JP6793556B2 - Motor with reduction mechanism - Google Patents

Description

The present invention relates to a motor with a reduction mechanism that decelerates and outputs the rotation of a rotating shaft.

Conventionally, some vehicles such as automobiles are equipped with an electric sunroof device, an electric sunshade device, and the like. As a drive source for an electric sunroof device, an electric sunshade device, or the like, a motor with a reduction mechanism capable of mounting a small space in a narrow space on the ceiling but capable of a large output is adopted. A worm deceleration mechanism that can obtain a relatively large reduction ratio is adopted as the deceleration mechanism of such a motor with a deceleration mechanism for vehicles.

Further reduction in size and weight is desired for an in-vehicle motor with a reduction mechanism. Therefore, for example, it is conceivable that the gear rotated by the worm is made of resin and the shaft to which the gear is fixed is made of steel. As a result, it is possible to reduce the weight of the gear having a large volume, and thus to reduce the weight of the entire motor with a reduction mechanism. On the other hand, if the gear and the shaft are made of different materials, it becomes difficult to firmly fix them so that they cannot rotate relative to each other.

In order to firmly fix the separate gears and shafts to each other, for example, a fixing method using "key grooves and keys" described in Patent Document 1 can be mentioned. Further, in addition to the fixing method using "key grooves and keys", a method of fixing a gear and a shaft made of another material by "insert molding" can be mentioned. The latter fixing method by "insert molding" requires large-scale equipment such as a plurality of molds and a dispenser for supplying molten resin, and an increase in cost is unavoidable. Therefore, in terms of cost, the former "keyway and key" fixing method is more advantageous.

JP-A-2007-139164

However, if the fixing method described in Patent Document 1 described above is to be applied as it is to fixing a resin gear and a steel shaft, it is made of resin due to a large rotational force transmitted between the gear and the shaft. Gear may be deformed. In particular, stress is concentrated on the key portion (one location) that receives the rotational force inside the gear in the radial direction, and that portion is easily deformed. When the gear is deformed, the rattling between the gear and the shaft becomes large, and the operating noise (mechanical noise) of the motor with the reduction mechanism becomes large.

When a motor with a reduction mechanism is used as a drive source for an electric sunroof device, an electric sunshade device, or the like, the motor with a reduction mechanism is arranged above the head of a driver or an occupant. Therefore, when a motor with a reduction mechanism is used as a drive source for an electric sunroof device, an electric sunshade device, or the like, it is necessary to suppress the generation of operating noise.

An object of the present invention is to provide a motor with a reduction mechanism capable of improving quietness while suppressing cost increase as well as further reducing the size and weight.

In one aspect of the present invention, a motor with a reduction mechanism that decelerates and outputs the rotation of the rotating shaft, wherein the worm rotated by the rotating shaft, a resin gear meshed with the worm, and the gear are It has a driven shaft made of steel to be fixed and a gear fixing mechanism provided between the gear and the driven shaft, and the gear fixing mechanism is provided on the driven shaft in the radial direction of the driven shaft. A protruding member protruding outward and a protruding engaging portion with which the protruding member is engaged are provided radially inside, and a gear engaging portion with which the axial end of the gear is engaged is radially outward. A steel plate member provided is provided , and the gear engaging portion is an engaging convex portion protruding outward in the radial direction of the plate member, and the engaging convex portion is formed on an axial end portion of the gear. A recessed portion into which the portion is inserted is provided, the protrusion engaging portion and the engaging convex portion are provided at the same positions in the circumferential direction of the plate member, and the tip portion of the engaging convex portion is the tooth of the gear. that extends up to the part.

In another aspect of the present invention, a key groove is provided on the radial outer side of the driven shaft, the protrusion member is a key mounted on the key groove, and the protrusion engaging portion is engaged with the key. It is said to be a joint recess.

In another aspect of the present invention, a plurality of the key grooves are provided at equal intervals in the circumferential direction of the driven shaft, and a plurality of engaging recesses are provided at equal intervals in the circumferential direction of the plate member.

In another aspect of the present invention, a plurality of the engaging convex portions are provided at equal intervals in the circumferential direction of the plate member, and a plurality of the recessed portions are provided at equal intervals in the circumferential direction of the gear.

In another aspect of the present invention, the gear fixing mechanism is provided on both sides of the gear in the axial direction.

In another aspect of the present invention, an output shaft rotated by the driven shaft is provided, and the output shaft opens and closes and drives an opening and closing body provided on the ceiling of the vehicle.

According to the present invention, the gear has a gear made of resin, a driven shaft made of steel, and a gear fixing mechanism between the gear and the driven shaft. The gear fixing mechanism is provided on the driven shaft and is provided on the driven shaft. A protrusion member protruding outward in the radial direction and a protrusion engagement portion with which the protrusion member is engaged are provided inside in the radial direction, and a gear engagement portion with which the axial end portion of the gear is engaged is provided outside in the radial direction. It is provided with a steel plate member to be provided.

