ENGINE DELAYS MECHANISM

Abstract

Motor delay mechanism (10) comprising: a motor part (50) with a rotating shaft (53); a delay mechanism (60) that delays the rotation of the rotating shaft (53) and includes: a first gear (61) which is provided in such a way that it rotates integrally with the rotating shaft (53); a second gear (62) that meshes with the first gear (61) and rotates at a lower speed than the first gear (61); and an output shaft (63) which is provided in a center of rotation of the second gear (62); and a gear housing (20) which rotatably accommodates the first gear (61) and the second gear (62), wherein a locking element (70) which maintains the engagement between the first gear (61) and the second gear (62) is provided on one side of the first gear (61) opposite one side of the second gear (62) in the gear housing (20), wherein the gear housing (20) comprises: a hub section (21a) that supports the output shaft (63); and a locking element receiving section (22a) that supports the locking element (70), wherein the rotating shaft (53) and the output shaft (63) are provided parallel to each other, the first gear (61) is a pinion with one tooth (61a), and the second gear (62) is a helical gear with inclined teeth (62c) with which the one tooth (61a) meshes, and wherein the locking element (70) is arranged at least in a longitudinal central section of the pinion, wherein the motor deceleration mechanism (10) is characterized in that a fastening section (71a) for fastening the locking element (70) to the gearbox housing (20) is provided in a central section of the locking element (70) in a longitudinal direction of the pinion and that the locking element (70) and the locking element receiving section (22a) each have inclined surfaces (71b, 22c) for positioning the locking element (70) in relation to the locking element receiving section (22a), making it possible to easily carry out the fastening process on the fastening section (71a).

Description

BACKGROUND Technical area

[0001] The disclosure relates to a motor with a deceleration or braking or retardation mechanism, which includes a motor part with a rotating or pivoting shaft and a retardation mechanism for slowing down or braking or retarding the rotation or turning of the pivoting shaft. Description of the state of the art

[0002] Conventionally, a motor with a delay mechanism, capable of generating high power or output despite its small size, was used as a drive source for wiper devices, electric window lifters, and the like, mounted on vehicles such as automobiles. Such a vehicle-mounted motor with a delay mechanism is described, for example, in patent literature 1.

[0003] The motor with delay mechanism described in patent specification 1 comprises a brushless motor with a pinion and a helical gear or helical spur gear with an output shaft that delays and outputs the rotation of the pinion. The pinion and the helical spur gear form a delay mechanism and mesh with each other. Furthermore, the axis of the pinion and the axis of the output shaft are parallel to each other.

[0004] CH 324 818 A discloses a worm gear in which a worm is held at its part provided with the screw thread opposite a field of engagement of the worm wheel in a sliding bearing which comprises a part of the worm circumference.

[0005] DE 10 2015 117 442 A1 discloses a drive device comprising a reduction gear, a receiving section, and an output unit. The reduction gear has at least two meshing helical gears made of resin. The at least two helical gears include an output-side helical gear and another helical gear. The output-side helical gear is located closer to the output unit in a power transmission path of the reduction gear than the other helical gear. The housing cover has a limiting section located in an area containing a straight line that intersects the first central axis and the second central axis. The limiting section projects towards the underside of the gear receiving section.The restraint section is designed to allow sliding contact with the output-side helical gear in order to limit axial bending of the output-side helical gear. State of the art patent literature

[0006] [Patent literature 1] published Japanese patent application JP 2020-18035A. BRIEF DESCRIPTION OF THE INVENTION Problems to be solved

[0007] However, according to the technology described in the aforementioned patent literature 1, a relatively large space is formed on one side of the pinion, opposite the side of the helical gear, within a gearbox housing. This space is required to accommodate a first ball bearing, which supports the pinion at a specific location within the gearbox housing, allowing it to rotate or turn freely.

[0008] Because there is a space on the side of the pinion opposite the side of the helical gear, applying a large external force to the output shaft, for example, results in a large load being applied to the pinion via the helical gear, and there is a risk that the pinion will bend away from the helical gear. If the pinion bends, it can separate from the helical gear.

[0009] One purpose of the revelation is to provide a motor with a delay mechanism that prevents the gears from disengaging or breaking free even when a large external force is applied to the output shaft. Means to solve the problems

[0010] The present invention is defined in the appended claim 1. The dependent claims describe advantageous embodiments of the invention. The following disclosure serves to facilitate understanding of the invention. According to one aspect of the disclosure, a motor delay mechanism is provided, comprising a motor part with a rotating shaft and a delay mechanism that delays the rotation of the rotating shaft, and further comprising a first gear that is provided to rotate integrally with the rotating shaft; a second gear that meshes with the first gear and rotates at a lower speed than the first gear; and an output shaft provided at a center of rotation of the second gear. The motor delay mechanism further comprises a gear housing that rotatably receives the first gear and the second gear. An engagement retaining element orA locking element that maintains the engagement between the first gear and the second gear is provided on one side of the first gear, opposite one side of the second gear in the gearbox housing. Effects

[0011] According to the disclosure, the engagement retaining element for maintaining the engagement between the first gear and the second gear is provided on the side of the first gear, opposite the side of the second gear in the gearbox housing, so that separation or loosening of the gears can be prevented even when a large external force is applied to the output shaft. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a cross-sectional view showing the internal structure of the motor deceleration mechanism. Fig. Figure 2 is a perspective view showing the inside of the gearbox housing. Fig. Figure 3 is a perspective view showing the side of the helical gear of the bearing holder. Fig. Figure 4 is an enlarged view of the dashed circle part A in Fig. 1, which shows the gap between the components. Fig. Figure 5 is a perspective exploded view showing the bearing holder, the helical gear and the gearbox housing. Fig. Figure 6 is a perspective view showing the output shaft, helical gear, pinion, rotor and locking element. Fig. Figure 7 is a perspective view showing the securing element from the side of a pair of surrounding wall sections. Fig. Figure 8 is a perspective view showing the securing element from the side of the solid main body section. Fig. Figure 9 is a cross-sectional view along line BB in Fig. 1, which shows the gearbox housing and the locking element. Fig. Figure 10 is an enlarged view of the dashed circle part A in Fig. 1, which shows a state of movement of the grease or lubricant. Fig. 11 is a view of arrow C in Fig. 1, which illustrates the positional relationship between the helical gear and the locking element. Fig. Figure 12 is a perspective view showing the second embodiment (bearing holder). Fig. Figure 13 is a perspective view showing the third embodiment (safety element). DESCRIPTION OF THE EXECUTION FORMS

[0012] The first embodiment of the disclosure is described in detail below with reference to the drawings.

