Motor device

Abstract

To provide a motor device in which a stable output characteristic can be obtained.SOLUTION: A motor device includes a reduction gear accommodation part 52 accommodating a pinion gear 38 and a face gear 60. The reduction gear accommodation part 52 has a lateral wall section 52b surrounding a radial outer side of the face gear 60. On a radial inner side of the lateral wall section 52b, a C-shaped stopper ring 54 for preventing the face gear 60 from moving in the axis direction of an output shaft 61a is disposed. Accordingly, in the reduction gear accommodation part 52, the face gear 60 can be supported in the axis direction thereof by the C-shaped stopper ring 54. Therefore, the face gear 60 can be prevented from rattling in the axis direction, and variations of an engagement state of the pinion gear 38 and the face gear 60 in each product can be suppressed. Consequently, a stable output characteristic can be obtained in each product .SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present invention relates to a motor device having a motor portion and a gear portion. [Background technology]

[0002] Conventionally, a motor device with a reduction mechanism that is small but can provide a large output has been adopted as a drive source for a power window device mounted on a vehicle such as an automobile. For example, Patent Document 1 describes a motor device with a reduction mechanism that includes a pinion gear having a pair of helical teeth, and a rotor having an output shaft and a helical gear. The pair of helical teeth and the helical gear are meshed with each other in the axial direction of the output shaft. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2020-034038 A Summary of the Invention [Problem to be solved by the invention]

[0004] In the technology described in Patent Document 1, the rotating body housed in the gear case is pressed down by the gear cover and the drum. This causes variations in the mounting accuracy of the gear cover to the gear case and the mounting accuracy of the drum to the motor device for each product, which may lead to the rotating body rattling in the axial direction. If the rotating body rattles in the axial direction, the gear meshing state changes, causing problems such as failure to obtain stable output characteristics.

[0005] An object of the present invention is to provide a motor device that can provide stable output characteristics. [Means for solving the problem]

[0006] In one embodiment of the present invention, a motor device having a motor section and a gear section includes a rotating shaft provided in the motor section, an output shaft provided in the gear section and rotated around an axis perpendicular to the axis of the rotating shaft, a first gear having a first tooth portion extending spirally in the axial direction of the rotating shaft, a second gear having a second tooth portion meshing with the first tooth portion in the axial direction of the output shaft and rotating the output shaft, and a housing that accommodates the first gear and the second gear, wherein the housing has a cylindrical wall portion that surrounds the radial outside of the second gear, and a movement restriction portion is provided on the radial inside of the cylindrical wall portion to prevent the second gear from moving in the axial direction of the output shaft. Effect of the Invention

[0007] According to the present invention, a motor device that can obtain stable output characteristics can be realized. [Brief description of the drawings]

[0008] [Figure 1] 1 is a perspective view of a motor device according to a first embodiment, as viewed from a cover member side. [Diagram 2] 2 is a perspective view of the motor device of FIG. 1 as viewed from the output shaft side. [Diagram 3] 2 is a cross-sectional view taken along the axial direction of an armature shaft of the motor device of FIG. 1. [Figure 4] 2 is a perspective view showing a reduction mechanism of the motor device of FIG. 1. [Diagram 5] 2 is a perspective view showing an assembly procedure of a gear portion of the motor device in FIG. 1. [Figure 6] 6 is a perspective view showing a procedure for assembling the motor unit to the gear unit in FIG. 5. FIG. [Figure 7] FIG. 11 is a perspective view of a motor device according to a second embodiment, as viewed from the cover member side. [Figure 8] 8 is a perspective view of the motor device of FIG. 7 as viewed from the bottom wall side of the gear case. [Figure 9] 8 is a cross-sectional view taken along the axial direction of an armature shaft of the motor device of FIG. 7. [Figure 10] 8 is a perspective view showing a reduction mechanism of the motor device of FIG. 7. [Figure 11] 8 is a perspective view showing an assembly procedure for the motor device of FIG. 7. [Figure 12] FIG. 11 is a perspective view of a face gear according to a third embodiment, as viewed from a meshing recess side. [Figure 13] FIG. 11 is a perspective view of a face gear according to a third embodiment, as viewed from the output shaft side. [Figure 14] FIG. 11 is a partially enlarged perspective view showing a reduction mechanism according to a fourth embodiment. [Figure 15] 15 is a side view of the pinion gear in FIG. 4 and the pinion gear in FIG. 14. [Figure 16] FIG. 15 is a partially enlarged plan view showing a meshing recess of the face gear of FIG. [Figure 17] 13 is a cross-sectional view taken along the axial direction of an armature shaft of a motor device according to a fifth embodiment. FIG. [Figure 18] FIG. 18 is a perspective view showing the face gear and the ring member of FIG. 17. [Figure 19] FIG. 13 is a partially enlarged cross-sectional view showing a face gear and a ring member according to a sixth embodiment. [Figure 20] FIG. 13 is a partially enlarged cross-sectional view showing a face gear and a gear case according to a seventh embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] [Embodiment 1] Hereinafter, the first embodiment of the present invention will be described in detail with reference to the drawings.

[0010] Figure 1 is an oblique view of the motor device of embodiment 1 seen from the cover member side, Figure 2 is an oblique view of the motor device of Figure 1 seen from the output shaft side, Figure 3 is a cross-sectional view along the axial direction of the armature shaft of the motor device of Figure 1, Figure 4 is an oblique view showing the reduction mechanism of the motor device of Figure 1, Figure 5 is an oblique view showing the assembly procedure of the gear portion of the motor device of Figure 1, and Figure 6 is an oblique view showing the assembly procedure of the motor portion relative to the gear portion of Figure 5.

[0011] 1 to 3 is used as a drive source for a power window device (not shown) installed in the door of a vehicle such as an automobile. Specifically, the motor device 10 includes a motor section 30 and a gear section 50, which are firmly connected to each other by a total of three fixing screws S1 (see FIGS. 1 and 2).

[0012] [Motor section] 1 to 3, the motor section 30 includes a yoke 31 that functions as a motor case. The yoke 31 is formed into a cylindrical shape with a bottom by pressing a steel plate (magnetic material) or the like, and is open at the front side in the longitudinal direction (left side in FIG. 3) and closed at the rear side in the longitudinal direction (right side in FIG. 3). The yoke 31 is formed so that the cross section perpendicular to the axial direction of the armature shaft 35 (see FIG. 3) is substantially elliptical. This gives the motor device 10 a flat shape as a whole, making it easy to install in a narrow space inside a door (not shown).

[0013] A total of four permanent magnets 32 (only two are shown in FIG. 3 ) having a cross section perpendicular to the axial direction of the armature shaft 35 formed into a substantially arc shape are fixed inside the yoke 31. In other words, the motor device 10 is a four-pole electric motor, and magnetic paths (not shown) formed by the respective permanent magnets 32 pass through the yoke 31.

[0014] Furthermore, an armature 33 is rotatably provided radially inside each permanent magnet 32 ​​via a predetermined air gap AG. A coil 34 made of enameled wire or the like is wound around an armature core 33a forming the armature 33 in a predetermined winding manner and with a predetermined number of turns.

[0015] An armature shaft 35 made of a round steel bar is fixed to the center of rotation of the armature 33. The axial rear side of the armature shaft 35 is rotatably supported by a first radial bearing B1 and a thrust bearing TB attached to the bottom 31a of the yoke 31.

[0016] The armature shaft 35 is provided in the motor section 30 and corresponds to the rotating shaft in the present invention.

[0017] The axial front side of the armature shaft 35 is fixed to the axial rear side of the pinion gear 38, and is rotatably supported by the second radial bearing B2 via the pinion gear 38. This allows the armature shaft 35 to rotate smoothly.

[0018] The second radial bearing B2 is attached to a brush holder holding portion 53 of the gear case 51.

[0019] 1 to 3, the axial direction of the armature shaft 35 is defined as the "front-rear direction." Also, the axial direction of the output shaft 61a perpendicular to the axial direction of the armature shaft 35 is defined as the "up-down direction." Furthermore, the direction perpendicular to both the axial direction of the armature shaft 35 (front-rear direction) and the axial direction of the output shaft 61a (up-down direction) is defined as the "left-right direction."

[0020] Furthermore, a commutator 36 formed in a substantially cylindrical shape is fixed to the axial front side of the armature shaft 35 and in the vicinity of the armature core 33a. A plurality of commutator segments (not shown) made of brass or the like are provided on the outer periphery of the commutator 36, and ends (not shown) of the coil 34 are electrically connected to these commutator segments. This causes a drive current to be supplied from the commutator 36 to the coil 34, which in turn generates an electromagnetic force in the armature 33. This causes the armature shaft 35 to rotate in a predetermined direction at a predetermined rotation speed.

