JP2010014251A - Output transmission device and motor with speed reducing mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an output transmission device and a motor with a speed reducing mechanism capable of suppressing axial rattling between a wheel gear and an output shaft even when they are composed without a cushioning member. <P>SOLUTION: The output transmission device and the motor with the speed reducing mechanism includes a transmission plate 32 used as a transmission member attached to the wheel gear 31 from its axial direction, directly engaging in a rotating direction with the wheel gear 31, and transmitting rotation of the wheel gear 31 to the output shaft 33, and a C-ring 51 provided in a position holding the transmission plate 32 with the wheel gear 31 in the axial direction and used as a regulating part regulating movement to an opposite wheel gear 31 side of the axial direction in the transmission plate 32. An elastic ratchet part 45 used as a pressing means for pressing the transmission plate 32 in the axial direction with respect to the C-ring 51 is formed on the wheel gear 31. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an output transmission device and a motor with a speed reduction mechanism.

2. Description of the Related Art Conventionally, for example, in a power window motor that opens and closes a window glass of an automobile, an output transmission device (decelerator) configured by meshing a worm shaft that rotates by driving the motor body and a wheel gear is integrated with the motor body. It is comprised by the motor with the speed reduction mechanism assembled | attached to (for example, refer patent document 1). Such an output transmission device includes a worm shaft, a wheel gear that meshes with the worm shaft, a transmission member that rotates integrally with the wheel gear, and an output shaft (in Patent Document 1, an intermediate wheel and a pinion). A damper as a buffer member is provided between the wheel gear and the output shaft. The damper is in contact with the wheel gear and the output shaft in the axial direction and the rotational direction of the wheel gear, respectively, and serves to absorb an impact when the rotation is transmitted from the worm shaft to the output shaft. Thereby, damage to components, such as a worm shaft in an output transmission device, is controlled.
Japanese Utility Model Publication No. 6-69493

  By the way, in the output transmission apparatus as described above, by improving the strength of the worm shaft or the like, it is possible to adopt a configuration that does not require a damper, and it is possible to contribute to the suppression of the increase in the number of parts. However, if the damper is eliminated, it is assumed that backlash occurs between the wheel gear and the output shaft in the axial direction of the wheel gear due to dimensional errors, assembly errors, and the like. There was room.

  The present invention has been made to solve the above-described problem, and the object thereof is to suppress the rattling in the axial direction between the wheel gear and the output shaft even if the buffer member is eliminated. An object of the present invention is to provide an output transmission device that can be used.

  In order to solve the above-mentioned problem, the invention according to claim 1 is an output transmission device for transmitting rotation of a rotating shaft having a worm portion on an outer periphery to an output shaft through a wheel gear meshing with the worm portion. A transmission member that is assembled to the wheel gear from its axial direction and directly engages with the wheel gear in the rotational direction, and transmits the rotation of the wheel gear to the output shaft, and the transmission member is the wheel gear. A restricting portion that is provided at a position sandwiched in the axial direction and restricts the movement of the transmission member toward the non-wheel gear side, and presses the transmission member against the wheel gear or the restricting portion in the axial direction. The gist of the present invention is that it includes a pressing means.

  In the present invention, since the transmission member is pressed in the axial direction against either the wheel gear or the restricting portion by the pressing means, there is a dimensional error or an assembly error in the axial direction between the wheel gear and the transmission member. Absorbed. As a result, even if the buffer member is eliminated, the axial play between the wheel gear and the transmission member can be suppressed, and as a result, the axial play between the wheel gear and the output shaft can be suppressed. Suppression can be suppressed.

  According to a second aspect of the present invention, in the output transmission device according to the first aspect, the rotation direction in which one of the wheel gear and the transmission member elastically contacts the other in the rotation direction. The gist is that the pressing means is provided.

  In the present invention, the rotation direction pressing means absorbs a dimensional error, an assembly error, and the like in the rotation direction between the wheel gear and the transmission plate, and suppresses rattling in the rotation direction between the wheel gear and the transmission plate. be able to.