[0013] Fig. Figure 1 is a cross-sectional view showing the internal structure of the motor deceleration mechanism. Fig. Figure 2 is a perspective view showing the inside of the gearbox housing. Fig. Figure 3 is a perspective view showing the side of the helical gear of the bearing holder. Fig. Figure 4 is an enlarged view of the dashed circle part A in Fig. 1, which shows the gap between the components. Fig. Figure 5 is a perspective exploded view showing the bearing holder, the helical gear and the gearbox housing. Fig. Figure 6 is a perspective view showing the output shaft, helical gear, pinion, rotor and locking element. Fig. Figure 7 is a perspective view showing the securing element from the side of a pair of surrounding wall sections. Fig. Figure 8 is a perspective view showing the securing element from the side of the solid main body section. Fig. Figure 9 is a cross-sectional view along line BB in Fig. 1, which shows the gearbox housing and the locking element. Fig. Figure 10 is an enlarged view of the dashed circle part A in Fig. 1, which shows a state of movement of the grease or lubricant. Fig. 11 is a view of arrow C in Fig. 1, which illustrates the positional relationship between the helical gear and the locking element. [Overview of the motor delay mechanism]

[0014] A in Fig. The motor delay mechanism 10 shown in Figure 1 is used, for example, as a drive source for a wiper device attached to a vehicle, such as an automobile. In particular, the motor delay mechanism 10 serves to pivot a wiper element (not shown), which is arranged in front of a windshield (not shown) of the vehicle and is pivotably mounted on the windshield, within a predetermined wiping range between a lower reversal position and an upper reversal position.

[0015] The motor delay mechanism 10 includes a housing 11, which forms its outer shell. A brushless motor 50 and a delay mechanism 60 are rotatably mounted inside the housing 11. The brushless motor 50 corresponds to the motor part in the disclosure.

[0016] Furthermore, a first sensor plate or sensor board 12 and a second sensor board 13, which are used to detect the rotational states of a rotor 52 and a helical gear 62, are each housed in the enclosure 11. The enclosure 11 then contains a gearbox housing 20, made of die-cast aluminum, and a cover element 30, which is formed by pressing a steel plate. [Gearbox housing]

[0017] As in Fig. 1 and Fig. As shown in Figure 2, the gearbox housing 20 is essentially shell-shaped, formed by injection molding a molten aluminum material. In particular, the gearbox housing 20 comprises a bottom wall section 21, a side wall section 22 which is integral or integral with the circumference of the bottom wall section 21, and a bearing holder mounting section 23 to which the bearing holder 40 (see Figure 2) is attached. Fig. 3) is mounted.

[0018] A substantially central section of the bottom wall section 21 is provided with a cylindrical hub section 21a, which rotatably supports an output shaft 63. The hub section 21a corresponds to the output shaft support section in the disclosure, and a plurality of reinforcing ribs 21b, which are formed in a substantially triangular shape, are provided on the radially outer side of the hub section 21a. These reinforcing ribs 21b serve to increase the fastening strength of the hub section 21a to the bottom wall section 21, and, for example, eight reinforcing ribs 21b are arranged at equal intervals in the circumferential direction of the hub section 21a.

[0019] A cylindrical bearing element 14, a so-called "metal", is mounted on the radial inner side of the hub section 21a. Therefore, the output shaft 63 can rotate freely without rattling with the hub section 21a. An O-ring 15, made of an elastic material such as rubber, is located on the tip side (top side in Fig. 1) and mounted on the radially inner side of the hub section 21a. This prevents rainwater, dust and the like from penetrating between the output shaft 63 and the bearing element 14.

[0020] Here, a retaining ring 16 is attached to the central longitudinal section of the output shaft 63. The retaining ring 16 is hooked onto the tip section of the hub section 21a. Therefore, the hub section 21a is clamped between the helical gear 62 and the retaining ring 16, and the output shaft 63 is in a state that prevents it from disengaging from the hub section 21a. Thus, rattling of the output shaft 63 relative to the hub section 21a is suppressed, ensuring smooth operation of the motor deceleration mechanism 10.

[0021] A bearing element receiving section 21c is provided at a position eccentric to the hub section 21a of the bottom wall section 21. The bearing element receiving section 21c is cylindrical with a base and projects from the bottom wall section 21 towards the outside of the gearbox housing 20 (upper side in Fig. 1) Then a first ball bearing BR1, which rotatably supports the tip side of the pinion 61, is housed within the bearing element receiving section 21c.

[0022] A retaining element receiving section 22a is provided in a section of the side wall section 22 near the bearing holder mounting section 23. The retaining element receiving section 22a corresponds to the engagement retaining element support section in the disclosure and is located near the bearing element receiving section 21c. A retaining element 70 is housed inside the retaining element receiving section 22a. Here, the retaining element 70 is supported by the retaining element receiving section 22a and positioned to cover the circumference of the pinion 61. The retaining element 70 then serves to suppress bending of the pinion 61 when a large external force is applied to the output shaft 63.

[0023] Furthermore, a single screw hole 22b is provided in the locking element receiving section 22a. The screw hole 22b is oriented radially (left-right direction). Fig. 1) The pinion 61 and the helical gear 62 are opened. Then, a fastening screw SC1 is inserted through the screw hole 22b to secure the locking element 70 to the locking element receptacle 22a. In this way, the locking element 70 is secured inside the locking element receptacle 22a without rattling. This also ensures the quiet operation of the motor deceleration mechanism 10.

[0024] As in Fig. 2 and Fig. As shown in Figure 9, a pair of housing-side inclined surfaces 22c are provided inside the locking element receiving section 22a. These housing-side inclined surfaces 22c face each other in a direction that intersects the axial direction of the pinion 61 and the helical gear 62 (see Figure 9). Fig. 1) The two housing-side inclined surfaces 22c are on the tip side in the insertion direction of the locking element 70 (see Fig. 7 and Fig. 8) arranged in the locking element receiving section 22a. In other words, the two housing-side inclined surfaces 22c are arranged on a section of the gearbox housing 20 near the bottom wall section 21.

[0025] Then a pair of locking element-side inclined surfaces 71b (see Fig. 7 to Fig. 9), which are provided on the locking element 70, against the pair of housing-side inclined surfaces 22c. Thus, as indicated by arrow M1 in Fig. As indicated in Figure 9, the pair of locking element-side inclined surfaces 71b abuts the pair of housing-side inclined surfaces 22c when the locking element 70 is mounted on the locking element receiving section 22a, and the locking element 70 is arranged (centered) in a prescribed position in the locking element receiving section 22a.