[0021] 3, a brush holder 37 made of a resin material (insulator) such as plastic is attached to the longitudinal front side (opening side) of the yoke 31. A pair of brushes (not shown) are arranged at 90 degree intervals around the commutator 36 and are provided on the brush holder 37 so as to be movable in the radial direction of the commutator 36. Each brush is in sliding contact with the commutator 36, thereby supplying a drive current from the brush to the commutator 36.

[0022] 1, a connector member CN formed in a substantially box shape is provided on the side (left side in FIG. 1) of the brush holder holding portion 53 forming the gear case 51. An external connector (not shown) provided on the vehicle side can be electrically connected to the connector member CN.

[0023] In this way, by disposing the connector member CN to the side (left side) of the brush holder holding portion 53, an increase in the thickness dimension of the motor device 10 is suppressed. This also makes it possible to easily install the motor device 10 in a narrow space inside a door. Here, in Fig. 1, the connector member CN is shown by an imaginary line (two-dot chain line), and in the other drawings (Figs. 2, 3, 5, and 6), the connector member CN is omitted from illustration.

[0024] [Pinion gear] 3 and 4, the axial rear side (right side in FIG. 3) of the pinion gear 38 is fixed to the axial front side (left side in FIG. 3) of the armature shaft 35. This causes the pinion gear 38 to rotate by the armature shaft 35. The pinion gear 38 is made of steel and has a generally rod-like shape, with a main shaft portion 38a provided at its rotation center. In addition, helical teeth 38b are integrally provided on the outer periphery of the main shaft portion 38a, and the helical teeth 38b extend helically in the axial direction of the armature shaft 35.

[0025] The helical teeth 38b correspond to the first teeth portion in the present invention, and the pinion gear 38 corresponds to the first gear in the present invention.

[0026] Specifically, the helical tooth 38b has a generally crescent-shaped cross section in a direction perpendicular to the axial direction of the main body shaft portion 38a, and only one helical tooth 38b is provided integrally with the main body shaft portion 38a. In other words, the number of teeth of the pinion gear 38 is "1." The helical tooth 38b enters an engagement recess 62d (see FIG. 4) that forms the arc-shaped tooth 62c of the face gear 60, so that the pinion gear 38 and the face gear 60 are engaged with each other so as to be able to transmit power.

[0027] Here, the number of teeth of the arc-shaped teeth 62c of the face gear 60, i.e., the number of meshing recesses 62d of the face gear 60, is set to "48" in this embodiment. In this way, by setting the number of teeth of the pinion gear 38 to "1", the gear transmission efficiency [%] is increased and a large reduction ratio of "1:48" is obtained. Specifically, when the pinion gear 38 rotates 48 times, the face gear 60 finally rotates once. This realizes a reduction in size and power consumption of the motor device 10. However, the number of meshing recesses 62d of the face gear 60 is not limited to "48" and can be set arbitrarily according to the required reduction ratio.

[0028] In this way, the pinion gear 38 and the face gear 60 form the reduction mechanism SD of the motor device 10. The reduction mechanism SD reduces the rotation of the armature shaft 35 to a predetermined speed to increase the torque, and outputs this increased torque to an external driven object (window regulator) from the output shaft 61a (see FIG. 2). This makes it possible to easily raise and lower the window glass (not shown), which is relatively heavy.

[0029] In addition, in the motor device 10 of this embodiment, a structure is adopted in which the armature shaft 35 and the pinion gear 38 are separate bodies and connected to each other so that power can be transmitted between them, but the armature shaft 35 and the pinion gear 38 may also be formed integrally from a single round steel bar.

[0030] [Gear section] 3 and 5, the gear unit 50 includes a gear case 51 to which the yoke 31 of the motor unit 30 is connected. The gear case 51 is made of a resin material such as plastic, and includes a reduction mechanism accommodating section 52 formed in a substantially dish shape, and a brush holder holding section 53 formed in a substantially box shape.

[0031] The reduction mechanism accommodating portion 52 includes a bottom wall portion 52a formed in a substantially disk shape, and a cylindrical side wall portion 52b that is integrally provided on the outer periphery of the bottom wall portion 52a and extends in the axial direction (up and down direction) of the output shaft 61a. The reduction mechanism accommodating portion 52, which is made up of the bottom wall portion 52a and the side wall portion 52b, rotatably accommodates the pinion gear 38 and the face gear 60 that form the reduction mechanism SD.

[0032] The side wall portion 52b forming the gear case 51 surrounds the radial outside of the face gear 60 and corresponds to the cylindrical wall portion of the present invention.

[0033] An insertion hole 52c is provided in the center of the bottom wall portion 52a, through which the output shaft 61a, which is integrally provided at the rotation center of the face gear 60, is inserted. The insertion hole 52c supports the annular surface portion 61b of the output shaft 61a rotatably without rattle.

[0034] In addition, an annular step portion 52d is integrally provided on the outer periphery of the bottom wall portion 52a and is disposed one step above the bottom wall portion 52a. That is, the bottom wall portion 52a is disposed below the annular step portion 52d. As a result, a recess 52e recessed downward is formed on the radially inner side of the annular step portion 52d.

[0035] The second surface portion 62b of the face gear 60 is in sliding contact with the annular step portion 52d. In other words, the annular step portion 52d has a function of supporting the face gear 60 from its axially lower side. Grease (not shown) is applied as a lubricant between the annular step portion 52d and the second surface portion 62b of the face gear 60. Therefore, the face gear 60 can rotate smoothly relative to the annular step portion 52d.

[0036] Here, the main body disk portion 61 of the face gear 60 fits into the recess 52e. However, the axial lower side of the main body disk portion 61 is not in contact with the bottom wall portion 52a. In other words, the face gear 60 comes into sliding contact with the gear case 51 at two locations, the annular surface portion 61b and the second surface portion 62b. This prevents an increase in sliding resistance, allowing the face gear 60 to rotate smoothly relative to the gear case 51.

[0037] Further, an annular recess 52f is provided on the radially inner side of the side wall portion 52b. The annular recess 52f is recessed on the radially outer side of the side wall portion 52b and is disposed around the entire circumference of the side wall portion 52b. Approximately the radially outer half of a C-shaped retaining ring 54 for a hole is fitted and attached in the annular recess 52f.

[0038] The annular recess 52f corresponds to the mounting recess in this invention.

[0039] 5, the C-shaped retaining ring 54 is made of metal, has a part cut out in the circumferential direction to form a substantially C-shape, and is elastically deformable inward in the radial direction. Specifically, by using a tool such as pliers (not shown), a first end 54a and a second end 54b arranged at the circumferential ends of the C-shaped retaining ring 54 can be elastically deformed so as to approach each other. This allows the C-shaped retaining ring 54 to be attached to the annular recess 52f.

[0040] The first surface portion 62a of the face gear 60 is in sliding contact with approximately half of the radially inner side of the C-shaped retaining ring 54. In other words, the C-shaped retaining ring 54 has a function of supporting the face gear 60 from its axially upper side. Grease (not shown) is applied between the C-shaped retaining ring 54 and the first surface portion 62a of the face gear 60 as a lubricant. Therefore, the face gear 60 can rotate smoothly relative to the C-shaped retaining ring 54.

[0041] The C-shaped retaining ring 54 is provided radially inside the side wall portion 52b to prevent the face gear 60 from moving in the axial direction of the output shaft 61a, and corresponds to the movement restricting portion in the present invention.

[0042] In this manner, the face gear 60 rotatably accommodated inside the reduction mechanism accommodation portion 52 is provided so as to be sandwiched between the annular step portion 52d and the C-shaped retaining ring 54 in the vertical direction of the gear case 51. In other words, the face gear 60 is disposed between the bottom wall portion 52a and the C-shaped retaining ring 54 in the axial direction of the face gear 60. Therefore, the face gear 60 does not rattle in the vertical direction of the gear case 51 (the axial direction of the output shaft 61a).

[0043] In particular, an edge portion 62e located radially outside the arc-shaped teeth 62c of the face gear 60 and in the vicinity of the arc-shaped teeth 62c is provided so as to be sandwiched between the annular step portion 52d and the C-shaped retaining ring 54. This effectively prevents the arc-shaped teeth 62c of the face gear 60 from being distorted or bent. This allows the meshing state between the pinion gear 38 and the face gear 60 to be properly maintained.