  According to a third aspect of the present invention, in the output transmission device according to the first or second aspect, the pressing unit is formed on one of the wheel gear and the transmission member, and the other is disposed in the axial direction. It is an elastic claw portion to be pressed, and the gist thereof is that the transmission member is configured to be pressed against the restricting portion in the axial direction by an elastic force of the elastic claw portion.

In this invention, the transmission member can be pressed against the restricting portion in the axial direction by the elastic claw portion as the pressing means.
According to a fourth aspect of the present invention, in the output transmission device according to the first or second aspect, the restricting portion constitutes the pressing unit, and the transmission member is connected to the wheel gear with respect to the shaft. The gist is that it is provided in a state of being pressed in the direction.

In the present invention, since the restricting portion also serves as the pressing means, a special configuration as the pressing means is not required, and the configuration can be simplified.
According to a fifth aspect of the present invention, in the output transmission device according to the fourth aspect, the wheel gear is provided with an inclined portion that is inclined in a rotation direction thereof, and the transmission member is provided by the restricting portion. The gist of the present invention is that it is configured to be pressed against the inclined portion in the axial direction.

  In this invention, the axial pressing force by the restricting portion is also distributed in the rotational direction, whereby the transmission member is pressed against the wheel gear in the rotational direction. For this reason, it is possible to suppress not only the axial direction but also the shaking in the rotational direction with a simple configuration.

A sixth aspect of the present invention is a motor with a speed reduction mechanism configured to be able to output the rotation of the rotation shaft of the motor body by the output transmission device according to any one of the first to fifth aspects.
According to the present invention, it is possible to provide a motor with a speed reduction mechanism in which backlash in the axial direction between the wheel gear and the output shaft is suppressed.

  Therefore, according to the above-described invention, even if the buffer member is omitted, it is possible to suppress the backlash in the axial direction between the wheel gear and the output shaft.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
A motor 1 according to this embodiment shown in FIG. 1 is a motor for a power window that opens and closes a window glass of an automobile, and includes a motor with a speed reducer that includes a motor main body 2 and a speed reduction unit 3 as an output transmission device. Has been.

  The motor body 2 includes a yoke housing 4, a pair of magnets 5, an armature 6, a brush holder 7, and a pair of brushes 8. The yoke housing 4 is formed in a substantially bottomed flat cylindrical shape, and a magnet 5 is fixed to the inner surface thereof. A bearing 9 is provided at the center of the bottom of the yoke housing 4, and the bearing 9 rotatably supports the base end of the rotating shaft 10 of the armature 6.

  The opening 4a of the yoke housing 4 is formed in a flange shape, and is fixed to the opening 21a of the gear housing 21 described later with screws 11. In this fixing, the brush holder 7 is sandwiched and fixed by the opening 4 a of the yoke housing 4 and the opening 21 a of the gear housing 21.

  The brush holder 7 holds, in the yoke housing 4, a brush 12 that is in sliding contact with a commutator 13 that is fixed to the bearing 12 and the rotating shaft 10 that rotatably supports the tip of the rotating shaft 10 of the armature 6. Further, the portion of the brush holder 7 that protrudes from both housings 4 and 21 is a connector portion 7a for connecting to a vehicle body side connector (not shown) extending from the vehicle body side, and a plurality of portions are provided in the recess 7b of the connector portion 7a. The terminal 14 is exposed. These terminals 14 are inserted into the brush holder 7 and are electrically connected to the brush 8 and the rotation sensor 15 provided in the motor 1. And by connecting the connector part 7a with the vehicle body side connector, the motor 1 and the window ECU 16 provided on the vehicle body side are electrically connected, and power supply, output of sensor signals and the like are performed.