[0026] This means that the pair of housing-side inclined surfaces 22c and the pair of locking element-side inclined surfaces 71b have a function to position the locking element 70 in a controlled position with respect to the locking element receiving section 22a. Therefore, it is possible to easily carry out the subsequent tightening or fastening process of the fastening screw SC1 (see arrow M2 in Fig. 9). The pair of housing-side inclined surfaces 22c and the pair of locking element-side inclined surfaces 71b each correspond to the chamfered surfaces in the disclosure.

[0027] As in Fig. 1 and Fig. As shown in Figure 2, a first convex locking section 21d, which is formed in a substantially ring-shaped form, is provided on the inside of the bottom wall section 21, that is, on a side of the bottom wall section 21 that is opposite the side of the reinforcing ribs 21b. The first convex locking section 21d has a substantially semicircular cross-section and projects towards the inside of the gearbox housing 20 (lower side in Figure 2). Fig. 1) protrudes at a predetermined height. The first convex locking section 21d has a function to prevent the helical gear 62 from tilting when a large external force is applied to the output shaft 63. The first convex locking section 21d corresponds to the tilt-prevention section in the disclosure.

[0028] Furthermore, as in Fig. As shown in Figure 2, a concave bearing holder positioning section 23a is provided in the bearing holder mounting section 23. The concave bearing holder positioning section 23a is designed to surround the circumference of the locking element receiving section 22a and is recessed in the direction of the locking element receiving section 22a. Then a convex positioning section 41a (see Figure 2) is provided. Fig. 3), which is provided on the bearing holder 40, fitted into the concave bearing holder positioning section 23a.

[0029] This allows the bearing holder 40 to be mounted in a controlled position relative to the bearing holder mounting section 23 with high accuracy. Accordingly, the subsequent fastening of the bearing holder 40 to the bearing holder mounting section 23 can be carried out using tightening screws SC2 (see Fig. 1) This facilitates the assembly, and it is possible to arrange the second ball bearing BR2, held by the bearing holder 40, and the first ball bearing BR1, received in the bearing element receiving section 21c, coaxially with high accuracy. Therefore, variations in the rotational resistance of the pinion 61 can be suppressed for each product. [Warehouse Holder]

[0030] As in Fig. 1 and Fig. As shown in Figure 3, the bearing holder 40, which is mounted on the bearing holder mounting section 23, holds the first sensor board 12 and the second ball bearing BR2, which rotatably supports the base end of the pinion 61. The bearing holder 40 is composed of a holder main body 41 and a support 42, formed by butting them together. The second ball bearing BR2 is then positioned between the holder main body 41 and the support 42.

[0031] Both the main holder body 41 and the support 42 are made of die-cast aluminum and can be securely and rattle-free attached to the gearbox housing 20 (bearing holder mounting section 23). Furthermore, in Fig. 3 only the holder main body 41 is shown, which forms the bearing holder 40.

[0032] As in Fig. As shown in Figure 3, the convex positioning section 41a, which leads into the concave bearing holder positioning section 23a (see Figure 3) are the convex positioning section 41a, which leads into the concave bearing holder positioning section 23a (see Figure 3). Fig. 2) is fitted and is essentially C-shaped, and a pair of second convex locking sections 41b, which are essentially arc-shaped, are provided on the holder main body 41 on the side of the helical spur gear 62. The projection height of the convex positioning section 41a is greater than the projection height of the pair of second convex locking sections 41b.

[0033] Then, in a state in which the bearing holder 40 (holder main body 41) is mounted on the gearbox housing 20 (bearing holder mounting section 23), the two second convex locking sections 41b are arranged such that they are opposite the first convex locking section 21d, which is provided on the gearbox housing 20, from the axial direction of the output shaft 63 (see Fig. 1) That is, the pair of second convex locking sections 41b also has a function of preventing the helical gear 62 from tilting when a large external force is applied to the output shaft 63. The pair of second convex locking sections 41b also has a substantially semicircular cross-section. Here, the pair of second convex locking sections 41b corresponds to the tilt-prevention section in the disclosure.

[0034] Three screw holes 41c are provided on the outer circumferential edge of the main holder body 41. The fastening screws SC2 for attaching the cover element 30 and the bearing holder 40 to the gearbox housing 20 are inserted through these screw holes 41c, as shown in Fig. 1 shown. Fig. However, 1 only shows one fastening screw SC2.

[0035] Furthermore, an insertion hole 41d is provided in the essentially central section of the holder's main body 41, through which the pinion 61 is inserted without contact. The length dimension of the pair of second convex locking sections 41b is freely selectable and is not limited to the short length dimension, as indicated by the solid line in Fig. 3 indicated, and can be set to a long length dimension, as indicated by the dashed arrow in the same drawing. [Cover element]

[0036] As in Fig. As shown in Figure 1, the cover element 30, which forms the housing 11, includes a circuit board retaining section 31, designed in a substantially flat plate shape, and a motor mounting section 32, designed in a substantially cylindrical shape with a base. The circuit board retaining section 31 faces the helical gear 62 in the axial direction of the output shaft 63 when the cover element 30 is mounted on the gearbox housing 20. The second sensor circuit board 13 is then attached to the inside of the circuit board retaining section 31 via a base element BS.

[0037] Furthermore, the circuit board retaining section 31 is provided with an insertion hole 31a through which a plug / connector connection section CC, which is connected to an external plug / connector CN on the vehicle side, is inserted. Here, the connector connection section CC is attached to the base element BS via a conductive element (not shown) and electrically connected to the first sensor board 12, the second sensor board 13, and the brushless motor 50. In this way, an in-vehicle controller (not shown), which is connected to the external connector CN, can precisely drive the brushless motor 50 according to detection signals from the first and second sensor boards 12 and 13.

[0038] Three Hall sensors 12a (only one is shown in the drawing) are mounted on the first sensor board 12, and these Hall sensors 12a correspond to the U-phase, V-phase, and W-phase, respectively. Each of the three Hall sensors 12a faces a permanent magnet MG, which is mounted on the rotor 52 in the axial direction of the pinion 61. The vehicle's internal controller gathers (grasps) the rotational state (speed, direction of rotation, etc.) of the brushless motor 50 (pinion 61) based on the detection signals from the three Hall sensors 12a and precisely controls the rotational state of the brushless motor 50 on this basis.