[0044] Furthermore, in the circumferential direction of the side wall portion 52b, at a location where the brush holder holding portion 53 is provided, a through hole 55 that penetrates in the front-rear direction of the gear case 51 is provided. As shown in Fig. 3, the pinion gear 38 is rotatably inserted into the through hole 55, and the second radial bearing B2 is attached to the axial rear side of the through hole 55. That is, the through hole 55 communicates between the interior of the reduction mechanism accommodating portion 52 and the interior of the brush holder holding portion 53 in the front-rear direction of the gear case 51.

[0045] 5, the through hole 55 overlaps with the annular recess 52f. This prevents the thickness of the reduction mechanism accommodating portion 52 from increasing in the vertical direction. On the other hand, the pinion gear 38 crosses the annular recess 52f, so it is necessary to avoid the C-shaped retaining ring 54. Therefore, when the C-shaped retaining ring 54 is attached to the annular recess 52f, the opening of the C-shaped retaining ring 54, i.e., the space between the first end 54a and the second end 54b of the C-shaped retaining ring 54 in the circumferential direction, is aligned with the through hole 55.

[0046] Furthermore, a total of three mounting parts 56 are integrally provided on the radially outer side of the side wall part 52b. Specifically, the mounting parts 56 are provided so as to protrude radially outward from the side wall part 52b, and are arranged at approximately equal intervals (approximately 120 degree intervals) in the circumferential direction of the side wall part 52b. The mounting parts 56 are formed in a substantially cylindrical shape, and a metallic collar 56a is attached to its radially inner side. The collar 56a has the function of reinforcing the resin mounting parts 56.

[0047] A fixing bolt (not shown) for fixing the motor device 10 to a bracket inside the door is inserted into the collar 56a attached to the mounting portion 56. In this way, the motor device 10 is supported at three points by the bracket inside the door and is firmly fixed to the bracket without any rattling.

[0048] Furthermore, a total of four cover member fixing claws 57 are integrally provided on the radial outside of the side wall portion 52b and between adjacent mounting portions 56 in the circumferential direction of the side wall portion 52b. Specifically, the cover member fixing claws 57 protrude radially outward from the side wall portion 52b, and the engaging claws 58b of the cover member 58 can be hooked onto the cover member fixing claws 57 with a single touch.

[0049] That is, the fixing structure of the cover member 58 to the gear case 51 employs a so-called "snap fit" system. This allows the cover member 58 to be easily fixed to the gear case 51. In order to ensure sufficient fixing strength of the cover member 58 to the gear case 51, the cover member fixing claws 57 are disposed dispersedly in the circumferential direction of the side wall portion 52b.

[0050] 1, 3, 5, and 6, cover member 58 is formed in a substantially circular disk shape from a resin material such as plastic, and closes the opening of reduction mechanism accommodating section 52. A bearing protrusion 58a that rotatably supports the axial front side of pinion gear 38 is provided integrally with cover member 58 on the reduction mechanism accommodating section 52 side, as shown in FIG.

[0051] Specifically, the bearing protrusion 58a protrudes toward the inside of the reduction mechanism accommodating portion 52, and the cross-sectional shape of the bearing protrusion 58a in a direction perpendicular to the axial direction of the pinion gear 38 is a substantially arc shape (not shown in detail). The arc surface of the bearing protrusion 58a rotatably supports the axial front side of the pinion gear 38. Grease (not shown) as a lubricant is also applied between the bearing protrusion 58a and the pinion gear 38. This allows the axial front side of the pinion gear 38 to rotate smoothly without wobbling upward or to the left and right.

[0052] Here, the pinion gear 38 is made of hard steel, and its longitudinal rear side is rotatably supported by the brush holder holding portion 53 of the gear case 51 via the second radial bearing B2. Therefore, when the reduction gear mechanism SD is in operation, a large load is not applied to the cover member 58 (bearing protrusion 58a) from the pinion gear 38. This allows the cover member 58 to be made thin (low rigidity), which in turn makes it possible to reduce the weight of the motor device 10.

[0053] In this way, both axial ends of the pinion gear 38 are rotatably supported by the brush holder holding portion 53 of the gear case 51 and the bearing protrusions 58a of the cover member 58. Therefore, the pinion gear 38 can rotate stably without wobbling.

[0054] A reduction gear mechanism SD consisting of the pinion gear 38 and the face gear 60 is housed inside the gear case 51 and the cover member 58, and both the gear case 51 and the cover member 58 correspond to the housing in this invention.

[0055] Furthermore, a total of four engagement claws 58b are integrally provided on the outer periphery of the cover member 58. These engagement claws 58b extend axially downward of the reduction mechanism accommodating portion 52 and are hooked onto the total of four cover member fixing claws 57 provided on the side wall portion 52b. That is, the total of four engagement claws 58b are disposed at positions corresponding to the cover member fixing claws 57 in the circumferential direction of the side wall portion 52b (cover member 58).

[0056] [Face gear] 3 to 5, a face gear 60 made of a resin material such as plastic is rotatably housed in the reduction mechanism housing 52. The face gear 60 is formed in a substantially circular plate shape and includes a main disk portion 61. An output shaft 61a is integrally provided at the center of the main disk portion 61 and on the axially lower side. That is, the output shaft 61a is rotated by the face gear 60.

[0057] The output shaft 61a extends in the vertical direction, and a portion of the output shaft 61a near the base end (upper in the figure) is provided with an annular surface portion 61b made of a smooth surface without any unevenness. The annular surface portion 61b is adapted to slide against the insertion hole 52c of the reduction mechanism accommodating portion 52. The output shaft 61a is provided in the gear portion 50, and is rotatable about an axis C2 perpendicular to the axis C1 of the armature shaft 35.

[0058] In addition, a serration portion 61c is provided on the output shaft 61a at a location other than the annular surface portion 61b in the axial direction thereof to be fixed to the driven object. The serration portion 61c has a plurality of projections and recesses in the circumferential direction thereof, and is thereby fixed to the driven object so as not to rotate relative thereto. Thus, the driven object is rotationally driven by the output shaft 61a.

[0059] Further, an annular gear forming portion 62 is integrally provided on the outer periphery of the main body disc portion 61 and is disposed one step higher than the main body disc portion 61. That is, the main body disc portion 61 is disposed lower than the gear forming portion 62. As a result, the main body disc portion 61 fits into the recess 52e of the reduction mechanism accommodating portion 52, as shown in FIG.

[0060] The gear forming portion 62 is an annular flat plate having a first surface portion 62a on its axially upper side and a second surface portion 62b on its axially lower side. That is, the first surface portion 62a faces the cover member 58, and the second surface portion 62b faces the annular step portion 52d of the reduction mechanism accommodating portion 52.

[0061] A plurality of arc-shaped teeth 62c are provided on the first surface 62a of the gear forming portion 62 so as to be aligned in the circumferential direction of the gear forming portion 62. The number of teeth of the arc-shaped teeth 62c is "48". Each of the arc-shaped teeth 62c has a plurality of meshing recesses 62d recessed in a substantially semicircular shape on the axial lower side of the face gear 60, and the number of the meshing recesses 62d is also "48". Note that the face gear 60 also forms a reduction mechanism SD like the pinion gear 38, and as shown in FIG. 4, the meshing recesses 62d are meshed with the helical teeth 38b of the pinion gear 38.

[0062] That is, the meshing recess 62d meshes with the helical teeth 38b from the axial direction of the output shaft 61a and corresponds to the second teeth portion in the present invention. Also, the face gear 60 having the meshing recess 62d corresponds to the second gear in the present invention.

[0063] In addition, an edge portion 62e is integrally provided on the outer periphery of the gear forming portion 62. The first surface portion 62a side of the edge portion 62e has no arc-shaped teeth 62c formed thereon, and is a smooth surface. Furthermore, the second surface portion 62b side of the edge portion 62e has no formed thereon, and is a smooth surface. The first surface portion 62a of the edge portion 62e is adapted to come into sliding contact with the axially lower side of the C-shaped retaining ring 54 as the face gear 60 rotates. In contrast, the second surface portion 62b of the edge portion 62e is adapted to come into sliding contact with the axially upper side of the annular step portion 52d as the face gear 60 rotates.

[0064] Here, when the motor device 10 is in operation, a thrust force of a predetermined magnitude is applied to the face gear 60 as shown by the arrows F1 and F2 in FIG. 3. Specifically, the thrust forces F1 and F2 are applied when a rotational force is applied to the face gear 60 from the pinion gear 38, or when a reaction force (weight of the window glass, etc.) is applied to the face gear 60 via the output shaft 61a. In this embodiment, as described above, the edge portion 62e of the face gear 60 is in sliding contact with both the C-shaped retaining ring 54 and the annular step portion 52d, and does not move in the thrust direction. In other words, the face gear 60 is sandwiched between both the metallic C-shaped retaining ring 54 and the highly rigid annular step portion 52d, and does not rattle in the thrust direction.

