JP2019011828A - Electric actuator - Google Patents

Abstract

To secure rigidity without accompanying size enlargement as much as possible, in a reduction gear mechanism of an electric actuator.SOLUTION: A reduction gear mechanism comprises a first gear 45, and a second gear 49 which is engaged with the first gear 45. A tooth-tip circle diameter of the second gear 49 is set larger than a tooth-tip circle diameter of the first gear 45. The first gear 45 is constituted of a base part 46 located inside a radial direction rather than its tooth bottom circle, and a tooth part 47 protruding to the outside of the radial direction from an external peripheral face 461 of the base part 46. A protrusion 462 protruding to a second housing 23 side rather than an end face 471 of the tooth part 47 at the second housing 23 side is formed at the end face of the base part 46 at the second housing 23 side.SELECTED DRAWING: Figure 5

Description

  The present invention relates to an electric actuator for opening and closing a door or the like of a vehicle.

  Patent Document 1 describes an electric actuator for an electric sliding door device for opening and closing a sliding door of a vehicle. In the electric actuator for the electric sliding door device of Patent Document 1, an electric motor and a reduction gear mechanism are accommodated inside a housing. The rotating shaft of the electric motor is drivingly connected to a reduction gear mechanism. The reduction gear mechanism decelerates the input rotational force to a rotational speed lower than the rotational speed of the rotating shaft of the electric motor, and outputs it as the rotation of the output shaft of the electric actuator.

Japanese Patent Laid-Open No. 2006-108797

  An electric actuator for an electric sliding door device as described in Patent Document 1 is disposed in a limited space such as the inside of a sliding door or the vicinity of a door opening in a vehicle body. Therefore, it is preferable to reduce the size of the electric actuator by reducing the size of the reduction gear mechanism. Further, not only the electric slide door device but also an electric actuator applied to an electric back door device that is opened and closed electrically, a slide panel device of a sunroof, and the like are preferably similarly reduced in size. However, if the gear is downsized to reduce the size of the reduction gear mechanism, it is difficult to ensure the strength required for the gear. Therefore, the gear of the reduction gear mechanism is required to have a structure that can ensure strength without increasing the size as much as possible.

  In order to solve the above problems, the present invention is a housing, an electric motor housed in the housing, and housed in the housing and connected to the rotating shaft of the electric motor. A reduction gear mechanism that decelerates and outputs the rotation speed of the rotation shaft, and a gear provided in the reduction gear mechanism includes a base portion that forms a radially inner side from a root circle of the gear, A plurality of teeth protruding outward in the radial direction from the outer peripheral surface, and a protruding portion protruding from the end surface of the teeth is provided on the end surface of the base in the central axis direction of the gear.

  According to the above configuration, even if stress acts on the end of the gear tooth bottom (outer peripheral surface of the base portion) in the central axis direction of the gear, the stress can be released to the protruding portion. Therefore, even if it does not enlarge the diameter of the base part of a gearwheel, it can suppress that a base part breaks. That is, the strength of the gear can be ensured without increasing the size.

  In the above invention, the end surface of the tooth portion in the central axis direction on the side where the protruding portion is provided is provided with an inclined surface that protrudes toward the protruding portion toward the radially inner side. It may be done.

  In the said structure, since the protrusion part protrudes with respect to the end surface of a tooth | gear part, the level | step difference arises in both, and stress concentrates on this level | step-difference part easily and acts. According to the above configuration, the stress that tends to concentrate on the stepped portion between the end surface of the tooth portion and the protruding portion is easily distributed and applied to the inclined surface that is the end surface of the tooth portion. Therefore, it is possible to appropriately prevent the gear from being damaged starting from the stepped portion between the end face of the tooth portion and the protruding portion.

  In the above invention, the reduction gear mechanism includes a first gear and a second gear having a tooth tip diameter larger than that of the first gear and meshing with the first gear, and has the protrusion. The gear which is carrying out may be the first gear.

  In the above configuration, since the tip diameter of the second gear is larger than that of the first gear, the first gear rotates at a higher speed than the second gear. The burden is greater. In such a 1st gearwheel, it is especially suitable to employ | adopt the structure which provides a protrusion part in a base and ensures intensity | strength.