[0039] On the other side, a single MR sensor 13a is mounted on the second sensor board 13, and the MR sensor 13a faces a sensor magnet SM, which is attached to the center of rotation of the helical gear 62 in the axial direction of the output shaft 63. The vehicle's internal controller then detects the rotational state (rotational position, etc.) of the output shaft 63 from the detection signal of the MR sensor 13a and, based on this, precisely controls the wiping position of the wiper element (not shown) relative to the windshield (not shown).

[0040] In a state where the cover element 30 is mounted on the gearbox housing 20, the motor mounting section 32 protrudes on the side (lower side in Fig. 1) opposite the side of the gearbox housing 20. Furthermore, in a state where the cover element 30 is mounted on the gearbox housing 20, the motor mounting section 32 faces the bearing element mounting section 21c of the gearbox housing 20. The brushless motor 50 is then housed inside the motor mounting section 32.

[0041] Furthermore, a shaft hole 32a is provided in the essentially central section of the motor mounting section 32, and the bearing element BR is provided in the section of the shaft hole 32a. The bearing element BR then rotatably supports the elongated base end (lower side in Fig. 1) the rotating shaft 53 of the brushless motor 50. In this way, the rotating shaft 53 including the pinion 61 is rotatably mounted by a total of three bearings (first and second ball bearings BR1 and BR2 and bearing element BR). [Brushless motor]

[0042] The brushless motor 50, housed in the motor mounting section 32, contains a stator core (stator) 51, which has a substantially cylindrical shape. The stator core 51 is fixedly attached to the retainer 42 of the bearing holder 40 within the motor mounting section 32 in a non-rotating state (details not shown).

[0043] The stator core 51 is formed by laminating a plurality of thin steel plates (magnetic material), and a plurality of teeth (not shown) are provided radially on its outer radial surface. Then, coils 51a, corresponding to the U-phase, V-phase, and W-phase, are each wound with a predetermined number of turns around these teeth by concentrated winding.

[0044] By alternately applying drive currents to the coils 51a of the U-phase, V-phase, and W-phase at predetermined times by the vehicle's internal controller, the rotor 52, which is provided on the radially outer side of the stator core 51, is rotated in a predetermined direction with a predetermined drive torque. In other words, the brushless motor 50 according to the present embodiment uses an external rotor brushless motor.

[0045] The rotor 52 is rotatably mounted on the radially outer side of the stator core 51 with a tiny (minute) gap (air gap) between them. As shown in Fig. 1 and Fig. As shown in Figure 6, the rotor 52 serves to rotate the rotating shaft 53, which is integrally provided with the pinion 61, and includes a rotor body 54 with a substantially U-shaped cross-section formed by pressing a steel plate (magnetic material) or the like. A plurality of permanent magnets MG, essentially tile-shaped, are then attached to the radial inner surface of the rotor body 54. Furthermore, the rotating shaft 53, which is integrally provided with the pinion 61, is rigidly connected to the center of rotation of the rotor body 54 by an interference fit or the like. [Delay mechanism]

[0046] As in Fig. 1 and Fig. As shown in Figure 6, the delay mechanism 60, which is rotatably housed inside the casing 11 (gearbox housing 20), comprises the pinion (first gear) 61, which is integrally formed with the rotating shaft 53, and the helical gear (second gear) 62, which meshes with the pinion 61 and rotates at a lower speed than the pinion 61. In this case, the axis of the pinion 61 and the axis of the helical gear 62 are parallel to each other. In other words, the rotating shaft 53 and the output shaft 63 are parallel to each other. In this way, the delay mechanism 60 can be built more compactly than a worm gear reduction gearbox with a worm and a worm wheel whose axes intersect.

[0047] Furthermore, the pinion 61 is located on the side of the rotating shaft 53 (intake side) of the motor deceleration mechanism 10, and the helical gear 62 is located on the side of the output shaft 63 (exhaust side) of the motor deceleration mechanism 10. That is, the deceleration mechanism 60 reduces the high-speed rotation of the pinion 61, which has a small number of teeth, to the low-speed rotation of the helical gear 62, which has a large number of teeth. Therefore, the helical gear 62 rotates at a lower speed than the pinion 61.

[0048] The rotating shaft 53 with the pinion 61 is made of metal, and the pinion 61 has the in Fig. 1 and Fig. Figure 7 shows the form. In particular, a spiral tooth (tooth) 61a is integrally provided with the circumference of the pinion 61, and the axial length of the spiral tooth 61a is slightly greater than the axial length of the helical gear 62. Thus, the spiral tooth 61a meshes reliably with the helical gear 62.

[0049] The spiral tooth 61a extends spirally and continuously in the axial direction of the pinion 61, and the pinion 61 is provided with only one spiral tooth 61a. That is, the number of teeth of the pinion 61 is "1". The spiral tooth 61a is then designed such that it has a circular cross-sectional shape and engages (meshes) in a meshing recess 62d of the helical gear 62.

[0050] The helical gear 62, which forms the delay mechanism 60, is made of plastic and has a shape as described in Fig. 1 and Fig. Figure 6 is shown. In particular, the helical gear 62 includes a gear body 62a, which is essentially disk-shaped, and the base end of the output shaft 63 is fixed to the center of rotation of the gear body 62a by a press fit or similar. Thus, the output shaft 63 rotates together with the helical gear 62. Furthermore, the sensor magnet SM is located at the center of rotation of the gear body 62a and on the side of the second sensor board 13 (lower side in Figure 6). Fig. 1) attached.

[0051] A gear-forming section 62b, having a substantially cylindrical shape, is provided on the radially outer side of the main gear body 62a. A plurality of inclined teeth 62c are provided on the gear-forming section 62b, arranged in its direction of rotation. These inclined teeth 62c are inclined at a predetermined angle with respect to the axial direction of the pinion 61, so that the helical gear 62 rotates with the rotation of the spiral tooth 61a. In particular, the engagement recess 62d is provided between the adjacent inclined teeth 62c, and the spiral tooth 61a engages in and meshes with the engagement recess 62d. The engagement recess 62d is also configured to have a circular cross-sectional shape.

[0052] A first surface SF1 and a second surface SF2 are each provided on both axial sides of the gear-forming section 62b. Then, as in Fig. 1 and Fig. As shown in Figure 5, the first surface SF1 is located on the side of the bottom wall section 21 of the gearbox housing 20, and the second surface SF2 is located on the side of the bearing holder 40. Furthermore, in the axial direction of the output shaft 63, the first surface SF1 faces the first convex locking section 21d, and the second surface SF2 faces the pair of second convex locking sections 41b. This prevents the helical gear 62 from tilting when a large external force is applied to the output shaft 63.