[0065] As shown in Fig. 3, the motor device 10 employs a reduction gear mechanism SD consisting of a pinion gear 38 and a face gear 60, so that the axis C1 of the armature shaft 35 and the axis C2 of the output shaft 61a can be perpendicular to each other. This allows the motor device 10 to have a substantially symmetrical shape when viewed from the axial direction of the output shaft 61a. In this way, the motor device 10 has a substantially line-symmetrical shape (symmetrical shape) with respect to the axis C1, and can be installed in the same posture in the driver's door and the passenger's door. In other words, the motor device 10 can be used commonly on the left and right sides.

[0066] [Assembly Instructions] Next, an example of an assembly procedure for the motor device 10 formed as above will be described in detail with reference to the drawings.

[0067] First, the gear unit 50 is assembled as shown in Fig. 5. Specifically, the gear case 51, the face gear 60, the C-shaped retaining ring 54, and the cover member 58, which are manufactured through separate manufacturing processes, are prepared.

[0068] Next, as shown by the arrow M1, the face gear 60 is assembled inside the reduction mechanism accommodating portion 52 of the gear case 51. At this time, the output shaft 61a of the face gear 60 is inserted into the insertion hole 52c of the bottom wall portion 52a. As a result, the second surface portion 62b of the edge portion 62e of the face gear 60 is placed on the upper side of the annular stepped portion 52d of the gear case 51. As a result, assembly of the face gear 60 into the reduction mechanism accommodating portion 52 is completed.

[0069] Thereafter, as shown by the arrow M2, the C-shaped retaining ring 54 is attached to the annular recess 52f inside the reduction mechanism accommodating portion 52. At this time, the C-shaped retaining ring 54 is elastically deformed using a tool such as pliers so that the first end 54a and the second end 54b approach each other. In addition, the through hole 55 provided in the side wall portion 52b is positioned between the first end 54a and the second end 54b in the circumferential direction of the C-shaped retaining ring 54. This completes the assembly of the C-shaped retaining ring 54 to the reduction mechanism accommodating portion 52.

[0070] Furthermore, as shown by arrow M3, cover member 58 is attached to reduction mechanism accommodating portion 52 to close the axially upper opening of reduction mechanism accommodating portion 52. At this time, a total of four engagement claws 58b provided on cover member 58 are hooked onto a total of four cover member fixing claws 57 provided on side wall portion 52b. As a result, cover member 58 is attached to reduction mechanism accommodating portion 52, and assembly of gear portion 50 is completed.

[0071] Next, as shown in FIG. 6, the motor section 30 assembled through another assembly process and a total of three fixing screws S1 are prepared.

[0072] Then, as indicated by arrow M4, the axial front side of the pinion gear 38 is brought into contact with the brush holder holding portion 53 of the gear case 51. Then, the pinion gear 38 is inserted into the through hole 55 (see FIG. 3), and the second radial bearing B2 is attached to the brush holder holding portion 53. As a result, the brush holder 37 is housed in the brush holder holding portion 53, and the yoke 31 is abutted against the gear case 51.

[0073] Here, the helical tooth 38b (one tooth) of the pinion gear 38 meshes with the meshing recess 62d (48 teeth) of the face gear 60, and the face gear 60 rotates as the pinion gear 38 is inserted into the through hole 55. At this time, the pinion gear 38 and the face gear 60 have an increased gear transmission efficiency [%], so the face gear 60 rotates smoothly. Therefore, the motor unit 30 can be easily assembled to the gear unit 50 without increasing the insertion load of the pinion gear 38 into the through hole 55.

[0074] Thereafter, as indicated by arrow M5, a total of three fixing screws S1 are screwed into the brush holder holding portion 53 using a tool such as a screwdriver (not shown) to fix the motor portion 30 to the gear portion 50. This fixes the motor portion 30 to the gear portion 50, thereby completing the assembly work of the motor device 10.

[0075] As described above in detail, the motor device 10 of embodiment 1 includes a reduction mechanism accommodating section 52 that accommodates the pinion gear 38 and the face gear 60, and the reduction mechanism accommodating section 52 has a side wall portion 52b that surrounds the radial outside of the face gear 60, and a C-shaped retaining ring 54 is provided on the radial inside of the side wall portion 52b to prevent the face gear 60 from moving in the axial direction of the output shaft 61a.

[0076] As a result, the face gear 60 can be supported in the axial direction by the C-shaped retaining ring 54 inside the reduction mechanism accommodating portion 52. This prevents the face gear 60 from wobbling in the axial direction, and suppresses changes in the meshing state between the pinion gear 38 and the face gear 60 from varying from product to product. This makes it possible to obtain stable output characteristics for each product.

[0077] According to the motor device 10 of the first embodiment, the metal C-shaped retaining ring 54 is attached to the annular recess 52f provided in the side wall portion 52b. Therefore, a general-purpose, inexpensive C-shaped retaining ring 54 can be used, and therefore manufacturing costs do not increase. Furthermore, the C-shaped retaining ring 54 can be easily attached to the annular recess 52f using a tool such as pliers, and therefore ease of assembly is not reduced.

[0078] Furthermore, according to the motor device 10 of the first embodiment, the reduction mechanism accommodating portion 52 includes the bottom wall portion 52a, and the face gear 60 is disposed between the annular step portion 52d forming the bottom wall portion 52a and the C-shaped retaining ring 54 in the axial direction of the face gear 60. This makes it possible to more reliably prevent the face gear 60 from rattling in the thrust direction.

[0079] Furthermore, according to motor device 10 of embodiment 1, gear case 51 and cover member 58 rotatably support both axial sides of pinion gear 38. Therefore, pinion gear 38 can rotate stably without wobbling, which also stabilizes the meshing state between pinion gear 38 and face gear 60.

[0080] Furthermore, according to the motor device 10 of the first embodiment, stable output characteristics can be obtained for each product, thereby suppressing the occurrence of defective products and eliminating the need for reassembly, etc. This makes it possible to save energy required for the manufacture of the motor device 10, and in particular to achieve Goal 7 (ensure access to affordable, reliable, sustainable and modern energy for all) and Goal 13 (take urgent action to combat climate change and its impacts) in the Sustainable Development Goals (SDGs) established by the United Nations.

[0081] [Embodiment 2] Next, a second embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the first embodiment are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0082] Figure 7 is an oblique view of the motor device of embodiment 2 seen from the cover member side, Figure 8 is an oblique view of the motor device of Figure 7 seen from the bottom wall side of the gear case, Figure 9 is a cross-sectional view along the axial direction of the armature shaft of the motor device of Figure 7, Figure 10 is an oblique view showing the reduction mechanism of the motor device of Figure 7, and Figure 11 is an oblique view showing the assembly procedure of the motor device of Figure 7.

[0083] 7 to 10, motor device 70 of embodiment 2 differs from motor device 10 of embodiment 1 only in the structure of gear portion 80. The structure of gear portion 80 will be described in detail below with reference to the drawings.

[0084] [Gear section] 9 and 11, the gear unit 80 includes a gear case 81 to which the yoke 31 of the motor unit 30 is connected. The gear case 81 is made of a resin material such as plastic, and includes a reduction mechanism housing section 82 formed in a substantially dish shape. The reduction mechanism housing section 82 rotatably houses a reduction mechanism SD consisting of the pinion gear 38 and a face gear 90.

[0085] A cylindrical center pole 82a is provided integrally with the center of the bottom wall 52a. The axial upper side (tip side) of the center pole 82a extends beyond the side wall 52b to the outside of the reduction gear accommodating section 82 in the axial direction of the reduction gear accommodating section 82. The center pole 82a is inserted into a hollow output shaft 91a provided integrally with the rotation center of the face gear 90.

[0086] In addition, a substantially annular seat 82b is integrally provided at the center of the bottom wall 52a and on the axially lower side (base end side) of the center pole 82a. The seat 82b protrudes from the bottom wall 52a axially upward at a predetermined height. In other words, the bottom wall 52a is disposed below the seat 82b. As a result, a recess 52e recessed downward is formed on the radially outer side of the seat 82b.

[0087] The first surface 62a of the face gear 90 is in sliding contact with the upper surface of the base portion 82b. In other words, the base portion 82b has a function of supporting the face gear 90 from its axially lower side. Grease (not shown) is applied between the base portion 82b and the first surface 62a of the face gear 90 as a lubricant. Therefore, the face gear 90 can rotate smoothly with respect to the base portion 82b.