  In the above invention, the length of the tooth portion of the second gear in the central axis direction of the second gear is shorter than the length of the tooth portion of the first gear in the central axis direction of the first gear. The end surface of the tooth portion in the two gears may be located inside the end surface of the tooth portion of the first gear in the central axis direction of the first gear.

  In the above configuration, the tooth portion of the second gear is not in contact with the end of the tooth portion of the first gear. Therefore, the force from the second gear does not act directly near the end face of the tooth portion of the first gear. Therefore, it can reduce more appropriately that a stress acts on the level | step difference between the end surface of a tooth | gear part, and a protrusion part.

In the above invention, the first gear may be formed of a material having a lower impact strength or static strength than the second gear.
In the above configuration, the first gear has a lower impact strength or static strength and is more likely to break. It is particularly preferable to employ a configuration in which the first gear is configured so that the protruding portion protrudes from the end surface of the tooth portion to ensure strength.

  According to the present invention, in the electric actuator, the strength of the gear can be ensured without increasing the diameter of the tip circle of the gear of the reduction gear mechanism.

The schematic block diagram of an electric slide door provided with an electric actuator. The top view which shows the internal structure of an electric actuator. The perspective view which shows the internal structure of an electric actuator. FIG. 4 is a sectional view taken along line 4-4 in FIG. The enlarged view of the meshing part of the 1st gearwheel and the 2nd gearwheel in a reduction gear mechanism. The enlarged view of the 1st gearwheel in a reduction gear mechanism. The figure which shows the reference example of the conventional gearwheel.

  Hereinafter, an embodiment of an electric actuator will be described with reference to FIGS. 1 to 6 as an embodiment applied to an electric sliding door device of a vehicle. First, a schematic configuration of the electric sliding door device 10 will be described.

  As shown in FIG. 1, the electric slide door device 10 includes a slide door 11 for closing a door opening that is open on a side surface of a vehicle body in a vehicle. A plurality (three in FIG. 1) of rails 12 are installed on the vehicle body so as to extend in the vehicle front-rear direction. The slide door 11 is attached to the vehicle body so as to be slidable in the vehicle longitudinal direction, which is the extending direction of the rail 12.

  An electric actuator 20 is provided inside the slide door 11. Further, the slide door 11 incorporates a conversion mechanism 15 that converts the rotational torque output from the electric actuator 20 into a force in the vehicle front-rear direction and transmits the force to the slide door 11. The conversion mechanism 15 includes, for example, a rotating drum that is rotated by the rotating torque of the electric actuator 20 and a cable that is wound around the rotating drum. The cable of the conversion mechanism 15 is connected to the slide door 11, and is drawn out of the rotary drum or drawn into the rotary drum as the rotary drum of the conversion mechanism 15 rotates.

Next, the electric actuator 20 will be described.
As shown in FIG. 4, the electric actuator 20 includes a housing 21 including a first housing 22 and a second housing 23 disposed to face the first housing 22. The first housing 22 includes a bottom wall 221 and a side wall 222 erected from the outer edge of the bottom wall 221 to the second housing 23 side (upper side in FIG. 4). Similarly, the second housing 23 includes a bottom wall 231 and a side wall 232 erected from the outer edge of the bottom wall 231 to the first housing 22 side (lower side in FIG. 4). The bottom wall 231 of the second housing 23 has substantially the same shape as the bottom wall 221 of the first housing 22 in plan view. The front end of the side wall 232 of the second housing 23 is abutted against the front end of the side wall 222 of the first housing 22, and the second housing 23 is fixed to the first housing 22 with a bolt or the like (not shown) in this state. . Due to the second housing 23 and the first housing 22, the housing 21 has a flat box shape as a whole, and an accommodation space is defined inside. As shown in FIG. 3, in this embodiment, an opening portion 223 in which the side wall 222 is not erected is provided on a part of the outer edge of the first housing 22. The opening 223 constitutes an opening that communicates the internal space of the housing 21 with the outside when the first housing 22 and the second housing 23 are disposed to face each other. A connector (not shown) for supplying power to and controlling the electric actuator 20 is disposed in the opening.