[0053] As in Fig. As shown in Figure 4, when no large external force is applied to the output shaft 63, a tiny gap δS1 forms between the first surface SF1 and the first convex locking section 21d. Furthermore, when no large external force is applied to the output shaft 63, a tiny gap δS2 forms between the second surface SF2 and the pair of second convex locking sections 41b (δS1 ≈ δS2). Thus, during "normal operation" of the motor deceleration mechanism 10, the helical gear 62 can rotate freely without contacting either the gearbox housing 20 or the bearing holder 40, without a large external force being applied to the output shaft 63.

[0054] In contrast, during an “overload operation” of the motor deceleration mechanism 10, in which a large external force is applied to the output shaft 63, the helical gear 62 tends to tilt due to the inclination of the inclined teeth 62c with respect to the axis of the output shaft 63. Then, depending on the direction of rotation of the helical gear 62, the first surface SF1 contacts the first convex locking section 21d (see the dashed arrow in Figure 1). Fig. 5), and the second surface SF2 touches the pair of second convex securing sections 41b (see the dashed arrow in Fig. 5) Consequently, the helical gear 62 is supported by the first and second convex retaining sections 21d and 41b and prevented from tilting further. Accordingly, a deterioration of the engagement between the helical gear 62 and the pinion 61 is prevented, and the plastic helical gear 62 is prevented from being hollowed out and damaged by the metal pinion 61.

[0055] Here, the number of inclined teeth 62c (engagement recesses 62d) of the helical gear 62 is 40. That is, in the present embodiment, the reduction ratio of the deceleration mechanism 60 with the pinion 61 and the helical gear 62 is 40. [Safety element]

[0056] As in Fig. 1, Fig. 4 and Fig. 6 to Fig. As shown in Figure 8, the locking element 70, housed in the locking element receiving section 22a of the gearbox housing 20, is formed by injection molding a resin material, such as plastic, in a substantially rectangular parallelepiped shape. The locking element 70 comprises a fixed main body section 71, which is attached to the gearbox housing 20; a pair of surrounding wall sections 72, which are integral with the fixed main body section 71 and surround the circumference of the pinion 61 together with the fixed main body section 71; and an annular wall section 73, which is integral with one longitudinal side (right side in Figure 8). Fig. 7 and Fig. 8) these surrounding wall sections 72 are provided and are essentially ring-shaped.

[0057] The fixed main body section 71 is provided with a female screw section 71a. The female screw section 71a corresponds to the fastening section in the disclosure and is provided in the central section of the locking element 70 in the longitudinal direction of the pinion 61. Furthermore, the female screw section 71a is arranged on the side (rear surface side) of the fixed main body section 71 opposite the side of the pinion 61. The fastening screw SC1 is then tightened on the female screw section 71a to fasten the locking element 70 to the gear housing 20.

[0058] Furthermore, the pair of sloping surfaces 71b on the locking element side is located on one longitudinal side (right side in Fig. 7 and Fig. 8) of the fixed main body section 71. These locking element-side inclined surfaces 71b each abut the pair of housing-side inclined surfaces 22c (see Fig. 2 and Fig. 9), which are provided on the gearbox housing 20. As in Fig. As shown in Figure 9, in a state where the locking element-side inclined surfaces 71b abut the housing-side inclined surfaces 22c, a space SP is formed between the tip section in the insertion direction of the locking element 70 and the lower section of the locking element receiving section 22a. Thus, the pair of locking element-side inclined surfaces 71b can abut against the pair of housing-side inclined surfaces 22c without rattling, and the positioning accuracy of the locking element 70 with respect to the gearbox housing 20 is improved.

[0059] As in Fig. 1, Fig. 4, Fig. 6 and Fig. As shown in Figure 10, in a state where the locking element 70 is attached to the gearbox housing 20, the fixed main body section 71, which forms the locking element 70, is positioned on the side of the pinion 61 opposite the side of the helical gear 62 in the gearbox housing 20. A tiny gap (clearance) δS3 is then formed between the pinion 61 and the fixed main body section 71. This tiny gap δS3 has essentially the same clearance dimension as the tiny gap δS1 between the first surface SF1 and the first convex locking section 21d, and the tiny gap δS2 between the second surface SF2 and the pair of second convex locking sections 41b (δS ≈ δS2 ≈ δS3).

[0060] Thus, during the “normal operation” of the motor delay mechanism 10, in which no large external force is applied to the output shaft 63, a load that bends the pinion 61 is not applied from the helical gear 62 to the pinion 61, so that the pinion 61 can rotate freely without touching the locking element 70.

[0061] Furthermore, since the hub section 21a, which supports the output shaft 63, and the locking element receiving section 22a, which supports the locking element 70, are each provided in the gearbox housing 20, which is made of aluminum and machined with high precision, it is possible to position the output shaft 63 and the locking element 70 with high accuracy. Accordingly, this also makes it possible to reduce the tiny gap δS3 between the pinion 61 and the fixed main body section 71, while the pinion 61 remains freely rotatable without contacting the locking element 70.

[0062] On the other hand, during the "overload operation" of the motor deceleration mechanism 10, in which a large external force is applied to the output shaft 63, the helical gear 62 tends to tilt relative to the axis of the output shaft 63 due to the angular position of the inclined teeth 62c. This exerts a large lateral force on the pinion 61 from its radial outer side. Furthermore, although the pinion 61 is made of metal, the section where the pinion 61 is located is particularly thin, making it susceptible to lateral stress. Consequently, the helical gear 62 forces the pinion 61 out of its radial direction, causing it to bend.

[0063] In this case, the substantially central section of the pinion 61 is pressed longitudinally by the helical gear 62. Therefore, the substantially central longitudinal section of the pinion 61 is brought into contact with the fixed main body section 71. Since the substantially central section of the pinion 61 is supported longitudinally by the fixed main body section 71, the pinion 61 is prevented from bending further, and the engagement between the pinion 61 and the helical gear 62 is maintained. Here, the locking element 70 corresponds to the engagement retaining element in the disclosure.

[0064] When the pinion 61 bends, the essentially central longitudinal section of the fixed main body section 71 is compressed. However, this essentially central longitudinal section of the fixed main body section 71 is the section that is secured to the gearbox housing 20 by the fastening screw SCl and is therefore the least prone to rattling. Accordingly, the retaining element 70 can support the pinion 61 without rattling with the gearbox housing 20, even if the pinion 61 bends repeatedly. Therefore, premature damage to the retaining element 70 is effectively prevented.