[0088] Here, the gear forming portion 62 of the face gear 90 and the pinion gear 38 are disposed inside the recess 52e. A bearing mounting hole 82c is provided at a location of the base portion 82b facing the through hole 55 in the circumferential direction. A third radial bearing B3 is mounted in the bearing mounting hole 82c, and the third radial bearing B3 rotatably supports the axial front side of the pinion gear 38.

[0089] In this way, both axial ends of the pinion gear 38 are rotatably supported by the gear case 81 via the second and third radial bearings B2, B3. Therefore, the pinion gear 38 can rotate stably without wobbling.

[0090] 9, in the second embodiment, the annular recess 52f in which the C-shaped retaining ring 54 is attached does not overlap with the through hole 55. In other words, the annular recess 52f and the through hole 55 are arranged offset from each other in the axial direction of the reduction mechanism accommodating portion 82. Therefore, when attaching the C-shaped retaining ring 54 to the annular recess 52f, there is no need to take the through hole 55 into consideration. Specifically, the annular recess 52f is arranged axially higher on the side wall portion 52b than in the first embodiment (see FIG. 3).

[0091] The second surface 62b of the face gear 90 is in sliding contact with the C-shaped retaining ring 54, and grease (not shown) is applied as a lubricant between the C-shaped retaining ring 54 and the second surface 62b of the face gear 90. Therefore, the face gear 90 can rotate smoothly relative to the C-shaped retaining ring 54.

[0092] In this manner, the face gear 90 rotatably accommodated inside the reduction gear accommodating portion 82 is provided so as to be sandwiched between the base portion 82b and the C-shaped retaining ring 54 in the vertical direction of the gear case 81. In other words, the face gear 90 is disposed between the bottom wall portion 52a and the C-shaped retaining ring 54 in the axial direction of the face gear 90. Therefore, the face gear 90 does not rattle in the vertical direction of the gear case 81 (the axial direction of the output shaft 91a).

[0093] 7, 9, and 11, the cover member 88 is formed in a substantially circular plate shape from a resin material such as plastic, and closes the opening of the reduction mechanism accommodating portion 82. An output shaft insertion hole 88a is provided in the center of the cover member 88, and an output shaft 91a is inserted into the output shaft insertion hole 88a in a non-contact state. Also, as shown in FIG. 9, the main body circular plate portion 61 of the face gear 90 and the cover member 88 are in a non-contact state with each other.

[0094] In this way, the face gear 90 comes into sliding contact with the gear case 81 at two locations, the center pole 82a and the first surface portion 62a. This prevents an increase in sliding resistance, allowing the face gear 90 to rotate smoothly with respect to the gear case 81. Here, the cover member 88 does not support the pinion gear 38 like the cover member 58 (see FIG. 3) of the first embodiment, and therefore can be made even thinner than the first embodiment.

[0095] A reduction gear mechanism SD consisting of the pinion gear 38 and the face gear 90 is housed inside the gear case 81 and the cover member 88, and both the gear case 81 and the cover member 88 correspond to the housing in this invention.

[0096] [Face gear] 9 to 11, a face gear 90 made of a resin material such as plastic is rotatably housed in the reduction mechanism housing 82. A hollow output shaft 91a is integrally provided in the center of the main body disc portion 61 forming the face gear 90 so as to protrude axially upward. In other words, the output shaft 91a is rotated by the face gear 90. The output shaft 91a is provided in the gear portion 80 and is rotatable about an axis C2 perpendicular to the axis C1 of the armature shaft 35.

[0097] The gear forming portion 62 is disposed one step lower than the main disk portion 61, and a first surface portion 62a on the axially lower side of the gear forming portion 62 faces the bottom wall portion 52a. A second surface portion 62b on the axially upper side of the gear forming portion 62 faces the cover member 88. A plurality of arc-shaped teeth 62c (meshing recesses 62d) are provided on the first surface portion 62a of the gear forming portion 62.

[0098] Here, in the face gear 90 of the second embodiment, compared to the face gear 60 of the first embodiment, the edge portion 62e (see FIG. 4) is not provided. Also, the output shaft 91a is hollow. Therefore, the face gear 90 of the second embodiment is made smaller and lighter than the face gear 60 of the first embodiment.

[0099] The face gear 90 having the meshing recess 62d corresponds to the second gear in the present invention.

[0100] Here, when the motor device 70 is in operation, a thrust force of a predetermined magnitude is applied to the face gear 90 as shown by arrows F1 and F2 in Fig. 9. Specifically, thrust forces F1 and F2 are applied when a rotational force is applied to the face gear 90 from the pinion gear 38, or when a reaction force (weight of the window glass, etc.) is applied to the face gear 90 via the output shaft 91a. As described above, the face gear 90 is in sliding contact with both the base portion 82b and the C-shaped retaining ring 54, and does not move in the thrust direction. In other words, the face gear 90 is sandwiched between both the highly rigid base portion 82b and the metallic C-shaped retaining ring 54, and does not rattle in the thrust direction.

[0101] [Assembly Instructions] Next, an example of an assembly procedure for the motor device 70 formed as above will be described in detail with reference to the drawings.

[0102] 11, the gear case 81, the face gear 90, the C-shaped retaining ring 54, and the cover member 88 are prepared through separate manufacturing processes, and the motor unit 30 is assembled through a separate assembly process. Then, as shown by the arrow M6, the motor unit 30 is fixed to the gear case 81 using a total of three fixing screws S1.

[0103] Next, as shown by arrow M7, the face gear 90 is assembled into the reduction mechanism accommodating portion 82 of the gear case 81. At this time, the center pole 82a is inserted into the hollow output shaft 91a, and the meshing recess 62d of the face gear 90 is meshed with the helical teeth 38b of the pinion gear 38. This completes the assembly of the face gear 90 into the reduction mechanism accommodating portion 82.

[0104] Thereafter, as shown by arrow M8, the C-shaped retaining ring 54 is attached to the annular recess 52f inside the reduction mechanism accommodating portion 82. As a result, the face gear 90 is pressed by the C-shaped retaining ring 54, and the assembly of the C-shaped retaining ring 54 to the reduction mechanism accommodating portion 82 is completed.

[0105] As shown by arrow M9, the cover member 88 is attached to the reduction mechanism accommodating portion 82 to close the axially upper opening of the reduction mechanism accommodating portion 82. At this time, the output shaft 91a is inserted into the output shaft insertion hole 88a of the cover member 88, and each of the engagement claws 58b is hooked onto each of the cover member fixing claws 57. In the second embodiment, six each of the engagement claws 58b and the cover member fixing claws 57 are provided.

[0106] As a result, the cover member 88 is attached to the reduction mechanism accommodating portion 82, and the assembly of the gear portion 80 is completed, and thus the assembly of the motor device 70 is completed.

[0107] The motor device 70 of the second embodiment formed as described above can also achieve the same effects as those of the first embodiment. In addition, in the motor device 70 of the second embodiment, both axial ends of the pinion gear 38 are supported by the second and third radial bearings B2 and B3, so that a support structure for the pinion gear 38 with higher rigidity can be realized. Also, the face gear 90 of the second embodiment does not include the edge portion 62e (see FIG. 4), and the output shaft 91a is hollow. Therefore, the face gear 90 can be made smaller and lighter.

[0108] [Embodiment 3] Next, a third embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the second embodiment described above are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0109] FIG. 12 is a perspective view of the face gear of the third embodiment as viewed from the meshing recess side, and FIG. 13 is a perspective view of the face gear of the third embodiment as viewed from the output shaft side.

[0110] 12 and 13, the third embodiment is different from the second embodiment in only the shape of the face gear 100. Specifically, the face gear 100 of the third embodiment is provided with a reinforcing portion 101 having a honeycomb structure on the second surface portion 62b of the face gear 100.

[0111] The face gear 100 corresponds to the second gear in the present invention.

[0112] Specifically, the reinforcing portion 101 is provided so as to surround the periphery of the main body disk portion 61. The protruding height of the reinforcing portion 101 in the axial direction of the face gear 100 is the same as the protruding height of the main body disk portion 61 in the axial direction of the face gear 100. In other words, in the axial direction of the face gear 100, the reinforcing portion 101 and the main body disk portion 61 are flush with each other.

[0113] 13, the reinforcing portion 101 is formed by arranging a plurality of regular hexagonal tubular portions 102 in the circumferential direction of the face gear 100. In other words, the reinforcing portion 101 has a "honeycomb structure." The reinforcing portion 101 is provided on the second surface portion 62b opposite to the first surface portion 62a on which the arc-shaped teeth 62c (meshing recesses 62d) are provided. The reinforcing portion 101 is provided over the entire circumferential area of ​​the face gear 100.