  As shown in FIG. 3, a surrounding wall 25 extending in an arc shape is provided upright from the bottom wall 221 of the first housing 22. The standing length of the surrounding wall 25 from the bottom wall 221 is substantially the same as the standing length of the side wall 222. As shown in FIG. 2, the surrounding wall 25 extends in a “C” shape when viewed from above, and the open portion of the “C” shape faces the center side in the surface direction of the bottom wall 221. It extends.

  As shown in FIG. 3, the bottom wall 221 of the first housing 22 is provided with an accommodating portion 26 that is recessed by one step from the other portions. The accommodating portion 26 has a substantially circular shape when seen in a plan view. The accommodating portion 26 is adjacent to the surrounding wall 25 on the open side of the “C” type of the surrounding wall 25. Moreover, the accommodating part 26 is arrange | positioned in the position containing the center position of the surrounding wall 25 extended in circular arc shape.

  As shown in FIG. 2, an electric motor 30 is accommodated in the first housing 22 (housing 21). The electric motor 30 has a motor body 31 having a substantially annular outer shape, which includes a stator core, windings, a rotor, and the like. The outer diameter of the motor body 31 is slightly smaller than twice the distance from the center position of the surrounding wall 25 to the surrounding wall 25 (the diameter of the arc of the surrounding wall 25). The rotating shaft 32 protrudes on both sides in the central axis direction with respect to the motor main body 31. The rotating shaft 32 is rotatable with respect to the motor main body 31.

  As shown in FIGS. 2 and 4, the motor main body 31 of the electric motor 30 is disposed inside the surrounding wall 25 extending in an arc shape (inside in the radial direction of the arc). As shown in FIG. 4, the rotating shaft 32 of the electric motor 30 is rotatably supported by the bottom wall 221 (accommodating portion 26) of the first housing 22 and the bottom wall 231 of the second housing 23 via a bearing B1. Yes. 2 and 4, the structure of the motor main body 31 in the electric motor 30 is illustrated in a simplified manner.

  As shown in FIG. 3, a reduction gear mechanism 40 that decelerates and outputs the rotation speed of the rotation shaft 32 of the electric motor 30 is accommodated in the housing 21. The reduction gear mechanism 40 includes an intermediate shaft 41 rotatably supported on the bottom wall 221 (accommodating portion 26) of the first housing 22 and the bottom wall 231 of the second housing 23 via a bearing B2. The intermediate shaft 41 extends in parallel with the rotation shaft 32 of the electric motor 30. The intermediate shaft 41 is located in the accommodating portion 26 in the first housing 22.

  As shown in FIG. 4, the first pulley 42 of the reduction gear mechanism 40 is attached to the tip of the rotating shaft 32 of the electric motor 30 on the first housing 22 side. The first pulley 42 is fixed to the rotary shaft 32 so as to rotate integrally with the rotary shaft 32 of the electric motor 30. The first pulley 42 is made of an insulating resin.

  A second pulley 43 is attached to an end of the intermediate shaft 41 of the reduction gear mechanism 40 on the first housing 22 side. The second pulley 43 is fixed to the intermediate shaft 41 so as to rotate integrally with the intermediate shaft 41. The outer diameter of the second pulley 43 is larger than the outer diameter of the first pulley 42. In this embodiment, almost the entire second pulley 43 is located in the accommodating portion 26 of the first housing 22.

  As shown in FIG. 3, an endless (annular) belt 44 is wound around the first pulley 42 and the second pulley 43 in the reduction gear mechanism 40. The belt 44 is an insulating belt formed of fiber-containing rubber having a glass core wire.