[0065] Furthermore, the tiny gap δS3 between the pinion 61 and the fixed main body section 71 is set to such a clearance dimension that the pinion 61 is prevented from disengaging from the helical gear 62. Moreover, as shown in Fig. 4 and Fig. As shown in Figure 10, in the present embodiment the fixed main body section 71 is provided substantially over the entire area of ​​the pinion 61 in the longitudinal direction, but as described above, it is known that the section of the pinion 61 that is substantially central in the longitudinal direction is bent during the “overload operation” of the motor deceleration mechanism 10. Therefore, the fixed main body section 71 of the locking element 70 is arranged at least in the central longitudinal section of the pinion 61. In particular, the hatched sections shown in Figure 10 can be seen as being located in the central longitudinal section of the pinion 61. Fig. 10 of the two-point catenary lines are removed. In this case, the weight of the locking element 70 can be reduced, and the thick section of the locking element 70 can be reduced to improve the dimensional accuracy of the locking element 70.

[0066] Furthermore, as in Fig. As shown in Figure 11, the pair of surrounding wall sections 72 extends from the fixed main body section 71 towards the helical gear 62, and a tiny gap δS4 is formed between the tip side of these surrounding wall sections 72 and the helical gear 62. These surrounding wall sections 72 are provided on both sides of the locking element 70 in the direction of rotation of the helical gear 62 and correspond to the second wall for preventing lubricant or grease leakage or lubricant leakage prevention wall within the scope of the disclosure. Furthermore, inclined surfaces 72a are provided on the tip side of each pair of surrounding wall sections 72 to be chamfered in the direction of rotation of the helical gear 62, and these inclined surfaces 72a extend in the direction of rotation of the helical gear 62 to follow the outer circumferential shape of the helical gear 62.Therefore, the space between the pair of inclined surfaces 72a and the helical gear 62 can be narrowed to form the tiny gap δS4.

[0067] Here, as in Fig. As shown in Figure 11, the formation of the tiny gap δS4 between the pair of surrounding wall sections 72 and the helical gear 62, when the helical gear 62 rotates in one direction, as indicated by the solid arrow ×, prevents lubricant or grease (not shown) applied to the engagement area between the pinion 61 and the helical gear 62 from escaping from the surrounding wall sections 72. Conversely, when the helical gear 62 rotates in the other direction, as indicated by the dashed arrow ×, lubricant applied to the engagement area between the pinion 61 and the helical gear 62 is also prevented from escaping from the surrounding wall sections 72.

[0068] The tiny gap δS4 has essentially the same clearance dimension as the tiny gap δS1 between the first surface SF1 and the first convex locking section 21d, the tiny gap δS2 between the second surface SF2 and the pair of second convex locking sections 41b, and the tiny gap δS3 between the pinion 61 and the fixed main body section 71 (δS1 ≈ δS2 ≈ δS3 ≈ δS4). Furthermore, one of the pair of surrounding wall sections 72 can also be removed and provided on at least one side of the locking element 70 in the direction of rotation of the helical gear 62. In this case, a single surrounding wall section 72 still prevents lubricant from leaking out of the surrounding wall section 72.

[0069] As in Fig. 7 and Fig. As shown in Figure 8, the ring-shaped wall section 73 is on one side (right side in Fig. 7 and Fig. 8) the locking element 70 is provided in the longitudinal direction of the pinion 61, and a pinion insertion hole 73a is provided in the substantially central section of the annular wall section 73. The pinion 61 is rotatably inserted through the pinion insertion hole 73a without touching the pinion insertion hole 73a, and a tiny gap δS5 is formed between the pinion 61 and the pinion insertion hole 73a (see Fig. 8).

[0070] The tiny gap δS5 has the same clearance dimension as the tiny gap δS3 between the pinion 61 and the fixed main body section 71 (δS3 = δS5).

[0071] By forming the tiny gap δS5 between the pinion 61 and the pinion insertion hole 73a in this manner, as shown in Fig. As shown in Figure 10, when the pinion 61 rotates in one direction, lubricant (not shown), which tends to move as indicated by the solid arrow, is prevented from running over and exiting the annular wall section 73 (see solid arrow ×). Then, when the pinion 61 rotates in one direction, the lubricant, which is driven toward that section of the annular wall section 73, is returned to the central longitudinal section of the pinion 61 when the pinion 61 rotates in the other direction, as indicated by the dashed arrow ◯. The annular wall section 73 corresponds to the first lubricant leakage prevention wall as described in the disclosure.

[0072] Here, in the present embodiment, the motor delay mechanism 10 is used as a drive source for a wiper device. Accordingly, when the wiper element (not shown) is pivoted, the pinion 61 and the helical gear 62 are each rotated in forward and reverse directions with predetermined cycles. As in Fig. As shown in Figure 10, by repeatedly rotating the pinion 61 and the helical gear 62 in one direction (forward rotation) and in the other direction (backward rotation), the lubricant is moved back and forth in the axial direction of the pinion 61 on the inside of the locking element 70. In other words, it is possible to keep the lubricant in the engagement area between the pinion 61 and the helical gear 62 for a long period of time.

[0073] In a state in which the locking element 70 is housed in the locking element receiving section 22a and the pair of locking element-side inclined surfaces 71b each abut the pair of housing-side inclined surfaces 22c, the annular wall section 73 enters the opening of the bearing element receiving section 21c, which is provided in the gearbox housing 20 (see Fig. 1, Fig. 4 and Fig. 10). This prevents the locking element 70 from rattling in the gearbox housing 20.

[0074] As described in detail above, in the present embodiment the locking element 70 for maintaining the engagement between the pinion 61 and the helical gear 62 is provided on the side of the pinion 61 that is opposite the side of the helical gear 62 in the gearbox housing 20, so that disengagement of the gears (disengagement of the pinion 61 and the helical gear 62) can be prevented even when a large external force is applied to the output shaft 63.

[0075] In this way, damage to the pinion 61 and the helical gear 62 (deceleration mechanism 60) can be prevented over a long period of time, and consequently the service life of the motor deceleration mechanism 10 can be extended. In other words, since the service life of the motor deceleration mechanism 10 can be extended, energy can be saved in the present embodiment for the manufacture of the motor deceleration mechanism 10, and consequently it is possible to achieve Goal No. 7 (affordable and clean energy for all) and Goal No. 13 (specific action against climate change) in the United Nations Sustainable Development Goals (SDGs).