As a result, the resin gear can be fixed to the steel plate member. Since the engagement portion between the plate member and the gear can be arranged radially outside as compared with the conventional one in which the radial inside of the gear and the key are directly engaged, the engagement portion between the plate member and the gear can be arranged. Rigidity can be increased. That is, the deformation of the gear is suppressed by preventing the stress from being locally concentrated on the inside in the radial direction of the gear. Therefore, by using the resin gear, it is possible to further reduce the size and weight of the motor with the reduction mechanism, and it is possible to improve the quietness while suppressing the cost increase.

It is a schematic diagram which shows the outline of the electric sunshade device mounted on the roof of a vehicle. It is a perspective view of the motor with a reduction mechanism used for the electric sunshade device of FIG. It is a top view of the motor with a reduction mechanism of FIG. It is a view of arrow A of FIG. It is a B arrow view of FIG. It is sectional drawing which follows the CC line of FIG. It is sectional drawing which follows the DD line of FIG. It is a perspective view which shows only the drive system of the motor with a reduction mechanism. It is a perspective view which shows the engagement state with respect to the mounting bracket of the 2nd flange part. It is a perspective view which shows the mounting procedure (the 1) of the 1st helical gear. It is a perspective view which shows the mounting procedure (the 2) of the 1st helical gear. It is a perspective view which shows the relief part provided in the gear case.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a schematic view showing an outline of an electric sunshade device mounted on the roof of a vehicle, FIG. 2 is a perspective view of a motor with a reduction mechanism used in the electric sunshade device of FIG. 1, and FIG. 3 is a reduction mechanism of FIG. A plan view of the attached motor, FIG. 4 is a view taken along the line A of FIG. 3, FIG. 5 is a view taken along the line B of FIG. 3, FIG. 6 is a sectional view taken along the line CC of FIG. A cross-sectional view taken along the line DD of FIG. 3, FIG. 8 is a perspective view showing only the drive system of the motor with a reduction mechanism, and FIG. 9 is a perspective view showing the engagement state of the second flange portion with the mounting bracket. FIG. 10 is a perspective view showing a first helical gear mounting procedure (No. 1), FIG. 11 is a perspective view showing a first helical gear mounting procedure (No. 2), and FIG. 12 is a perspective view showing a relief portion provided in the gear case. The figures are shown respectively.

The electric sunshade device 10 shown in FIG. 1 is provided on the vehicle interior side of a glass roof (not shown) provided on the vehicle roof (ceiling), and functions as a shade that softens the passage of sunlight into the vehicle interior. .. The electric sunshade device 10 includes a pair of guide rails 11 fixed to the roof of the vehicle, a sunshade 12 (shaded portion in the figure) as an opening / closing body moved in the longitudinal direction of the guide rails 11, and a front side of the guide rails 11. It is provided with a drive mechanism 13 arranged (on the right side in the drawing).

The pair of guide rails 11 are arranged in parallel so as to be spaced apart from each other, and sliding grooves 11a (only one side is shown) are provided on the surfaces facing each other. Sliding members 12a (shown only on one side) provided on both sides of the sunshade 12 in the width direction enter into these sliding grooves 11a and slide. Here, the sunshade 12 is formed in a sheet shape by a cloth or the like, is moved to the rear side (left side in the drawing) of the guide rail 11 to be in the "open state", and is moved to the front side of the guide rail 11 to be in the "closed state". It becomes. That is, the state shown in FIG. 1 indicates that the electric sunshade device 10 is in the “open state”.

The drive mechanism 13 includes a motor 20 with a reduction mechanism arranged between the pair of guide rails 11, and first and second connecting portions 72, 73 (one end of which is provided on the output shaft 70 of the motor 20 with a reduction mechanism). (See FIG. 7), the other end is provided in a pair of drive shafts 14 arranged in the sliding groove 11a and the sliding groove 11a, and the sliding member 12a is moved by the rotation of the drive shaft 14. It includes a drive chain 15 (shown on only one side). Then, the drive shaft 14 is rotated in the forward and reverse directions by operating the operation switch (not shown) in the vehicle interior to rotate the motor 20 with the reduction mechanism in the forward and reverse directions. As a result, the drive chain 15 is driven and the sliding member 12a (sunshade 12) is moved in the front-rear direction. That is, the output shaft 70 of the motor 20 with a reduction mechanism opens and closes the sunshade 12.

As shown in FIGS. 2 and 3, the motor 20 with a reduction mechanism includes a motor unit 30 and a gear unit 40.