  For such a motor body 2, the speed reduction unit 3 includes a gear housing 21, a worm shaft 22, an output member 23, and a brake mechanism 24. The output member 23 outputs the rotation of the worm shaft 22 to the outside, and includes a wheel gear 31, a transmission plate 32 as a transmission member, and an output shaft 33 (see FIG. 2).

  The gear housing 21 is made of resin, and a worm shaft 22, a wheel gear 31, a transmission plate 32, and a brake mechanism 24 are accommodated in the gear housing 21. The gear housing 21 includes an opening 21a that faces the opening 4a of the yoke housing 4, and the brush holder 7 is interposed between the openings 4a and 21a.

  The gear housing 21 includes a substantially cylindrical shaft housing cylinder portion 21b extending from the opening 21a in the axial direction of the worm shaft 22 for housing the worm shaft 22, and a wheel gear 31 communicating with the shaft housing cylinder portion 21b. A wheel housing recess 21 c for housing and a brake housing recess 21 d for housing the brake mechanism 24 provided at the base end (motor body 2 side) of the shaft housing tube portion 21 b are provided.

  A worm shaft 22 is rotatably supported coaxially with the rotary shaft 10 by a pair of bearings 25a and 25b having a predetermined interval and accommodated in the shaft accommodating cylinder portion 21b. A worm 22a (worm portion) for meshing with the wheel gear 31 is formed between portions of the worm shaft 22 supported by the bearings 25a and 25b. The worm 22a is constituted by a drum-type worm that follows the outer peripheral portion having the tooth portion 23a of the wheel gear 31 having a smaller diameter in the central portion in the axial direction than both end portions in the axial direction. That is, the meshing range between the worm 22a and the wheel gear 31 is increased, and the strength of this meshing portion is improved. A thrust receiving ball 26 a and a thrust receiving plate 26 b for receiving a thrust load of the worm shaft 22 are provided at the tip of the worm shaft 22.

  A brake mechanism 24 interposed between the rotating shaft 10 of the motor body 2 and the worm shaft 22 is housed in the brake housing recess 21d. The brake mechanism 24 transmits the rotational force to the worm shaft 22 when the rotary shaft 10 is rotated by driving the motor body 2. On the other hand, when the rotational force from the output member 23 side is input via the worm shaft 22, the brake mechanism 24 is controlled. It operates so that power is generated and its rotation is restricted.

  As shown in FIG. 2B, a cylindrical support portion 21e extending in the axial direction of the wheel gear 31 (left and right direction in the figure) is formed at the central portion of the wheel receiving recess 21c. The cylindrical support portion 21e is inserted into the insertion hole 41 of the wheel gear 31, and rotatably supports the wheel gear 31. The cylindrical support portion 21e is provided with a bearing 27. The bearing 27 supports the output shaft 33 in a rotatable manner.

  The wheel gear 31 is made of resin, and as shown in FIGS. 3A, 3B, and 3C, a gear portion 42 that meshes with the worm 22a of the worm shaft 22 is formed on the outer peripheral portion, and at the center portion. The insertion hole 41 is formed. Further, on one end surface of the wheel gear 31 in the axial direction (end surface on the side shown in FIG. 2 (a)), nine engagement grooves 43 are arranged at equal intervals in the circumferential direction between the insertion hole 41 and the gear portion. Is formed. Each engaging groove 43 extends in the radial direction, and both side surfaces in the circumferential direction are parallel to each other. Three of the nine engaging grooves 43 positioned at equal intervals in the circumferential direction are formed with through holes 44 penetrating in the axial direction. Each through hole 44 is formed with an elastic claw portion 45 as a pressing means extending from the outer peripheral side end portion to the inner peripheral side, and each elastic claw portion 45 is allowed to bend in the axial direction. Yes. A protruding portion 46 that protrudes in the axial direction of the wheel gear 31 is formed at the inner peripheral side end portion of each elastic claw portion 45.