  As shown in FIG. 4, a first gear 45 is provided on the second housing 23 side (upper side in FIG. 4) from the attachment position of the second pulley 43 on the intermediate shaft 41. The diameter of the tip circle of the first gear 45 is smaller than the outer diameter of the second pulley 43. As shown in FIG. 3, the first gear 45 is a so-called bevel gear. In this embodiment, the first gear 45 is integrally formed with the second pulley 43 and rotates together with the second pulley 43 and the intermediate shaft 41. The first gear 45 and the second pulley 43 are formed of an insulating resin. Specifically, the first gear 45 and the second pulley 43 are made of polyphenylene sulfide (PPS) to which rubber is added. In this embodiment, the reinforcing fibers such as glass fibers and carbon fibers are not added to the PPS that forms the first gear 45 and the second pulley 43.

  As shown in FIG. 4, the reduction gear mechanism 40 includes an output shaft 48 rotatably supported on the bottom wall 221 of the first housing 22 and the bottom wall 231 of the second housing 23 via a bearing B3. The output shaft 48 extends in parallel to the intermediate shaft 41 and the rotation shaft 32 of the electric motor 30. As shown in FIG. 2, the output shaft 48 is located on the side opposite to the rotating shaft 32 side of the electric motor 30 (left side in FIG. 2) with respect to the intermediate shaft 41.

  As shown in FIG. 4, a second gear 49 is attached to the output shaft 48. The second gear 49 is fixed to the output shaft 48 so as to rotate integrally with the output shaft 48. The tooth tip circle diameter of the second gear 49 is larger than the tooth tip circle diameter of the first gear 45. As shown in FIG. 3, the second gear 49 is a so-called bevel gear and meshes with the first gear 45. The second gear 49 is formed of an insulating resin. Specifically, the second gear 49 is made of polyoxymethylene (POM). In this embodiment, the reinforcing fiber such as glass fiber or carbon fiber is not added to the POM constituting the second gear 49.

  As shown in FIG. 5, the first gear 45 includes a base portion 46 that is radially inward of the root circle, and a plurality of tooth portions 47 that protrude radially outward from the outer peripheral surface 461 of the base portion 46. It is configured. In addition, a protruding portion 462 that protrudes toward the second housing 23 from the end surface 471 of the tooth portion 47 on the second housing 23 side is provided on the end surface of the base portion 46 on the second housing 23 side. The outer diameter of the protruding portion 462 is the same as the diameter of the root circle in the first gear 45 (the diameter of the base portion 46). The edge on the second housing 23 side on the outer peripheral surface of the protrusion 462 has a shape that is chamfered (R chamfered) in an arc shape.

  As shown in FIGS. 5 and 6, among the end surfaces of the tooth portions 47 of the first gear 45 in the central axis direction, the end surface on the side where the protruding portion 462 is provided, that is, the end surface 471 on the second housing 23 side, An inclined surface is provided. Specifically, the end surface 471 of the tooth portion 47 is provided with an inclined surface that protrudes toward the protruding portion 462 (second housing 23 side) toward the radially inner side of the first gear 45. In this embodiment, the end surface 471 of the tooth portion 47 has a substantially planar C chamfer shape.

  As shown in FIG. 5, the length L2 of the tooth tip of the tooth portion of the second gear 49 in the central axis direction of the second gear 49 is the same as that of the tooth portion 47 of the first gear 45 in the central axis direction of the first gear 45. It is smaller than the length L1 of the tooth tip. The second gear 49 is located on the inner side (on the first housing 22 side) than the end surface 471 of the tooth portion 47 of the first gear 45 in the central axis direction of the first gear 45. That is, the end of the first gear 45 on the end surface 471 side of the tooth portion 47 is not in contact with the second gear 49.

Next, the operation (action) of the electric actuator 20 configured as described above will be described.
When the electric motor 30 is driven and the rotating shaft 32 rotates, the first pulley 42 rotates integrally with the rotating shaft 32. When the first pulley 42 rotates, the rotational force is transmitted to the second pulley 43 through the belt 44, and the second pulley 43 rotates. At this time, since the diameter of the second pulley 43 is larger than that of the first pulley 42, the rotation speed of the second pulley 43 is slower than that of the first pulley 42 (the rotating shaft 32 of the electric motor 30). That is, the first pulley 42, the belt 44, and the second pulley 43 reduce the rotational speed.