The motor unit 30 includes a yoke 31 formed in a bottomed tubular shape by pressing a steel plate or the like. Specifically, as shown in FIG. 5, the yoke 31 includes a pair of arcuate portions 31a curved around the axis of the yoke 31, and a pair of flat plates connected to these arcuate portions 31a and parallel to each other. A portion 31b and a stepped bottom portion 31c are provided. As a result, the cross-sectional shape along the direction intersecting the axial direction of the yoke 31 is formed into a substantially oval shape.

Further, a yoke flange 31d that bulges outward in the radial direction is provided on a portion of the yoke 31 that is opposite to the bottom portion 31c side along the axial direction and that corresponds to the pair of arc portions 31a. The pair of yoke flanges 31d are fixed to the yoke fixing portion 42a (see FIG. 2) of the gear case 41 by a pair of fixing screws S1. That is, the motor portion 30 and the gear portion 40 are firmly connected to each other by a pair of fixing screws S1.

Four permanent magnets 32 as shown in FIG. 8 are mounted on the inside of the yoke 31 in the radial direction. The cross-sectional shape of these permanent magnets 32 is formed in a substantially arc shape, and the armature 33 is rotatably housed inside each of the permanent magnets 32 in the radial direction through a predetermined gap.

An armature shaft (rotation shaft) 34 is provided at the center of rotation of the armature 33. One side of the armature shaft 34 in the axial direction (right side in FIG. 8) is rotatably supported by a first radial bearing B1 mounted on the bottom portion 31c of the yoke 31. As a result, the armature 33 is rotatable inside the yoke 31 in the radial direction. A plain bearing called a so-called "metal bearing" is used for the first radial bearing B1.

Around the armature shaft 34, an armature core 35 formed by laminating a plurality of steel plates is fixed. The armature core 35 is provided with a plurality of slots (for example, 10) (not shown), and a plurality of coils 36 (not shown in detail) are wound in these slots in a predetermined winding method and number of windings. ..

Further, a commutator 37 having a plurality of segments 37a is fixed to the armature shaft 34 so as to be adjacent to the armature core 35. The coil ends (not shown) of the plurality of coils 36 are electrically connected to the plurality of segments 37a.

Further, a plurality of brushes (not shown) are in sliding contact with the periphery of the commutator 37. Then, a drive current is supplied to each coil 36 at a predetermined timing via the plurality of brushes and commitators 37. As a result, an electromagnetic force is generated in the armature 33, and the armature 33 is rotated in a predetermined rotation direction at a predetermined rotation speed.

As described above, the motor unit 30 in the present embodiment employs an electric motor with a brush. However, as the motor unit 30, a brushless electric motor can be adopted instead of the brushed electric motor.

As shown in FIGS. 2 to 7, the gear portion 40 includes a gear case 41 formed in a hollow substantially box shape by injection molding a resin material such as plastic. The gear case 41 includes a ceiling wall portion 41a, a bottom wall portion 41b, and a side wall portion 41c. The gear case 41 is provided with a worm shaft accommodating portion 42, an intermediate shaft accommodating portion 43, and an output shaft accommodating portion 44 so as to be surrounded by the ceiling wall portion 41a, the bottom wall portion 41b, and the side wall portion 41c. There is.

A worm shaft 50 (see FIG. 8) is rotatably housed inside the worm shaft housing portion 42, and a yoke fixing portion 42a is provided on the yoke 31 side along the longitudinal direction thereof. A pair of yoke flanges 31d provided on the yoke 31 are firmly fixed to the yoke fixing portion 42a by a pair of fixing screws S1. That is, the opening portion (not shown) of the worm shaft accommodating portion 42 is closed by the yoke 31.

The intermediate shaft accommodating portion 43 is arranged on the side opposite to the yoke 31 side along the longitudinal direction of the worm shaft accommodating portion 42, and the intermediate shaft 60 (see FIG. 8) is rotatably accommodated therein. As shown in FIG. 6, the intermediate shaft accommodating portion 43 extends in a direction intersecting the extending direction of the worm shaft 50, that is, in a lateral direction intersecting the longitudinal direction of the motor 20 with a reduction mechanism. A first opening 43a is formed on one side of the intermediate shaft accommodating portion 43 in the longitudinal direction (right side in FIG. 6), and the first opening 43a is closed by a first cover member 43b made of a steel material. .. Here, the first cover member 43b is formed in a substantially square shape, and its four corners are firmly fixed to the gear case 41 by four fixing screws S2 (see FIG. 2).

A relatively large reaction force acts from the output shaft 70 in the axial direction of the intermediate shaft 60. Therefore, the first cover member 43b is made of steel to sufficiently secure the fixing strength of the intermediate shaft 60 in the axial direction. As a result, it is possible to reliably prevent the intermediate shaft 60 from being moved in the axial direction, and thus reduce the operating noise (mechanical noise) of the motor 20 with the reduction mechanism. Since the electric sunshade device 10 is arranged above the driver or occupant's head, improvement of quietness is one of the important problems to be solved, especially when it is used in a hybrid vehicle or an electric vehicle having a quiet interior. It has become one.