[0076] Furthermore, according to the present embodiment, since the tiny gap δS3 is provided between the pinion 61 and the fixed main body section 71 of the locking element 70, the pinion 61 can be rotated freely during the "normal operation" of the motor deceleration mechanism 10 without significant external force being applied to the output shaft 63 and without contacting the locking element 70. Therefore, it is possible to effectively suppress the generation of abnormal noise by the motor deceleration mechanism 10 and to use the motor deceleration mechanism 10 in a vehicle, such as an electric vehicle, that requires silent operation.

[0077] Furthermore, according to the present embodiment, since the gearbox housing 20 contains the hub section 21a, which supports the output shaft 63, and the locking element receiving section 22a, which carries the locking element 70, the positions of the output shaft 63 and the locking element 70 can be arranged with high accuracy. Therefore, it is possible to reduce the tiny gap δS3 between the pinion 61 and the fixed main body section 71 while allowing the pinion 61 to rotate freely without contacting the locking element 70, and it is possible to prevent the motor deceleration mechanism 10 from becoming unnecessarily large.

[0078] Furthermore, according to the present embodiment, the locking element 70 and the locking element receiving section 22a each include the pair of locking element-side inclined surfaces 71b and the pair of housing-side inclined surfaces 22c for positioning the locking element 70 relative to the locking element receiving section 22a. Accordingly, when the locking element 70 is mounted in the locking element receiving section 22a, the pair of locking element-side inclined surfaces 71b can abut the pair of housing-side inclined surfaces 22c to position (center) the locking element 70 in a prescribed position within the locking element receiving section 22a. Therefore, it is possible to easily mount the motor delay mechanism 10.

[0079] Furthermore, according to the present embodiment, the rotating shaft 53 and the output shaft 63 are arranged parallel to each other, and the pinion 61 has a spiral tooth 61a, and the helical gear 62 has inclined teeth 62c with which the spiral tooth 61a engages. In this way, it is possible to achieve a large reduction ratio while keeping the deceleration mechanism 60 compact. Therefore, it is possible to reduce the size of the motor deceleration mechanism 10 and to easily use the motor deceleration mechanism 10 in a small vehicle, such as a compact car.

[0080] Furthermore, according to the present embodiment, the locking element 70 can also be arranged at least in the longitudinal central section of the pinion 61. In other words, as in Fig. As shown in Figure 10, the hatched sections surrounded by the two-point catenary lines can also be removed. In this case, the weight of the locking element 70 can be reduced, and the thickness of the locking element 70 can be reduced to improve the dimensional accuracy of the locking element 70 (injection-molded product).

[0081] Furthermore, according to the present embodiment, the female screw section 71a for fastening the locking element 70 to the gearbox housing 20 is provided in the longitudinally central section of the locking element 70 of the pinion 61. Accordingly, if the pinion 61 bends, the section of the fixed main body section 71 that rattles the least is pressed, and even if the pinion 61 bends repeatedly, the locking element 70 can support the pinion 61 without rattling relative to the gearbox housing 20. Therefore, it is possible to prevent premature damage to the locking element 70.

[0082] Furthermore, according to the present embodiment, the annular wall section 73, which prevents the lubricant applied between the pinion 61 and the helical gear 62 from escaping, is on one side (right side in Fig. 7 and Fig. 8) the locking element 70 is provided in the longitudinal direction of the pinion 61. Accordingly, as in Fig. As shown in Figure 10, when the pinion 61 rotates in one direction, the lubricant, which tends to move as indicated by the solid arrow, is prevented from running over the annular wall section 73 and exiting it. Therefore, it is possible to retain the lubricant in the engagement area between the pinion 61 and the helical gear 62 for a long period of time and consequently to operate the motor deceleration mechanism 10 smoothly for an extended period.

[0083] Furthermore, according to the present embodiment, the two surrounding wall sections 72, which prevent the lubricant applied between the pinion 61 and the helical gear 62 from escaping, are provided on both sides of the locking element 70 in the direction of rotation of the helical gear 62. Accordingly, as in Fig. As shown in Figure 11, when the helical gear 62 rotates in one direction and in the other, the lubricant applied to the engagement section between the pinion 61 and the helical gear 62 is prevented from escaping from the surrounding wall sections 72. This also allows the motor deceleration mechanism 10 to operate smoothly over a long period of time.

[0084] Furthermore, according to the present embodiment, the gearbox housing 20 includes the first convex locking section 21d and the second convex locking section 41b, which prevent the helical gear 62 from tilting relative to the gearbox housing 20. Accordingly, the helical gear 62 can be prevented from tilting when a large external force is applied to the output shaft 63, and consequently, damage to the plastic helical gear 62 at an early stage can be prevented, thus extending the service life of the motor deceleration mechanism 10. [Second embodiment]

[0085] The second embodiment of the disclosure is described in detail below with reference to the drawings. It should be noted that sections having similar functions to the first embodiment described above are identified by the same reference numerals, and a detailed description of these sections is omitted.

[0086] Fig. Figure 12 shows a perspective view of the second embodiment (bearing holder).

[0087] As in Fig. As shown in 12, the bearing holder 80 of the second embodiment, in comparison to the bearing holder 40 (see Fig. 3) The difference between the first embodiment and the annular base section 81 is that an annular base section 81 is provided on the circumference of the insertion hole 41d of the holder main body 41 on the side of the convex positioning section 41a. A further difference is that a pair of second convex locking sections (anti-tilt sections) 82 are extended so that they are connected to the annular base section 81.

[0088] The ring-shaped base section 81 is a section that corresponds to the other longitudinal side (lower side in Fig. 1) of the locking element 70 (surrounding wall sections 72) in the assembled state of the motor delay mechanism 10 (see Fig. 1) is facing. Thus, the ring-shaped base section 81 is used similarly to the ring-shaped wall section 73 (see Fig. 7 and Fig. 8) of the locking element 70, also prevents lubricant from running over the annular base section 81 and leaking out of the annular base section 81.

[0089] In the second embodiment, as described above, it is also possible to achieve the same effects as in the first embodiment. Furthermore, in the second embodiment, because the bearing holder 80 is provided with the annular base section 81, lubricant is prevented from reaching the brushless motor 50. Therefore, it is prevented that any lubricant that leaks out could adversely affect the operation of the brushless motor 50. Since the two second convex locking sections 82 are extended to connect with the annular base section 81, it is also possible to prevent the helical gear 62 from tilting. [Third embodiment]

[0090] The third embodiment of the disclosure is described in detail below with reference to the drawings. It should be noted that sections having similar functions to the first embodiment described above are identified by the same reference numerals, and a detailed description of these sections is omitted.

[0091] Fig. Figure 13 shows a perspective view of the third embodiment (safety element).