  When the second pulley 43 rotates, the first gear 45 rotates together with the second pulley 43. When the first gear 45 rotates, the second gear 49 meshing with the first gear 45 rotates. At this time, since the second gear 49 has a larger tip diameter than the first gear 45, the rotational speed of the second gear 49 is slower than the rotational speed of the first gear 45 (second pulley 43). That is, the first gear 45 and the second gear 49 reduce the rotational speed. The rotation of the second gear 49 is output from the electric actuator 20 as the rotation of the output shaft 48.

The electric actuator 20 configured as described above has the following effects.
(1) As described above, in the above-described embodiment, the tooth tip circle diameter of the second gear 49 in the reduction gear mechanism 40 is larger than the tooth tip circle diameter of the first gear 45. Therefore, the rotation speed of the first gear 45 is higher than that of the second gear 49 and the first gear 45 is likely to be burdened.

  Here, as shown in FIG. 7, the protruding portion 462 does not protrude from the end surface of the base portion 46A of the first gear 45A rotating together with the intermediate shaft 41A, and the end surface of the base portion 46A is flush with the end surface of the tooth portion 47A. Suppose that In this case, the stress acting on the first gear 45A tends to concentrate on the axial end portion P of the tooth bottom of the first gear 45A (the outer peripheral surface 461A of the base portion 46A). If stress is concentrated on the end portion P, damage such as cracking may occur in the base portion 46A.

  In this regard, according to the above embodiment, as shown in FIG. 6, stress is applied to the end portion P in the central axis direction of the first gear 45 in the tooth bottom of the first gear 45 (the outer peripheral surface 461 of the base 46). Even if this acts, the stress can be released to the protrusion 462. The protruding portion 462 is not provided with the tooth portion 47, and the stress from the second gear 49 does not act directly. Therefore, even if the stress from the end portion P acts on the protruding portion 462, it is unlikely that the protruding portion 462 is damaged due to the stress. As a result, even if the diameter of the base portion 46 of the first gear 45 is not increased, the occurrence of breakage in the base portion 46 can be suppressed. That is, the strength of the first gear 45 can be ensured without increasing the size.

  (2) As described above, in the above embodiment, since the protruding portion 462 protrudes with respect to the end surface 471 of the tooth portion 47, a step is generated at the boundary between the protruding portion 462 and the tooth portion 47. Therefore, the stress acting on the first gear 45 is likely to be concentrated and act on the step portion between the protruding portion 462 and the tooth portion 47. According to the above embodiment, since the end surface 471 of the tooth portion 47 of the first gear 45 is an inclined surface, stress that tends to concentrate on the step portion between the protruding portion 462 and the tooth portion 47 is applied to the tooth. It is easy to act on the end surface 471 of the portion 47. Therefore, it is possible to appropriately prevent the first gear 45 from being damaged starting from the stepped portion between the end surface 471 of the tooth portion 47 and the protruding portion 462.

  (3) In the above embodiment, the end of the first gear 45 on the end surface 471 side of the tooth portion 47 is not in contact with the second gear 49. Therefore, the force from the second gear 49 does not directly act on the vicinity of the end surface 471 of the tooth portion 47 of the first gear 45. Therefore, it can reduce more appropriately that a stress acts on the level | step-difference part between the end surface 471 of the tooth | gear part 47, and the protrusion part 462. FIG.

  (4) In the above embodiment, the second gear 49 is located on the inner side (first housing 22 side) than the end surface 471 of the tooth portion 47 of the first gear 45 in the central axis direction of the first gear 45. . Therefore, the second gear 49 is assembled with a slight inclination with respect to the first gear 45 due to an assembly error in manufacturing the electric actuator 20, or the second gear 49 is attached to the first gear 45 by vibration during use. On the other hand, even if the position shifts in the central axis direction, the meshing state of the second gear 49 and the first gear 45 can be maintained.