[0114] As a result, when the face gear 100 is viewed in the axial direction, the reinforcing portion 101 and the arc-shaped tooth 62c (meshing recess 62d) overlap each other. Therefore, the gear forming portion 62 in which the arc-shaped tooth 62c (meshing recess 62d) is formed is reinforced, and distortion of the arc-shaped tooth 62c (meshing recess 62d) is suppressed. The reinforcing portion 101 abuts against the C-shaped retaining ring 54 (see FIGS. 9 and 11) in the axial direction of the face gear 100. That is, the reinforcing portion 101 is in sliding contact with the C-shaped retaining ring 54.

[0115] The third embodiment formed as described above can also achieve the same effects as those of the second embodiment. In addition, in the third embodiment, the reinforcing portion 101 can suppress distortion of the arc-shaped tooth 62c (meshing recess 62d). This can further suppress changes in the meshing state of the gears. In addition, the grease (not shown) applied between the reinforcing portion 101 and the C-shaped retaining ring 54 can be stored inside the tubular portion 102. In other words, the reinforcing portion 101 can also function as a "grease reservoir". Furthermore, the reinforcing portion 101 can effectively suppress the generation of sink marks, voids, and the like in the arc-shaped tooth 62c (meshing recess 62d) during injection molding of the face gear 100.

[0116] [Embodiment 4] Next, a fourth embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the first embodiment are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0117] FIG. 14 is a partially enlarged perspective view showing the reduction gear mechanism of embodiment 4, FIG. 15 is a side view of the pinion gear of FIG. 4 and the pinion gear of FIG. 14, and FIG. 16 is a partially enlarged plan view showing the meshing recess of the face gear of FIG. 14.

[0118] As shown in the lower part of FIG. 14 and FIG. 15, in the fourth embodiment, the shape of the pinion gear (first gear) 200 is different from that in the first embodiment.

[0119] The pinion gear 200 has helical teeth (first teeth portion) 201 extending helically in the axial direction of the armature shaft 35 (see FIG. 3). The pinion gear 200 is tapered (see the dashed line in the lower part of FIG. 15) toward the rotation center (lower left side of FIG. 14) of the face gear (second gear) 210. That is, the outer diameter (thickness) of the helical teeth 201 differs between the rear side and the front side of the pinion gear 200 in the axial direction. Specifically, the outer diameter of the helical teeth 201 is larger (thicker) on the rear side of the pinion gear 200 in the axial direction, and is smaller (thinner) on the front side of the pinion gear 200 in the axial direction.

[0120] 16, an interlocking recess (second tooth portion) 220 of the face gear 210 with which the helical teeth 201 mesh is formed in accordance with the shape of the helical teeth 201. That is, a width dimension W1 of the interlocking recess 220 on the radially outer side of the face gear 210 is larger than a width dimension W2 of the interlocking recess 220 on the radially inner side of the face gear 210 (W1>W2).

[0121] In this way, by forming the meshing recess 220 of the face gear 210 following the shape of the helical tooth 201, the thickness dimension T1 of the arc-shaped tooth 230 on the radially outer side of the face gear 210 and the thickness dimension T2 of the arc-shaped tooth 230 on the radially inner side of the face gear 210 can be made to be approximately the same thickness (T1 ≈ T2). As a result, even if the radial dimension R of the face gear 210 is increased, the arc-shaped tooth 230 along the radial direction of the face gear 210 can be made to have a sufficient thickness (thickness), and therefore it becomes possible to ensure sufficient meshing strength of the face gear 210.

[0122] If the pinion gear 38 of embodiment 1 shown in the upper part of FIG. 15 (having the same outer diameter over the entire axial area (see the dashed line in the upper part of FIG. 15)) is used and the radial dimension R of the face gear 210 is increased, the following problem will arise.

[0123] In other words, unless the thickness dimension T2 of the arc-shaped teeth 230 on the radial inside of the face gear 210 is made smaller (thinner) than the thickness dimension T1 of the arc-shaped teeth 230 on the radial outside of the face gear 210, the helical teeth 38b will interfere with the arc-shaped teeth 230 on the radial inside of the face gear 210. As a result, the reduction gear mechanism SD will not operate.

[0124] Incidentally, by making the thickness dimension T2 of the arc-shaped teeth 230 on the radially inner side of the face gear 210 smaller (thinner), the interference between the helical teeth 38b and the arc-shaped teeth 230 can be avoided to some extent, but on the other hand, the strength of the arc-shaped teeth 230 will become insufficient.

[0125] The fourth embodiment formed as above can also achieve the same effects as the first embodiment. In addition, in the fourth embodiment, the pinion gear 200 is formed to have a tapered shape toward the center of rotation of the face gear 210, so that even if the radial dimension R of the face gear 210 is increased, the helical teeth 201 and the meshing recess 220 can be meshed with each other so as to transmit power. This improves the design freedom of the face gear 210, making it possible to meet various needs.

[0126] [Embodiment 5] Next, a fifth embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the second embodiment described above are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0127] FIG. 17 is a cross-sectional view taken along the axial direction of the armature shaft of a motor device according to the fifth embodiment, and FIG. 18 is a perspective view showing a face gear and a ring member of FIG.

[0128] 17 and 18, motor device 300 of embodiment 5 differs from embodiment 2 in that face gear (second gear) 310 has a different shape and uses a ring-shaped member (movement restricting portion) 320 instead of C-shaped retaining ring 54 (see FIG. 9). Also, as shown in FIG. 17, a minute gap ΔS is provided between face gear 310 and ring-shaped member 320 in the axial direction of output shaft 91a.

[0129] The face gear 310 includes a protrusion 311 formed in a substantially circular plate shape. The protrusion 311 is disposed on the second surface 62b side of the gear forming part 62, and protrudes from the second surface 62b toward the output shaft 91a by a predetermined height. That is, the protrusion 311 protrudes toward the side where the ring-shaped member 320 is disposed (the upper side in FIG. 17).

[0130] The protrusion 311 is tapered toward the output shaft 91a. Specifically, the protrusion 311 is formed in a flat, generally truncated cone shape. The outer periphery of the protrusion 311 is provided with an outer periphery surface 312 that is inclined at a predetermined angle with respect to the axis of the output shaft 91a.

[0131] On the other hand, the ring-shaped member 320 is formed in a substantially circular ring shape, and an outer circumferential portion 321 on the radially outer side thereof is fixed without rattle to the annular recess 52f of the gear case 81. Specifically, the outer circumferential portion 321 of the ring-shaped member 320 climbs over a claw portion CP (not shown in detail) partially provided on the cover member 88 side of the annular recess 52f, and is fitted into the annular recess 52f.

[0132] Furthermore, a hole 322 is provided on the radially inner side of the ring-shaped member 320, penetrating the ring-shaped member 320 in the thickness direction. The hole 322 is recessed in a tapered shape so as to taper toward the output shaft 91a. The inner periphery of the hole 322 is provided with an inner periphery surface 323 that is inclined at a predetermined angle with respect to the axis of the output shaft 91a.

[0133] Here, as shown by the arrow M10 in Fig. 18, the outer peripheral surface 312 of the protrusion 311 and the inner peripheral surface 323 of the hole 322 face each other as shown in Fig. 17 by stacking the ring-shaped member 320 on the face gear 310. When the face gear 310 moves in the axial direction of the output shaft 91a and approaches the ring-shaped member 320, the protrusion 311 can be fitted into the hole 322.

[0134] Furthermore, as shown in the portion surrounded by the dashed square in Fig. 17, when a line segment extending in the axial direction of the output shaft 91a is used as the reference line BL, the acute-angle side inclination angle “a degrees” of the outer peripheral surface 312 of the protrusion 311 with respect to the reference line BL is smaller than the acute-angle side inclination angle “b degrees” of the inner peripheral surface 323 of the hole 322 with respect to the reference line BL (a degrees < b degrees). Thereby, as the face gear 310 moves in the axial direction of the output shaft 91a and approaches the ring-shaped member 320, the inner peripheral surface 323 of the hole 322 is abutted against the outer peripheral surface 312 of the protrusion 311 so as to bite into it.

[0135] Here, when the motor device 300 is driven, that is, when the window glass is moved up and down, even if a thrust force acts on the face gear 310 and the face gear 310 approaches the ring-shaped member 320, the protrusion 311 only loosely fits into the hole 322. Therefore, the face gear 310 can easily rotate relative to the ring-shaped member 320 with substantially no resistance. Thus, when the motor device 300 is driven, the face gear 310 does not enter a locked state (a state where a brake is applied) in which it cannot rotate relative to the ring-shaped member 320.