The output shaft accommodating portion 44 is arranged on the side opposite to the first cover member 43b side along the lateral direction of the motor 20 with a reduction mechanism, and the output shaft 70 (see FIG. 8) is rotatably accommodated therein. Has been done. As shown in FIG. 7, the output shaft accommodating portion 44 extends in the extending direction of the armature shaft 34 (worm shaft 50). A second opening 44a is formed on one side of the output shaft accommodating portion 44 in the longitudinal direction (right side in FIG. 7), and the second opening 44a is closed by a second cover member 44b made of a resin material. There is. Here, the second cover member 44b is formed in a substantially square shape, and its four corners are firmly fixed to the gear case 41 by four fixing screws S3 (see FIG. 2).

Since the drive shaft 14 (see FIG. 1) is connected to both sides of the output shaft 70 in the axial direction via the first and second connecting portions 72 and 73, the output shaft 70 is connected to the intermediate shaft 60. As such, a large reaction force does not act in the axial direction. Therefore, the second cover member 44b does not need as much rigidity as the first cover member 43b. Therefore, the second cover member 44b is made of resin in order to give priority to weight reduction of the motor 20 with a reduction mechanism.

As shown in FIGS. 2 and 3, the worm shaft accommodating the worm shaft accommodating portion 42 side along the lateral direction (vertical direction in the figure) of the gear case 41 and along the longitudinal direction (horizontal direction in the figure) of the gear case 41. A first mount fixing portion 45 is integrally provided on the side of the portion 42 opposite to the yoke fixing portion 42a side. The first mount fixing portion 45 projects from the worm shaft accommodating portion 42 along the longitudinal direction of the gear case 41 to the side opposite to the yoke fixing portion 42a side, and the yoke 31 along the longitudinal direction of the motor 20 with a reduction mechanism. It is located at the end opposite to the side.

A first mount 45a made of an elastic material such as natural rubber is attached to the first mount fixing portion 45. The first mount 45a is formed in a substantially tubular shape, and a fixing bolt (not shown) for fixing the motor 20 with a reduction mechanism to the roof of the vehicle is inserted through the central portion thereof.

Further, a second mount fixing portion 46 is integrally provided on the output shaft accommodating portion 44 side along the lateral direction of the gear case 41 and on the yoke fixing portion 42a side of the output shaft accommodating portion 44 along the longitudinal direction of the gear case 41. Has been done. The second mount fixing portion 46 protrudes toward the yoke fixing portion 42a from the output shaft accommodating portion 44 along the longitudinal direction of the gear case 41, and is arranged at a substantially central portion along the longitudinal direction of the motor 20 with a reduction mechanism. ing. A second mount 46a having the same structure as the first mount 45a is attached to the second mount fixing portion 46.

As described above, the motor 20 with the reduction mechanism is elastically supported by the roof of the vehicle via the first mount 45a and the second mount 46a. This makes it difficult for the vibration of the motor 20 with a reduction mechanism to be transmitted to the vehicle.

Hereinafter, the positional relationship between the first mount 45a and the second mount 46a with respect to the gear case 41 will be described in more detail with reference to FIGS. 3 and 7.

First, as shown in FIG. 7, both the first mount 45a and the second mount 46a are arranged on one side (lower side) along the thickness direction (vertical direction in FIG. 7) of the motor 20 with a reduction mechanism. It is arranged on a plane SF parallel to the axial direction of the armature shaft 34 and the output shaft 70. That is, the first mount 45a and the second mount 46a are arranged on the same plane as each other.

Further, as shown in FIG. 3, the first mount 45a and the second mount 46a are arranged so as to be offset from each other in a direction intersecting (orthogonal) with the axial direction of the armature shaft 34 and the output shaft 70. That is, the first mount 45a and the second mount 46a are arranged at predetermined intervals in the lateral direction (vertical direction in FIG. 3) of the motor 20 with the reduction mechanism.

Further, as shown in FIG. 3, when the motor 20 with a reduction mechanism is viewed from a direction intersecting (orthogonal) with the direction in which the armature shaft 34 and the output shaft 70 overlap, the first mount 45a has the armature shaft 34. It is arranged on the axis of. More specifically, the first mount 45a is arranged on the armature shaft extension region AR1 (shaded portion in the figure) formed on the extension line of the armature shaft 34. On the other hand, the second mount 46a is arranged on the axis of the output shaft 70. More specifically, the second mount 46a is arranged on the output shaft extension region AR2 (shaded portion in the figure) formed on the extension line of the output shaft 70.