  On the other hand, as shown in FIG. 2 (b), the output shaft 33 pivotally supported by the bearing 27 has a front end protruding outside the gear housing 21, and a window glass is opened and closed near the front end. A connecting portion 33a that is drivingly connected to a window regulator (not shown) is formed. The connecting portion 33a is in axial contact with the outer surface of the gear housing 21 (wheel accommodating recess 21c). The base end portion of the output shaft 33 is located in the gear housing 21 (the wheel accommodating recess 21 c), and the base plate includes a transmission plate that constitutes the output member 23 together with the output shaft 33 and the wheel gear 31. A plate mounting portion 33b for mounting 32 is formed. The plate mounting portion 33b has a cross shape when viewed from the axial direction (see FIG. 2A).

  The transmission plate 32 is made of metal, and as shown in FIGS. 4A, 4B, and 4C, a cylindrical portion 32a into which the plate mounting portion 33b of the output shaft 33 is inserted is formed at the center thereof. ing. The cylindrical portion 32a has a cross shape corresponding to the plate mounting portion 33b, and is engaged with the plate mounting portion 33b in the rotation direction. Thereby, the transmission plate 32 and the output shaft 33 can rotate integrally. A C ring 51 as a restricting portion is fixed to the proximal end portion of the output shaft 33. The C-ring 51 is in contact with the transmission plate 32 in the axial direction, and functions as a stopper from the proximal end side of the output shaft 33 in the transmission plate 32.

  The transmission plate 32 is formed with an intermediate portion 32b that is curved from one end portion in the axial direction of the cylindrical portion 32a and extends to the outer peripheral side. Nine engaging pieces 32c extending radially outward are formed in the intermediate portion 32b at equal intervals in the circumferential direction, and the engaging pieces 32c are fitted in the engaging grooves 43 of the wheel gear 31. Has been. Thereby, each engagement groove | channel 43 and each engagement piece 32c engage in a rotation direction, and the wheel gear 31 and the transmission plate 32 can rotate integrally. That is, the wheel gear 31, the transmission plate 32, and the output shaft 33 constituting the output member 23 are coaxially and integrally rotated. The wheel housing recess 21c that houses the output member 23 is closed at the opening portion by the cover member 52, and a base end portion (plate mounting portion 33b) of the output shaft 33 at a part of the cover member 52. Is supported.

  In such an output member 23, three of the engagement pieces 32 c of the transmission plate 32 are in elastic contact with the protruding portions 46 of the elastic claw portions 45 of the wheel gear 31 in the axial direction. That is, the transmission plate 32 is urged toward the base end side of the output shaft 33, and the cylindrical portion 32 a of the transmission plate 32 is pressed against the C ring 51. Due to the pressing of the elastic claw portion 45 against the transmission plate 32, the dimensional error and the assembly error in the axial direction between the wheel gear 31 and the transmission plate 32 are absorbed, and the shaft between the wheel gear 31 and the transmission plate 32 is absorbed. The play in the direction is prevented.

  Further, when the output member 23 is assembled as described above, the transmission gear 32 is assembled from the axial direction after the wheel gear 31 and the output shaft 33 are assembled to the wheel receiving recess 21c. At that time, each engagement piece 32 c of the transmission plate 32 is press-fitted into each engagement groove 43 of the wheel gear 31. Here, as shown in FIG. 5, press-fitting protrusions 43 a as rotation direction pressing means are formed on both sides in the rotation direction of each engagement groove 43, and the engagement piece 32 c is formed in the engagement groove 43. Each of the press-fitting protrusions 43a is crushed by being pushed. Accordingly, the press-fitting protrusion 43a is elastically pressed against the engagement piece 32c in the rotation direction. Therefore, a dimensional error and an assembly error in the rotation direction between the wheel gear 31 and the transmission plate 32 are absorbed, and rattling in the rotation direction between the wheel gear 31 and the transmission plate 32 is prevented. ing.