[0092] As in Fig. 13 shown, in comparison to the locking element 70 of the first embodiment (see Fig. 7 and Fig. 8), the locking element 90 of the third embodiment has the difference that the other annular wall section (first lubricant leakage prevention wall) 91 is located on the other side (corresponding to the right side in Fig. 7 and Fig.8) is provided in the longitudinal direction of the pinion 61. The other annular wall section 91 is also provided with a pinion insertion hole 73a, similar to that of the annular wall section 73. Then the other annular wall section 91 faces the annular wall section 73 in the longitudinal direction of the pair of surrounding wall sections 72.

[0093] In the third embodiment, which is formed as described above, it is also possible to achieve the same effects as in the first embodiment described above. Furthermore, in the third embodiment, since the other annular wall section 91 is provided on the other side (the side of the brushless motor 50) of the locking element 70, lubricant is prevented from reaching the brushless motor 50 as in the second embodiment described above. Therefore, any leaked lubricant can be prevented from negatively affecting the operation of the brushless motor 50.

[0094] It is understood that the disclosure is not limited to the embodiments described above and that various modifications can be made without departing from the spirit of the disclosure. For example, although the embodiments mentioned above illustrate that the motor delay mechanism 10 is used as the drive source for a wiper device mounted on a vehicle, the disclosure is not limited thereto, and the motor delay mechanism 10 can also be used as other drive sources for an electric window lift device, a sunroof device, and the like.

[0095] Although the above embodiments show the motor delay mechanism 10 including the brushless motor 50, the disclosure is not limited thereto, and a motor with a brush can be used as the motor part.

[0096] Furthermore, the material, shape, size, number, installation location and the like of the individual components in each of the above-mentioned embodiments are arbitrary, as long as disclosure can be achieved, and are not limited to each of the above-mentioned embodiments. Reference symbol list

[0097] 10: Motor deceleration mechanism, 11: Housing, 12: First sensor board, 12a: Hall sensor, 13: Second sensor board, 13a: MR sensor, 14: Bearing element, 15: O-ring, 16: Retaining ring, 20: Gearbox housing, 21: Bottom wall section, 21a: Hub section (output shaft support section), 21b: Reinforcing rib, 21c: Bearing element receiving section, 21d: First convex locking section (anti-tilt section), 22: Side wall section, 22a: Locking element receiving section (engagement retaining element support section), 22b: Screw hole, 22c: Housing-side chamfered surface (chamfered surface), 23: Bearing holder mounting section, 23a: Concave bearing holder positioning section, 30: Cover element 31: Circuit board holding section, 31a: Insertion hole, 32: Motor mounting section, 32a: Shaft hole, 40: Bearing holder, 41: Holder main body, 41a: Convex positioning section, 41b: Second convex locking section (anti-tilt section), 41c: Screw hole, 41d: Insertion hole, 42: Support,50: Brushless motor (motor part), 51: Stator core, 51a: Coil, 52: Rotor, 53: Shaft, 54: Rotor body, 60: Deceleration mechanism, 61: Pinion (first gear), 61a: Spiral tooth (tooth), 62: Helical spur gear (second gear), 62a: Gear body, 62b: Gear forming section, 62c: Inclined tooth, 62d: Engagement recess, 63: Output shaft, 70: Locking element (engagement retaining part), 71: Fixed main body section, 71a: Female screw section (fastening section), 71b: Locking element-side chamfered surface (chamfered surface), 72: Surrounding wall section (second lubricant leakage prevention wall), 72a: Chamfered surface, 73: Annular wall section (first lubricant leakage prevention wall), 73a: pinion insertion hole, 80: bearing holder, 81: annular base section, 82: second convex locking section (tilt prevention section), 90: locking element, 91: the other annular wall section (first lubricant leakage prevention wall),BR: Bearing element, BR1: First ball bearing, BR2: Second ball bearing, BS: Base element, CC: Connector connection section, CN: External connector, MG: Permanent magnet, SF1: First surface, SF2: Second surface, SM: Sensor magnet, SP: Space, δS1: Tiny gap, δS2: Tiny gap, δS3: Tiny gap (play), δS4: Tiny gap, δS5: Tiny gap

Claims

[1] Motor delay mechanism (10) comprising: a motor part (50) with a rotating shaft (53); a delay mechanism (60) that delays the rotation of the rotating shaft (53) and includes: a first gear (61) which is provided in such a way that it rotates integrally with the rotating shaft (53); a second gear (62) that meshes with the first gear (61) and rotates at a lower speed than the first gear (61); and an output shaft (63) which is provided in a center of rotation of the second gear (62); and a gear housing (20) which rotatably accommodates the first gear (61) and the second gear (62), wherein a locking element (70) which maintains the engagement between the first gear (61) and the second gear (62) is provided on one side of the first gear (61) opposite one side of the second gear (62) in the gear housing (20), wherein the gear housing (20) comprises: a hub section (21a) that supports the output shaft (63); and a locking element receiving section (22a) that supports the locking element (70), wherein the rotating shaft (53) and the output shaft (63) are provided parallel to each other, the first gear (61) is a pinion with one tooth (61a), and the second gear (62) is a helical gear with inclined teeth (62c) with which the one tooth (61a) meshes, and wherein the locking element (70) is arranged at least in a longitudinal central section of the pinion, wherein the motor deceleration mechanism (10) characterized by is that a fastening section (71a) for fastening the locking element (70) to the gearbox housing (20) is provided in a central section of the locking element (70) in a longitudinal direction of the pinion and that the locking element (70) and the locking element receiving section (22a) each have inclined surfaces (71b, 22c) for positioning the locking element (70) in relation to the locking element receiving section (22a), making it possible to easily carry out the fastening process on the fastening section (71a). [2] Motor delay mechanism (10) according to claim 1, wherein a gap is provided between the first gear (61) and the locking element (70). [3] Motor delay mechanism (10) according to any one of claims 1 to 2, wherein an annular wall section (73, 91) which prevents leakage of a lubricant applied between the pinion and the helical gear is provided on at least one side of the locking element (70) in the longitudinal direction of the pinion. [4] Motor delay mechanism (10) according to any one of claims 1 to 3, wherein a surrounding wall section (72) which prevents leakage of a lubricant applied between the pinion and the helical gear is provided on at least one side of the locking element (70) in a direction of rotation of the helical gear. [5] Motor delay mechanism (10) according to any one of claims 1 to 4, wherein the gearbox housing (20) comprises a tilt prevention section (21d, 41b, 82) which prevents the second gear (62) from tilting in relation to the gearbox housing (20).

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