As a result, the motor 20 with the reduction mechanism can be fixed in a well-balanced manner by the first mount 45a and the second mount 46a even though there are two fixing points to the roof of the vehicle. More specifically, since the first mount 45a and the second mount 46a are arranged on the axes of the armature shaft 34 and the output shaft 70, respectively, the armature shaft 34 and the output shaft 70 rotate, and the gear case 41 ( Even if a reaction force for twisting the gear case 41 acts on the motor 20) with a reduction mechanism, rattling and distortion of the gear case 41 can be effectively suppressed.

As shown in FIGS. 3 and 7, the output shaft accommodating portion 44 and the second cover member 44b are provided with a first flange portion 44c and a second flange portion 44d protruding in the axial direction of the output shaft 70, respectively. ing. These first and second flange portions 44c and 44d are formed in an annular shape and are arranged coaxially with the output shaft 70. The first and second flange portions 44c and 44d are provided to position the motor 20 with a reduction mechanism at a predetermined position on the roof of the vehicle, as shown in FIG. Specifically, the first and second flange portions 44c and 44d are inserted into the insertion recess DP of the mounting bracket BR provided in the roof of the vehicle.

This makes it possible to easily install the motor 20 with a reduction mechanism in a narrow space in the roof. Here, in FIG. 9, only the second flange portion 44d side is shown, but the same mounting bracket BR as that shown in FIG. 9 is also provided on the first flange portion 44c side.

A worm shaft (rotating shaft) 50 is rotatably housed inside the worm shaft accommodating portion 42. As shown in FIG. 8, the worm shaft 50 is arranged coaxially with the armature shaft 34 and is rotated by the armature shaft 34 via the connecting member 51. That is, the armature shaft 34 and the worm shaft 50 are integrally rotatably connected by the connecting member 51.

An annular sensor magnet MG is provided close to the connecting member 51 on the longitudinal proximal end side (right side in FIG. 8) of the worm shaft 50. Further, a hall sensor (not shown) is provided in the vicinity of the sensor magnet MG, whereby the hall sensor outputs a square wave signal as the sensor magnet MG rotates. Then, a rectangular wave signal from the hall sensor is detected by a controller (not shown), whereby the controller grasps the rotational state of the worm shaft 50 and controls the rotational state of the armature shaft 34.

A first worm 52 (not shown in detail) is integrally provided on the side opposite to the sensor magnet MG side along the longitudinal direction of the worm shaft 50. The first worm 52 is formed on a worm shaft 50 made of a steel material by rolling or the like. Here, the first worm 52 constitutes the worm in the present invention, and is rotated by the armature shaft 34 and the worm shaft 50.

A second radial bearing B2 and a third radial bearing B3 are provided on both sides of the first worm 52 in the axial direction, respectively. These second and third radial bearings B2 and B3 are fixed to the inside of the worm shaft accommodating portion 42, whereby the worm shaft 50 can rotate smoothly without rattling inside the worm shaft accommodating portion 42. Will be done. As for the second and third radial bearings B2 and B3, as with the first radial bearing B1, a so-called "metal bearing" is used as a slide bearing.

As shown in FIGS. 6 and 8, a steel intermediate shaft 60 is rotatably housed inside the intermediate shaft accommodating portion 43. The intermediate shaft 60 constitutes the driven shaft in the present invention, and is rotated by the rotation of the worm shaft 50. The intermediate shaft 60 extends in a direction intersecting the worm shaft 50. A first ball bearing 61 is fixed to one side of the intermediate shaft 60 in the axial direction (right side in FIG. 6). The first ball bearing 61 includes an inner race 61a, an outer race 61b, and a plurality of steel balls 61c rotatably provided between them.

The inner race 61a is fixed to one side of the intermediate shaft 60 in the axial direction by press fitting, and is prevented from coming off by the washer W and the first snap ring SR1. Further, as shown in FIG. 6, the outer race 61b is sandwiched between the gear case 41 and the first cover member 43b. That is, the first ball bearing 61 is supported by the gear case 41 and the first cover member 43b. As a result, the intermediate shaft 60 is in a state in which the movement in the axial direction is restricted inside the intermediate shaft accommodating portion 43, and the intermediate shaft 60 can rotate smoothly.

In this way, the intermediate shaft 60 is in a state in which the movement in the axial direction is restricted by the first ball bearing 61, so that thrusts that support the intermediate shaft 60 from the axial direction are on both sides of the intermediate shaft 60 in the axial direction. There is no need to provide bearings or the like. As a result, it is possible to prevent the dimension along the axial direction of the intermediate shaft 60 of the gear case 41 (the dimension along the lateral direction of the gear case 41) from becoming large. In other words, the motor 20 with a reduction mechanism achieves both reduction in the number of parts and miniaturization.