  (5) As described above, in the reduction gear mechanism 40, the first gear 45 is more likely to be subjected to a larger load than the second gear 49. Therefore, as a material for forming the first gear 45, impact strength and static strength are used. It is conceivable to use a material having a high value. However, in consideration of processability and cost in manufacturing, a material having a lower impact strength or static strength than a material forming the second gear 49 may be adopted as the material forming the first gear 45. is there. In this way, when the burdened first gear 45 is formed of a material having a relatively low impact strength or low static strength, the base portion 46 is provided with the protruding portion 462 or the end surface of the tooth portion 47 as described above. It is particularly preferable to make 471 an inclined surface. Examples of the impact test for measuring the impact strength include a Charpy impact test and an Izod impact test.

  (6) In the above embodiment, the members that transmit power in the reduction gear mechanism 40, that is, the first pulley 42, the second pulley 43, the belt 44, the first gear 45, and the second gear 49 are all insulative. It is made of material. Therefore, the abrasion powder generated when these members slide or the like adheres to the electric motor 30 or other electronic components (not shown) or circuit boards accommodated in the housing 21 to cause an electrical short circuit. There is no cause.

The above embodiment may be modified as follows.
-In above-mentioned embodiment, although the electric actuator 20 was applied to the electric sliding door apparatus 10, it can also be applied to another apparatus. For example, you may apply the electric actuator 20 of the said embodiment to the electric back door (electric luggage door), an electric sunroof apparatus, etc. of a vehicle.

  -The shape of the housing 21 is not restricted to the example of the said embodiment. If it is designed appropriately according to the shape of the electric motor 30 and the reduction gear mechanism 40 accommodated in the housing 21, the shape of the device to which the electric actuator 20 is applied (the electric sliding door device 10 in the example of the above embodiment), etc. Good.

  -Other than the electric motor 30 and the reduction gear mechanism 40 may be accommodated in the housing 21. For example, a control board for controlling the electric motor 30 and its related parts may be accommodated in the housing 21.

  If the reduction gear mechanism 40 has at least one gear and can reduce the rotation speed of the rotary shaft 32 of the electric motor 30 and output it as rotation of the output shaft 48, the configuration of the reduction gear mechanism 40 is as follows. It can be changed as appropriate. For example, a gear may be provided on the rotating shaft 32 of the electric motor 30 and the first gear 45 of the reduction gear mechanism 40 may be engaged with the gear. Moreover, in addition to each structure of the reduction gear mechanism 40 of the said embodiment, a gear, a pulley, etc. may be added and a reduction ratio may be raised. Further, in the above embodiment, the rotating shaft 32 of the electric motor 30, the intermediate shaft 41 of the reduction gear mechanism 40, and the output shaft 48 extend in parallel to each other, but a bevel gear or the like is applied as the gear of the reduction gear mechanism 40. Accordingly, the extending directions of the respective axes can be varied.

  The outer diameter of the protrusion 462 in the first gear 45 may be larger than the diameter of the root circle of the first gear 45 (the diameter of the base 46). In this case, depending on the shape of the end surface 471 (inclined surface) of the tooth portion 47 in the first gear 45, a part of the end surface 471 is partially connected to the protruding portion 462 and is in a continuous state. There is also. Furthermore, the outer diameter of the protrusion 462 in the first gear 45 can be made smaller than the diameter of the root circle of the first gear 45 (the diameter of the base 46).

A configuration similar to the protruding portion 462 in the first gear 45 may be applied to the base portion of the second gear 49 instead of or in addition to the protruding portion 462 of the first gear 45.
-When the protrusion part of the 2nd gearwheel 49 is provided, you may apply to the 2nd gearwheel 49 the structure which makes the end surface 471 of the tooth | gear part 47 in the 1st gearwheel 45 an inclined surface. That is, an inclined surface that protrudes toward the protruding portion 462 toward the radially inner side of the second gear 49 may be provided on the end surface 471 of the tooth portion 47 of the second gear 49.

  -The end surface 471 of the tooth part 47 in the first gear 45 may not have a C-chamfered shape. The end surface 471 may be, for example, an arcuate inclined surface (R chamfered shape) as long as the end surface 471 protrudes toward the protruding portion 462 toward the inner side in the radial direction.

