gear is further provided.
The geared motor according to any one of claims 1 to 4 , wherein the drive gear reciprocates in the circumferential direction by the power transmission member. The claim is characterized in that the drive gear has a gap portion, which is a portion in which a tooth portion is not formed, between the first gear on the drive side and the second gear on the drive side in the axial direction thereof. The geared motor according to any one of claims 1 to 5. The claim is characterized in that the driven gear has a gap portion, which is a portion in which a tooth portion is not formed, between the driven side first gear and the driven side second gear in the axial direction thereof. The geared motor according to any one of claims 1 to 6. The one according to any one of claims 1 to 7 , wherein at least one of the drive gear and the driven gear meshes with the other in a predetermined angle range which is not the entire circumference in the circumferential direction thereof. Geared motor. The geared motor according to claim 8 , wherein the drive gear has the drive-side first gear and the drive-side second gear formed in a predetermined angle range that is not the entire circumference in the circumferential direction. The eighth or ninth aspect of the driven gear is characterized in that the driven side first gear and the driven side second gear are formed within a predetermined angle range which is not the entire circumference in the circumferential direction. The described geared motor. In the drive gear, the combination of the shape of each tooth portion of the drive side first gear and the shape of the tooth portion of the drive side second gear at the circular pitch of each tooth portion is the combination of the drive side first gear. The geared motor according to any one of claims 1 to 10 , wherein the geared motors are different in all teeth. In the driven gear, the combination of the shape of each tooth portion of the driven side first gear and the shape of the tooth portion of the driven side second gear at the circular pitch of each tooth portion is the combination of the driven side first gear. The geared motor according to any one of claims 1 to 11 , wherein the geared motors are different in all teeth. The drive gear is a perfect circular gear member in which the drive-side first gear and the drive-side second gear are formed on the entire circumference in the circumferential direction.
The geared motor according to any one of claims 1 to 7 , wherein the greatest common divisor of the number of teeth of the drive-side first gear and the number of teeth of the drive-side second gear is 2. The driven gear is a perfect circular gear member in which the driven side first gear and the driven side second gear are formed on the entire circumference in the circumferential direction.
Claims 1 to 7, wherein the number of teeth of the driven-side first gear and the teeth number of the greatest common divisor of the driven-side second gear is 2, and any one of claims 13 The described geared motor. The first output shaft and the second output shaft,
Further equipped with a differential gear mechanism using a planetary gear mechanism,
The first output shaft is directly connected to any one of the sun gear member, the internal gear member, and the planetary carrier member, which are constituent members of the differential gear mechanism, or is connected to the second output shaft via another gear member. The output shaft is connected to the other component of the differential gear mechanism directly or via another gear member.
One of claims 1 to 14 , wherein the differential gear mechanism switches the output unit of the component member according to the rotational resistance of the first output shaft or the second output shaft. The geared motor described in.

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