A resin-made first helical gear 62 is provided on one side of the intermediate shaft 60 in the axial direction and in the vicinity of the first ball bearing 61. The first helical gear 62 constitutes the gear according to the present invention, and the first worm 52 is meshed with the first helical gear 62. That is, the first worm 52 and the first helical gear 62 constitute the first reduction mechanism SD1 including the worm reduction gear. Specifically, the first deceleration mechanism SD1 decelerates the rotation of the armature shaft 34 (worm shaft 50) to a predetermined rotation speed, and outputs the decelerated and high torque rotational force from the intermediate shaft 60. It has become.

A second worm 63 (not shown in detail) is integrally provided on the other side (left side in FIG. 6) of the intermediate shaft 60 in the axial direction. The second worm 63 is formed on an intermediate shaft 60 made of a steel material by rolling or the like.

Further, a fourth radial bearing B4 is mounted between the first helical gear 62 and the second worm 63 along the axial direction of the intermediate shaft 60. Similar to the first radial bearing B1, the fourth radial bearing B4 also employs a so-called "metal bearing", which is a slide bearing. Then, in the fourth radial bearing B4, as shown in FIG. 8, the motor 20 with a reduction mechanism is viewed from a direction in which the first worm 52 of the worm shaft 50 and the second helical gear 71 of the output shaft 70 do not overlap. At that time, it is provided between the first worm 52 and the second helical gear 71 along the axial direction of the intermediate shaft 60. More specifically, as shown in FIG. 6, the fourth radial bearing B4 is arranged in the gap region AR3 between the first worm 52 and the second helical gear 71.

As shown in FIGS. 7 and 8, the output shaft 70 is rotatably housed inside the output shaft accommodating portion 44. The output shaft 70 is made of a steel material like the intermediate shaft 60, and extends in a direction intersecting the intermediate shaft 60. A second helical gear 71 is integrally provided at the central portion of the output shaft 70 in the axial direction, so that the second helical gear 71 is made of steel. A second worm 63 is meshed with the second helical gear 71, whereby the output shaft 70 is rotated by the intermediate shaft 60. The second worm 63 and the second helical gear 71 constitute a second reduction mechanism SD2 including a worm reduction gear. Specifically, the second deceleration mechanism SD2 decelerates the rotation of the intermediate shaft 60 to a predetermined rotation speed, and outputs the rotational force which has been decelerated to increase the torque from the output shaft 70.

As described above, the motor 20 with a speed reduction mechanism includes only a two-stage worm speed reducer (first speed reduction mechanism SD1 and second speed reduction mechanism SD2).

The output shaft 70 is parallel to the armature shaft 34 and the worm shaft 50, and the first connecting portion 72 and the second connecting portion 73 are provided on both sides in the axial direction thereof. Specifically, the first connecting portion 72 is provided on the yoke 31 side along the axial direction of the output shaft 70, and the second connecting portion 73 is on the side opposite to the yoke 31 side along the axial direction of the output shaft 70 ( It is provided on the first mount 45a side).

Then, as shown in FIG. 9, a pair of drive shafts 14 are connected to the first and second connecting portions 72 and 73 so as to be able to transmit power. In this way, since the drive shafts 14 are connected to both sides of the output shaft 70 in the axial direction, the output shaft 70 is not subjected to a reaction force for moving the output shaft 70 in the axial direction.

A second ball bearing 74 is fixed to one side of the output shaft 70 in the axial direction (right side in FIG. 7). The second ball bearing 74 includes an inner race 74a, an outer race 74b, and a plurality of steel balls 74c rotatably provided between them.

The inner race 74a is fixed to one side of the output shaft 70 in the axial direction by press fitting, and is prevented from coming off by the second snap ring SR2. Further, as shown in FIG. 7, the outer race 74b is sandwiched between the gear case 41 and the second cover member 44b. That is, the second ball bearing 74 is supported by the gear case 41 and the second cover member 44b. As a result, the output shaft 70 is in a state in which the movement in the axial direction is restricted inside the output shaft accommodating portion 44, and the output shaft 70 can rotate smoothly.

Further, a fifth radial bearing B5 is mounted on the other side of the output shaft 70 in the axial direction (left side in FIG. 7). Similar to the first radial bearing B1, the fifth radial bearing B5 also employs a so-called "metal bearing", which is a slide bearing. The outer peripheral portion of the fifth radial bearing B5 is fixed in the vicinity of the first flange portion 44c of the gear case 41.

As shown by the broken line circle in FIG. 7, it is possible to easily obtain a variation in which the axial direction of the output shaft 70 is shifted by a predetermined angle (α °) with respect to the axial direction of the armature shaft 34 and the worm shaft 50. it can. Specifically, the output shaft 70 is tilted by a predetermined angle about the intermediate shaft 60, only the gear case 41 whose shape has been changed is prepared, and other parts are kept in common, and a variation of the motor 20 with a reduction mechanism is provided. Can be increased. In this case, the length dimension of the output shaft 70 and the length dimension of the intermediate shaft 60 are substantially the same length dimension as shown in FIG. 8, and therefore, by tilting the output shaft 70, the deceleration mechanism The physique of the attached motor 20 does not change significantly. Therefore, the mountability in a narrow space is well maintained.