  In the motor 1 as described above, when the rotating shaft 10 is rotated by driving the motor body 2, the brake mechanism 24 and the worm shaft 22 are rotated, and the rotation of the worm shaft 22 is transmitted to the wheel gear 31, and the wheel The gear 31, the transmission plate 32, and the output shaft 33 rotate integrally. At this time, backlash in the axial direction and the rotational direction between the wheel gear 31 and the transmission plate 32 is suppressed, and the rotation of the worm shaft 22 is smoothly transmitted to the output shaft 33. Further, in the motor 1 of the present embodiment, the worm shaft 22 is constituted by a drum-type worm that can increase the number of meshes with the wheel gear 31, and therefore, between the wheel gear 31 and the transmission plate 32 in the rotation direction. Even if a cushioning member such as rubber is not provided, damage to the worm shaft 22 and the wheel gear 31 can be suppressed.

Next, characteristic effects of the present embodiment will be described.
(1) In this embodiment, the wheel gear 31 is assembled from the axial direction and directly engaged with the wheel gear 31 in the rotational direction, and serves as a transmission member that transmits the rotation of the wheel gear 31 to the output shaft 33. A C-ring 51 is provided at a position where the transmission plate 32 and the wheel gear 31 sandwich the transmission plate 32 in the axial direction, and restricts movement of the transmission plate 32 in the axial direction to the opposite wheel gear 31 side. Prepare. The wheel gear 31 is formed with an elastic claw portion 45 as pressing means for pressing the transmission plate 32 against the C ring 51 in the axial direction. As a result, the transmission plate 32 is pressed in the axial direction against the C-ring 51 by the elastic claw portion 45, so that dimensional errors and assembly errors in the axial direction between the wheel gear 31 and the transmission plate 32 are absorbed. The Therefore, even if the buffer member is omitted, it is possible to suppress backlash in the axial direction between the wheel gear 31 and the transmission plate 32, and thus the shaft between the wheel gear 31 and the output shaft 33. The play of the direction can be suppressed.

  (2) In the present embodiment, the engagement groove 43 of the wheel gear 31 is formed with a press-fit protrusion 43a (rotation direction pressing means) that elastically presses the engagement piece 32c of the transmission plate 32 in the rotation direction. Is done. Therefore, dimensional errors and assembly errors in the rotational direction between the wheel gear 31 and the transmission plate 32 are absorbed, and rattling in the rotational direction between the wheel gear 31 and the transmission plate 32 can be suppressed.

  (3) In the present embodiment, the wheel gear 31 is formed with the elastic claw portion 45 that presses the engagement piece 32c of the transmission plate 32 in the axial direction. 51 can be pressed in the axial direction.

In addition, you may change embodiment of this invention as follows.
In the above embodiment, the elastic claw portion 45 is formed on the wheel gear 31, but is not particularly limited to this, and for example, the elastic claw portion 45 as shown in FIGS. 6A and 6B is not provided. It is good also as a structure. As shown in FIGS. 6 (a) and 6 (b), each engaging groove 61 of the wheel gear 31 has inclined portions 62 whose both sides in the rotation direction are inclined in the rotation direction. Has a tapered shape that expands toward the opening direction (upward in FIG. 6B). Each engaging piece 32c of the transmission plate 32 is in contact with the inclined portion 62 of each engaging groove 61 at both sides in the rotational direction.

  The C ring 51 as a restricting portion is fixed to the base end portion (plate mounting portion 33b) of the output shaft 33 in a state where the transmission plate 32 is pressed against the wheel gear 31 in the axial direction. Each engagement piece 32 c is pressed in the axial direction against the inclined portion 62 of each engagement groove 61 of the wheel gear 31. Thereby, the pressing force in the axial direction with respect to the inclined portion 62 is dispersed also in the rotation direction, and each engagement piece 32c applies the pressing force not only in the axial direction but also in the rotation direction to each engagement groove 61. It is like that.