  The relationship between the tooth tip length L1 of the tooth portion 47 of the first gear 45 and the tooth tip length L2 of the tooth portion of the second gear 49 is not limited to the above embodiment. For example, the tooth tip length L2 of the tooth portion of the second gear 49 may be equal to or longer than the tooth tip length L1 of the tooth portion 47 of the first gear 45. These length relationships may be determined as appropriate in consideration of the impact strength of the second gear 49 and the first gear 45.

The tip diameter of the second gear 49 may be equal to or smaller than the diameter of the tip of the first gear 45 as long as the reduction gear mechanism 40 as a whole can reduce the rotational speed.
-The material which comprises the 1st gearwheel 45 and the 2nd gearwheel 49 can be changed suitably. For example, the first gear 45 may be formed of the same material as the second gear 49 or may be formed of a material having a higher impact strength than the second gear 49.

  The first pulley 42, the second pulley 43, the belt 44, the first gear 45, and the second gear 49 in the reduction gear mechanism 40 are not necessarily formed of an insulating material. Any or all of these may be formed of a metal conductive material. In the above embodiment, the surrounding wall 25 is provided in the first housing 22, and the electric motor 30 is disposed on the inner side thereof. Therefore, the inside of the housing 21 is separated to some extent from the outside of the surrounding wall 25. Therefore, for example, even if wear powder is generated from the first gear 45 or the second gear 49, it is possible to suppress the wear powder from entering the electric motor 30 to some extent.

According to the embodiment and the modification, the following technical idea can be derived.
(A) The outer diameter of the protrusion is equal to the diameter of the root circle of the gear.
(B) The outer diameter of the protrusion is larger than the diameter of the root circle of the gear.

  DESCRIPTION OF SYMBOLS 10 ... Electric slide door apparatus, 11 ... Sliding door, 12 ... Rail, 15 ... Conversion mechanism, 20 ... Electric actuator, 21 ... Housing, 22 ... 1st housing, 221 ... Bottom wall, 222 ... Side wall, 223 ... Opening part, DESCRIPTION OF SYMBOLS 23 ... 2nd housing, 231 ... Bottom wall, 232 ... Side wall, 25 ... Enclosure wall, 26 ... Housing part, 30 ... Electric motor, 31 ... Motor main body, 32 ... Rotating shaft, 40 ... Reduction gear mechanism, 41 ... Intermediate shaft 42 ... 1st pulley, 43 ... 2nd pulley, 44 ... belt, 45 ... 1st gear, 46 ... base part, 461 ... outer peripheral surface, 462 ... projecting part, 47 ... tooth part, 471 ... end face, 48 ... output shaft 49 ... second gear, B1 ... bearing, B2 ... bearing, B3 ... bearing.

Claims (5)

A housing;
An electric motor housed in the housing;
A reduction gear mechanism that is housed in the housing and is drivingly connected to the rotation shaft of the electric motor, and that reduces and outputs the rotation speed of the rotation shaft;
The gear provided in the reduction gear mechanism has a base portion that forms a radially inner side than the root circle of the gear, and a plurality of tooth portions that protrude radially outward from the outer peripheral surface of the base portion,
An electric actuator, wherein a projecting portion that projects from an end surface of the tooth portion is provided on an end surface of the base portion in a central axis direction of the gear. Of the end surfaces of the tooth portions in the central axis direction, the end surface on the side where the protruding portion is provided is provided with an inclined surface that protrudes toward the protruding portion side toward the radially inner side. The electric actuator according to claim 1. The reduction gear mechanism includes a first gear and a second gear having a diameter of a tip circle larger than that of the first gear and meshing with the first gear;
The electric actuator according to claim 1, wherein the gear having the protruding portion is the first gear. The length of the tooth portion of the second gear in the central axis direction of the second gear is shorter than the length of the tooth portion of the first gear in the central axis direction of the first gear,
The end face of the tooth part in the second gear is located inside the end face of the tooth part of the first gear in the central axis direction of the first gear. Electric actuator. The electric actuator according to claim 3 or 4, wherein the first gear is formed of a material having a lower impact strength or static strength than the second gear.