Here, it is necessary to firmly fix the first helical gear 62 made of resin to the intermediate shaft 60 made of steel. Therefore, in the motor 20 with a reduction mechanism according to the present embodiment, as shown in FIGS. 10 and 11, a gear fixing mechanism GF is provided between the first helical gear 62 and the intermediate shaft 60 to fix both. Is devised.

The intermediate shaft 60 is provided with a gear mounting portion 64 on which the first helical gear 62 is mounted. A pair (s) of first and second key grooves 64a and 64b are formed on both sides of the gear mounting portion 64 in the axial direction, respectively. The pair of first key grooves 64a are provided on the second worm 63 side (left side in the drawing) along the axial direction of the gear mounting portion 64, and are spaced 180 ° (equally spaced) in the circumferential direction of the gear mounting portion 64. They are arranged so as to face each other. On the other hand, the pair of second key grooves 64b are provided on the side opposite to the second worm 63 side (right side in the drawing) along the axial direction of the gear mounting portion 64, and 180 ° in the circumferential direction of the gear mounting portion 64. They are arranged so as to be spaced apart (equally spaced).

Here, the pair of first key grooves 64a and the pair of second key grooves 64b constitute the key grooves in the present invention. Further, the pair of first key grooves 64a and the pair of second key grooves 64b are arranged straight in the axial direction of the intermediate shaft 60. Further, in FIGS. 10 and 11, only one of the first and second key grooves 64a and 64b is shown.

A pair of first keys 65a (see FIG. 10) are inserted into the pair of first key grooves 64a, and a pair of second keys 65b (see FIG. 11) are inserted into the pair of second key grooves 64b. ) Is to be inserted. The first and second keys 65a and 65b are made of steel and formed in a substantially rectangular parallelepiped shape, respectively. Then, under the state where the first and second keys 65a and 65b are inserted into the first and second key grooves 64a and 64b, a part of the first and second keys 65a and 65b has a diameter of the gear mounting portion 64. It is designed to protrude outward in the direction. That is, the height dimension of the first and second keys 65a and 65b is larger than the depth dimension of the first and second key grooves 64a and 64b. Here, the first and second keys 65a and 65b each constitute a protrusion member and a key in the present invention.

A steel annular plate (plate member) 66 is attached to each of the pair of first keys 65a and the pair of second keys 65b. Specifically, the annular plate 66 includes a main body 66a, a pair (plurality) of engaging recesses (projection engaging portions) 66b provided inside the main body 66a in the radial direction, and a radial outer side of the main body 66a. It is provided with four (plurality) engaging convex portions (gear engaging portions) 66c provided in the above.

Then, the pair of first and second keys 65a and 65b are inserted into and engaged with the pair of engaging recesses 66b, respectively. That is, even in the pair of engaging recesses 66b, they are arranged so as to face each other at 180 ° intervals (equal intervals) in the circumferential direction of the annular plate 66. As a result, the annular plate 66 is firmly fixed to the intermediate shaft 60 so as not to rotate relative to the intermediate shaft 60.

The intermediate shaft 60 and the annular plate are not limited to the provision of the first key groove 64a and the first key 65a, the second key groove 64b and the second key 65b, and the engaging recess 66b of the annular plate 66. If the rigidity of 66 can be sufficiently ensured, three or more of each may be provided.

Further, plate accommodating portions 62a for accommodating the annular plate 66 are provided at both ends of the first helical gear 62 in the axial direction, and the plate accommodating portions 62a are recessed in the axial direction of the first helical gear 62. It is provided. By accommodating the annular plates 66 in these plate accommodating portions 62a, the first helical gear 62 rotates integrally with the pair of annular plates 66. In addition, in FIG. 10 and FIG. 11, only the plate accommodating portion 62a on one side (left side in the drawing) is shown.

More specifically, four (plurality) accommodating recesses 62b are provided on the radial outer side of the plate accommodating portions 62a provided on both sides of the first helical gear 62 in the axial direction. These accommodating recesses 62b form the recessed portions in the present invention, and are arranged at 90 ° intervals (equal intervals) in the circumferential direction of the first helical gear 62. Then, inside these accommodating recesses 62b, four engaging convex portions 66c provided on the annular plate 66 and projecting outward in the radial direction are respectively inserted. Therefore, the engaging convex portions 66c are also arranged at 90 ° intervals (equal intervals) in the circumferential direction of the annular plate 66. As a result, the annular plate 66 is engaged with the axial end portion of the first helical gear 62 so as not to rotate relative to each other.