  According to such a configuration, the C ring 51 also serves as a pressing unit that presses the transmission plate 32 against the wheel gear 31. The pressing force from the C-ring 51 absorbs dimensional errors and assembly errors in the axial direction and rotational direction between the wheel gear 31 and the transmission plate 32, and the wheel gear 31 and the transmission plate 32 in each direction. The backlash between the two is prevented. Moreover, according to such a structure, since the C-ring 51 as the restricting portion also serves as the pressing unit, a special configuration as the pressing unit is not required, and the configuration can be simplified.

  6 (a) and 6 (b), the engagement piece 32c of the transmission plate 32 may be changed to a shape as shown in FIGS. 7 (a) and 7 (b), for example. 7 (a) is formed with elastic portions 32d (rotational direction pressing means) extending from both ends in the rotational direction toward the wheel gear 31, and each elastic portion 32d has an engagement groove 61. Each inclined portion 62 is elastically contacted. Further, the engaging piece 32c of FIG. 7B is formed with elastic portions 32e (rotating direction pressing means) extending from both ends in the rotating direction toward the counter wheel gear 31, respectively. The cross section 32c is substantially U-shaped. The elastic portions 32 d and 32 e are in elastic contact with the inclined portions 62 of the engagement groove 61. According to such a structure, since each elastic part 32d and 32e contact | abuts each inclination part 62 elastically, it can exhibit the rattle prevention effect stably.

  In the above-described embodiment, the press-fitting protrusion 43a is formed as the rotation direction pressing means. However, the present invention is not particularly limited to this, and an elastic portion 63 as the rotation direction pressing means is shown in FIGS. It is good also as such a structure.

  8 (a) and 8 (b), a pair of elastic portions 63 facing each other in the rotational direction are formed on the bottom 43b of the engaging groove 43 so as to project between the elastic portions 63. The engagement piece 32c of the plate 32 is fitted. Thereby, the engagement piece 32c is elastically clamped by each elastic part 63.

  9 (a) and 9 (b), an elastic portion 63 is formed at the distal end of the engagement piece 32c of the transmission plate 32. The elastic portion 63 extends once in the rotational direction and is then bent toward the wheel gear 31. The elastic portion 63 is fixed to a groove-shaped fixing portion 43 c formed on the bottom portion 43 b of the engaging groove 43.

  According to the configuration shown in FIGS. 8 and 9, dimensional errors and assembly errors in the axial direction and rotational direction between the wheel gear 31 and the transmission plate 32 are absorbed, and transmission with the wheel gear 31 in each direction is absorbed. Backlash between the plate 32 and the plate 32 is prevented. In addition, since the elastic portion 63 elastically contacts the engagement piece 32c, the rattling prevention effect can be stably exhibited.

Further, in the structure shown in FIG. 10, an elastic portion 63 is formed to extend on one side surface of the engaging groove 43 in the rotational direction, and the elastic portion 63 is in elastic contact with the engaging piece 32c in the rotational direction. Yes.
In the structure shown in FIG. 11A, the engaging groove 43 is formed so as to become narrower toward the outer peripheral side, and the engaging piece 32c has an elastic portion that extends from the front end thereof in an inclined manner to both sides in the rotational direction. 63 is formed. Each elastic portion 63 elastically presses the engagement groove 43 in the rotation direction. Further, in the structure shown in FIG. 11 (b), an elastic portion 63 that is inclined from the tip to one side in the rotation direction is formed, and the elastic portion 63 elastically presses the engagement groove 43 in the rotation direction. .

  10 and 11 (a) and 11 (b), the dimensional error and assembly error in the rotational direction between the wheel gear 31 and the transmission plate 32 are absorbed, and the wheel gear in the rotational direction is absorbed. The backlash between 31 and the transmission plate 32 is prevented. In addition, since the elastic portion 63 elastically contacts the engagement groove 43, the rattling prevention effect can be stably exhibited.