[0136] In contrast, when a large external force is applied to the output shaft 91a, such as when the closed window glass is forcibly pushed down, a large thrust force acts on the face gear 310. This causes the face gear 310 to approach the ring-shaped member 320 more closely so as to eliminate the minute gap δS. As a result, the protrusion 311 fits tightly into the hole 322. Therefore, the inner circumferential surface 323 of the hole 322 is butted against the outer circumferential surface 312 of the protrusion 311 so as to bite into it, and the face gear 310 is unable to rotate relative to the ring-shaped member 320 (locked state). This prevents the window glass from being forcibly pushed down, making it possible to protect the vehicle from theft, vandalism, and the like.

[0137] The fifth embodiment formed as above can also achieve the same advantageous effects as the above-mentioned second embodiment. In addition, the fifth embodiment is provided with the above-mentioned so-called "lock mechanism," so that the reliability of the motor device 300 can be further improved.

[0138] [Embodiment 6] Next, a sixth embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the fifth embodiment described above are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0139] FIG. 19 is a partially enlarged cross-sectional view showing a face gear and a ring member according to a sixth embodiment.

[0140] As shown in FIG. 19, in the sixth embodiment, the shape of a face gear (second gear) 400 and the shape of a ring-shaped member (movement restricting portion) 410 are different from those in the fifth embodiment.

[0141] The protrusion 401 provided on the face gear 400 has an outer diameter dimension larger than that of the protrusion 311 (see FIG. 17) of the fifth embodiment. Specifically, the outer periphery of the protrusion 401 is disposed in the radial direction of the face gear 400 at a location where the gear forming portion 62 is provided.

[0142] As a result, when the output shaft 91a (see FIG. 17) is viewed in the axial direction, the outer circumferential surface 312 of the protrusion 401 overlaps with the helical tooth 38b of the pinion gear 38 and the meshing portion of the meshing recess 62d of the face gear 400. Specifically, the outer circumferential surface 312 of the protrusion 401 is disposed on the meshing center GC between the helical tooth 38b and the meshing recess 62d in the axial direction of the output shaft 91a (the vertical direction in FIG. 19).

[0143] Furthermore, by positioning the outer peripheral surface 312 of the protrusion portion 401 on the meshing center GC, the thickness of the region AR in the radial direction of the face gear 400, i.e., the thickness of the portion between the gear forming portion 62 and the third radial bearing B3 along the radial direction of the face gear 400, is made thicker in both the axial and radial directions of the output shaft 91a.

[0144] Here, since the face gear 400 is formed by injection molding a resin material such as plastic, the thick portion shrinks significantly when hardened, and there is a risk of sink marks, voids, etc. Therefore, a plurality of recessed portions 402 are provided in the thick region AR. This suppresses distortion of the face gear 400 including the gear forming portion 62, and improves the molding accuracy of the face gear 400.

[0145] Moreover, the hole 411 provided on the radially inner side of the ring-shaped member 410 has an inner diameter dimension larger than that of the hole 322 (see FIG. 17) of the fifth embodiment. Specifically, as shown in FIG. 19, the hole 411 of the ring-shaped member 410 is disposed at a position where the gear forming portion 62 is provided in the radial direction of the face gear 400.

[0146] As a result, when the output shaft 91a (see FIG. 17) is viewed in the axial direction, the inner circumferential surface 323 of the hole 411 overlaps with the helical tooth 38b of the pinion gear 38 and the meshing portion of the meshing recess 62d of the face gear 400. Specifically, the inner circumferential surface 323 of the hole 411 is disposed on the meshing center GC between the helical tooth 38b and the meshing recess 62d in the axial direction of the output shaft 91a (the vertical direction in FIG. 19).

[0147] The sixth embodiment formed as described above can also achieve the same effects as the fifth embodiment. In addition, in the sixth embodiment, the outer peripheral surface 312 of the protrusion 401 and the inner peripheral surface 323 of the hole 411 are disposed on the meshing center GC. That is, the locking mechanism (the outer peripheral surface 312 and the inner peripheral surface 323) is disposed at the portion of the face gear 400 that is most susceptible to deformation (the portion to which the thrust force is applied). This makes it possible to operate the locking mechanism reliably and accurately, and further improves reliability. In addition, since the surface areas of the outer peripheral surface 312 and the inner peripheral surface 323 can be increased compared to the fifth embodiment, it is possible to increase the locking force (braking force) of the locking mechanism.

[0148] [Embodiment 7] Next, a seventh embodiment of the present invention will be described in detail with reference to the drawings. Note that parts having the same functions as those in the first embodiment are given the same reference numerals, and detailed descriptions thereof will be omitted.

[0149] FIG. 20 is a partially enlarged cross-sectional view showing a face gear and a gear case according to the seventh embodiment.

[0150] 20, in motor device 500 of embodiment 7, the shape of face gear (second gear) 510 is different from that of embodiment 1, and the shape of bottom wall portion 52a of gear case 51 is also different. Also, in the axial direction of output shaft 61a, a minute gap ΔS is provided between face gear 510 and annular step portion 52d (gear case 51).

[0151] The face gear 510 has a protruding portion 511 formed in a substantially circular plate shape. The protruding portion 511 is disposed on the second surface portion 62b side of the gear forming portion 62, and protrudes from the second surface portion 62b toward the output shaft 61a by a predetermined height. That is, the protruding portion 511 protrudes toward the side where the bottom wall portion 52a is disposed (the lower side in FIG. 20).

[0152] The protruding portion 511 is tapered toward the output shaft 61a. Specifically, the protruding portion 511 is formed in a flat, generally truncated cone shape. The outer periphery of the protruding portion 511 is provided with an outer periphery surface 512 that is inclined at a predetermined angle with respect to the axis of the output shaft 61a.

[0153] Here, when the output shaft 61a is viewed in the axial direction, the outer circumferential surface 512 of the protrusion 511 overlaps with the helical tooth 38b of the pinion gear 38 and the meshing portion of the meshing recess 62d of the face gear 510. Specifically, the outer circumferential surface 512 of the protrusion 511 is disposed on the meshing center GC between the helical tooth 38b and the meshing recess 62d in the axial direction of the output shaft 61a (the vertical direction in FIG. 20).

[0154] In addition, in the axial direction of the output shaft 61a, the outer peripheral surface 512 of the protrusion 511 is arranged to overlap the helical teeth 38b of the pinion gear 38 and the meshing portion of the meshing recess 62d of the face gear 510, so that the thickness of the region AR in the radial direction of the face gear 510 (near the meshing recess 62d) is thickened in both the axial and radial directions of the output shaft 61a. Therefore, similar to the sixth embodiment (see FIG. 19), a plurality of reduced thickness portions 513 are provided in the portion. Thus, distortion of the face gear 510 including the gear forming portion 62 is suppressed, and the forming accuracy of the face gear 510 is improved.

[0155] Meanwhile, the bottom wall portion 52a forms a recess 514 one step below the annular step portion 52d. The recess 514 is recessed in a tapered shape so as to taper toward the output shaft 61a. The inner periphery of the recess 514 is provided with an inner periphery surface 515 that is inclined at a predetermined angle with respect to the axis of the output shaft 61a.

[0156] 20, the outer circumferential surface 512 of the protruding portion 511 and the inner circumferential surface 515 of the recessed portion 514 are opposed to each other by accommodating (attaching) the face gear 510 in the gear case 51. When the face gear 510 moves in the axial direction of the output shaft 61a and approaches the bottom wall portion 52a, the protruding portion 511 can be fitted into the recessed portion 514.

[0157] As a result, when the output shaft 61a is viewed in the axial direction, the inner circumferential surface 515 of the recess 514 overlaps with the meshing portion of the helical tooth 38b of the pinion gear 38 and the meshing recess 62d of the face gear 510. Specifically, the inner circumferential surface 515 of the recess 514 is disposed on the meshing center GC between the helical tooth 38b and the meshing recess 62d in the axial direction of the output shaft 61a (the vertical direction in FIG. 20).

[0158] 20, when a line segment extending in the axial direction of the output shaft 61a is taken as a reference line BL, an inclination angle "c degrees" of the outer peripheral surface 512 of the convex portion 511 on the acute angle side with respect to the reference line BL is larger than an inclination angle "d degrees" of the inner peripheral surface 515 of the recessed portion 514 on the acute angle side with respect to the reference line BL (c degrees > d degrees). As a result, as the face gear 510 moves in the axial direction of the output shaft 61a and approaches the bottom wall portion 52a, the inner peripheral surface 515 of the recessed portion 514 is butted against the outer peripheral surface 512 of the convex portion 511 so as to bite into it.

[0159] Here, when the motor device 500 is driven, that is, when the window glass is raised or lowered, even if a thrust force acts on the face gear 510 and the face gear 510 approaches the bottom wall portion 52a, the convex portion 511 only fits loosely into the concave portion 514. Therefore, the face gear 510 can easily rotate relatively to the bottom wall portion 52a with almost no resistance. Therefore, when the motor device 500 is driven, the face gear 510 does not enter a locked state (a braked state) in which it cannot rotate relatively to the bottom wall portion 52a.

[0160] On the other hand, when a large external force is applied to the output shaft 61a, such as when the closed window glass is forcibly pushed down, a large thrust force acts on the face gear 510. This causes the face gear 510 to approach the bottom wall portion 52a more closely so as to eliminate the minute gap δS. As a result, the convex portion 511 fits tightly into the concave portion 514. Therefore, the inner peripheral surface 515 of the concave portion 514 is butted against the outer peripheral surface 512 of the convex portion 511 so as to bite into it, and the face gear 510 is unable to rotate relative to the bottom wall portion 52a (gear case 51) (locked state). This prevents the window glass from being forcibly pushed down, making it possible to protect the vehicle from theft, vandalism, and the like.

[0161] The seventh embodiment formed as above can also achieve the same advantageous effects as those of the above-mentioned embodiment 1. In addition, in the seventh embodiment, the so-called "lock mechanism" as described above is provided, so that the reliability of the motor device 500 can be further improved.

[0162] The present invention is not limited to the above-mentioned embodiments, and it goes without saying that various modifications can be made without departing from the scope of the present invention. For example, in the above-mentioned embodiments, the movement restricting portion of the present invention is the C-shaped retaining ring 54 or the ring-shaped member 320, 410 attached to the annular recess 52f, but the present invention is not limited to this. For example, a plurality of protruding members can be fixed to the radial inner side of the side wall portion 52b at intervals in the circumferential direction, thereby achieving the same function as the C-shaped retaining ring 54 or the ring-shaped member 320, 410.

[0163] In the above-mentioned third embodiment, the reinforcing portion 101 is formed of a honeycomb structure in which a plurality of regular hexagonal tubular portions 102 are arranged in the circumferential direction of the face gear 100. However, the present invention is not limited to this. For example, a reinforcing portion made of hemispherical projections and recesses or linear ribs may also be used.

[0164] Furthermore, in each of the above-described embodiments, the motor devices 10, 70, 300, and 500 are shown as being applied to a drive source for a power window device that raises and lowers the window glass of a vehicle. However, the present invention is not limited to this, and can be applied to other drive sources such as an electric sunroof device or a sliding door device mounted on a vehicle.

[0165] In addition, the material, shape, size, number, installation location, etc. of each component in each of the above-mentioned embodiments are arbitrary as long as the present invention can be achieved, and are not limited to the above-mentioned embodiments. [Explanation of symbols]

[0166] 10: motor device, 30: motor section, 31: yoke, 31a: bottom section, 32: permanent magnet, 33: armature, 33a: armature core, 34: coil, 35: armature shaft (rotating shaft), 36: commutator, 37: brush holder, 38: pinion gear (first gear), 38a: main body shaft section, 38b: helical teeth (first teeth section), 50: gear section, 51: gear case (housing), 52: reduction mechanism accommodating section, 52a: bottom wall section, 52b: side wall section (cylindrical wall section), 52c: insertion hole, 52d: annular step section, 52e: recess, 52f: annular recess (mounting recess), 53: brush holder retaining portion, 54: C-shaped retaining ring (movement restricting portion), 54a: first end portion, 54b: second end portion, 55: through hole, 56: mounting portion, 56a: collar, 57: cover member fixing claw, 58: cover member (housing), 58a: bearing protrusion portion, 58b: engagement claw, 60: face gear (second gear), 61: main body disc portion, 61a: output shaft, 61b: annular surface portion, 61c: serration portion, 62: gear forming portion, 62a: first surface portion, 62b: second surface portion, 62c: arc-shaped teeth, 62d: meshing recess (second tooth portion), 62e: edge portion, 70: motor device, 80: gear portion, 81: gear case (housing ), 82: Reduction mechanism accommodating section, 82a: Center pole, 82b: Base section, 82c: Bearing mounting hole, 88: Cover member (housing), 88a: Output shaft insertion hole, 90: Face gear (second gear), 91a: Output shaft, 100: Face gear (second gear), 101: Reinforcement section, 102: Tubular section, 200: Pinion gear (first gear), 201: Spiral teeth (first teeth section), 210: Face gear (second gear), 220: Meshing recess (second teeth section), 230: Arc-shaped teeth, 300: Motor device, 310: Face gear (second gear), 311: Protrusion section, 312: Outer periphery, 320: Ring shaped member (movement restriction portion), 321: outer periphery, 322: hole, 323: inner periphery, 400: face gear (second gear), 401: protrusion, 402: thinning portion, 410: ring-shaped member (movement restriction portion), 411: hole, 500: motor device, 510: face gear (second gear), 511: convex portion, 512: outer periphery, 513: thinning portion, 514: concave portion, 515: inner periphery, AG: air gap, AR: area, B1: first radial bearing, B2: second radial bearing, B3: third radial bearing, BL: reference line, CN: connector member, CP: claw portion, GC: meshing center, S1: fixing screw,SD: Reduction mechanism, TB: Thrust bearing, δS: Minute gap,

Claims

1. A motor device having a motor portion and a gear portion, A rotating shaft provided in the motor unit; an output shaft provided in the gear portion and rotated about an axis perpendicular to an axis of the rotation shaft; a first gear including a first tooth portion extending helically in an axial direction of the rotating shaft; a second gear having a second tooth portion meshed with the first tooth portion in the axial direction of the output shaft, the second gear rotating the output shaft; a housing that accommodates the first gear and the second gear; Equipped with the housing has a cylindrical wall portion surrounding the radially outer side of the second gear, A movement restricting portion that prevents the second gear from moving in the axial direction of the output shaft is provided on a radially inner side of the cylindrical wall portion. Motor device.

2. 2. The motor device according to claim 1, The cylindrical wall portion has a mounting recess recessed on a radially outer side of the cylindrical wall portion, The movement restricting portion is a metal C-shaped retaining ring having a circumferential portion cut out therefrom, and is attached to the mounting recess. Motor device.

3. 2. The motor device according to claim 1, The housing includes a bottom wall. The second gear is disposed between the bottom wall portion and the movement restricting portion in an axial direction of the second gear. Motor device.

4. 2. The motor device according to claim 1, the second gear has a first surface portion on which the second tooth portion is formed, and a second surface portion provided on a side opposite to a side on which the first surface portion is provided in an axial direction of the second gear, The second surface portion is provided with a reinforcing portion that suppresses distortion of the second tooth portion. Motor device.

5. The reinforcing portion has a honeycomb structure formed by arranging a plurality of regular hexagonal tubular portions in the circumferential direction of the second gear. The motor device according to claim 4.

6. The housing rotatably supports both axial sides of the first gear. The motor device according to claim 1 .

7. The first gear is formed in a tapered shape toward the rotation center of the second gear. The motor device according to claim 1 .

8. 2. The motor device according to claim 1, the second gear includes a tapered protrusion protruding toward a side on which the movement restricting portion is disposed, the movement restricting portion includes a tapered hole portion into which the protrusion can be fitted when the second gear moves in the axial direction of the output shaft and approaches the movement restricting portion. Motor device.

9. When a line segment extending in the axial direction of the output shaft is taken as a reference line, an inclination angle of an acute angle side of an outer circumferential surface of the protrusion with respect to the reference line is smaller than an inclination angle of an acute angle side of an inner circumferential surface of the hole with respect to the reference line; The motor device according to claim 8.

10. When the output shaft is viewed in the axial direction, an outer circumferential surface of the protrusion and an inner circumferential surface of the hole overlap with meshing portions of the first tooth portion and the second tooth portion. The motor device according to claim 9.

11. 4. The motor device according to claim 3, the second gear includes a tapered protrusion protruding toward a side on which the bottom wall portion is disposed, The bottom wall portion has a tapered recess into which the protrusion can be fitted when the second gear moves in the axial direction of the output shaft and approaches the bottom wall portion. Motor device.

12. When a line segment extending in the axial direction of the output shaft is taken as a reference line, an inclination angle of an acute angle side of an outer circumferential surface of the protruding portion with respect to the reference line is larger than an inclination angle of an acute angle side of an inner circumferential surface of the recessed portion with respect to the reference line; The motor device according to claim 11.

13. When the output shaft is viewed in the axial direction, an outer circumferential surface of the protruding portion and an inner circumferential surface of the recessed portion overlap with meshing portions of the first tooth portion and the second tooth portion. The motor device according to claim 12.

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