  In each of the above embodiments, the engaging piece 32c and the engaging groove 43 are configured such that both sides in the rotational direction are parallel to each other. However, for example, as shown in FIG. You may comprise so that it may become narrow toward this. According to such a configuration, rattling in the radial direction and the rotational direction between the wheel gear 31 and the transmission plate 32 can be suppressed.

In the above embodiment, nine engaging grooves 43 and nine engaging pieces 32c are provided. However, the number of engaging grooves 43 and the engaging pieces 32c is not particularly limited thereto, and may be eight or less, or ten or more.
In the above embodiment, the elastic claw portion 45 is formed on the wheel gear 31 side, but may be formed on the transmission plate 32 side. Further, instead of the elastic claw portion 45, for example, a sheet-like rubber member as a separate member may be interposed between the wheel gear 31 and the transmission plate 32 in the axial direction.

  -In above-mentioned embodiment, although the transmission plate 32 and the output shaft 33 were comprised as a different body, you may comprise integrally.

Sectional drawing of the motor of this embodiment. (A) The front view which shows an output member, (b) Sectional drawing of a deceleration part. (A) Front view which shows wheel gear, (b) AA sectional view taken on the line in (a), (c) Rear view. (A) Front view which shows a transmission plate, (b) BB sectional drawing in the same figure (a), (c) Rear view. The front view which shows an engaging groove and an engaging piece. The output member of another example is shown (a) front view, (b) sectional drawing. (A) (b) Sectional drawing for demonstrating the elastic part of another example, respectively. The (a) front view which shows the elastic part of another example, (b) sectional drawing. The (a) front view which shows the elastic part of another example, (b) sectional drawing. The front view which shows the elastic part of another example. (A) (b) The front view for demonstrating the elastic part of another example, respectively. The front view which shows the engaging groove and engaging piece of another example.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Motor main body, 10 ... Rotating shaft, 22 ... Worm shaft, 22a ... Worm (worm part), 31 ... Wheel gear, 32 ... Transmission plate as a transmission member, 32c ... Engagement piece, 33 ... Output shaft, 43 ... Engaging groove, 43a ... press-fitting protrusion as rotation direction pressing means, 45 ... elastic claw portion as pressing means, 51 ... C-ring as restriction portion, 62 ... inclined portion, 63 ... elastic portion as rotation direction pressing means .

Claims (6)

In the output transmission device that transmits the rotation of the rotating shaft having the worm portion on the outer periphery to the output shaft through the wheel gear meshing with the worm portion,
A transmission member that is assembled to the wheel gear from its axial direction and directly engages with the wheel gear in the rotational direction, and transmits the rotation of the wheel gear to the output shaft;
A restricting portion that is provided at a position sandwiching the transmission member with the wheel gear in the axial direction, and restricts movement of the transmission member toward the non-wheel gear;
An output transmission device comprising: a pressing unit that presses the transmission member in the axial direction against one of the wheel gear and the restricting portion. The output transmission device according to claim 1,
One of the wheel gear and the transmission member is provided with a rotation direction pressing means that elastically contacts with the other in the rotation direction. The output transmission device according to claim 1 or 2,
The pressing means is an elastic claw portion that is formed on one of the wheel gear and the transmission member and presses the other in the axial direction.
The output transmission device, wherein the transmission member is configured to be pressed in the axial direction against the restricting portion by an elastic force of the elastic claw portion. The output transmission device according to claim 1 or 2,
The output part according to claim 1, wherein the restricting part constitutes the pressing means and is provided in a state in which the transmitting member is pressed against the wheel gear in the axial direction. The output transmission device according to claim 4, wherein
The wheel gear is provided with an inclined portion that is inclined in the rotational direction thereof,
The output transmission device, wherein the transmission member is configured to be pressed in the axial direction against the inclined portion of the wheel gear by the restricting portion.   A motor with a speed reduction mechanism configured to be able to output the rotation of the rotation shaft of the motor body by the output transmission device according to any one of claims 1 to 5.

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