As described above, gear fixing mechanisms GF including the first and second keys 65a and 65b and the annular plate 66 are provided on both sides of the first helical gear 62 in the axial direction. As a result, the rotational force of the intermediate shaft 60 is transmitted to the first helical gear 62 from the four engaging convex portions 66c of the pair of annular plates 66 (a total of eight engaging convex portions 66c). In this way, the rotational force of the intermediate shaft 60 can be transmitted to the first helical gear 62 in a state of being dispersed from the total of eight engaging convex portions 66c, so that a part of the resin-made first helical gear 62 (1). It is possible to reliably prevent the stress from being concentrated and damaged at the location). Therefore, even the first helical gear 62 made of resin can transmit a larger rotational force.

The procedure for assembling the first helical gear 62 with respect to the intermediate shaft 60 will be described. First, as shown by the arrow (1) in FIG. 10, the pair of first keys 65a are mounted on the pair of first key grooves 64a, respectively. .. Next, as shown by the arrow (2), one annular plate 66 is attached to the plate accommodating portion 62a on one side in the axial direction (second worm 63 side) of the first helical gear 62. At this time, the four engaging protrusions 66c are accommodated in the four accommodating recesses 62b, respectively.

After that, as shown by the arrow (3), the first helical gear 62 to which one of the annular plates 66 is mounted is mounted on the gear mounting portion 64. At this time, the pair of first keys 65a are inserted into the pair of engaging recesses 66b.

Next, as shown by the arrow (4) in FIG. 11, the pair of second keys 65b are attached to the pair of second key grooves 64b, respectively. Then, as shown by the arrow (5), the other annular plate 66 is mounted on the gear mounting portion 64. At this time, the pair of second keys 65b is inserted into the pair of engaging recesses 66b. Further, the other annular plate 66 is accommodated in the plate accommodating portion 62a (not shown) on the other side in the axial direction of the first helical gear 62 (the side opposite to the second worm 63 side). At this time, the four engaging protrusions 66c are accommodated in the four accommodating recesses 62b, respectively.

Next, as shown by the arrow (6), the third snap ring SR3 is attached to the intermediate shaft 60. Specifically, the third snap ring SR3 is fitted into the annular groove 67 provided on the side opposite to the second worm 63 side along the axial direction of the gear mounting portion 64. As a result, the first helical gear 62 is prevented from coming off by the third snap ring SR3, and the assembly (fixation) of the first helical gear 62 to the intermediate shaft 60 (gear mounting portion 64) is completed.

Here, since the motor 20 with a reduction mechanism according to the present embodiment has been miniaturized as described above, further measures are taken as shown below.

Specifically, as shown in FIGS. 5 and 12, the yoke flange 31d of the yoke 31 can be easily positioned with respect to the yoke fixing portion 42a of the gear case 41, and the output shaft 70 has a second position. A space SP is secured in the vicinity of the 1 connecting portion 72 so that the drive shaft 14 (see FIGS. 1 and 9) can be easily connected.

As shown in FIGS. 5 and 12, a total of three first, second, and third positioning protrusions 42b, 42c, and 42d are provided on the abutting surface to which the yoke flange 31d of the yoke fixing portion 42a is abutted. ing. These first, second, and third positioning protrusions 42b, 42c, and 42d are projected toward the yoke 31, and the cross-sectional shape along the direction intersecting the protruding direction is a substantially quadrangle.

The first positioning protrusion 42b of the first, second, and third positioning protrusions 42b, 42c, and 42d is provided on one of the arc portions 31a (on the first cover member 43b side) of the pair of arc portions 31a of the yoke 31. It is provided correspondingly and is arranged at a position corresponding to the top T of the arc portion 31a. On the other hand, the other second and third positioning protrusions 42c and 42d are provided corresponding to the other arc portion 31a (output shaft 70 side) of the pair of arc portions 31a of the yoke 31, and the arc portion 31a It is arranged at a position deviated from the top portion T of the pair of flat plate portions 31b.

The first, second, and third positioning projections 42b, 42c, and 42d enter the first, second, and third positioning recesses 31e, 31f, and 31g, respectively, provided in the pair of yoke flanges 31d. I'm out. As a result, the yoke 31 can be positioned at a regular position with respect to the gear case 41, and the assembling workability (connection workability) between the motor portion 30 and the gear portion 40 can be improved.

Here, the pair of fixing screws S1 for fixing the yoke 31 and the gear case 41 are arranged at positions avoiding the first, second, and third positioning recesses 31e, 31f, and 31g. Thereby, the "positioning mechanism" including the first, second and third positioning protrusions 42b, 42c, 42d and the first, second and third positioning recesses 31e, 31f, 31g can be made relatively large. Therefore, it is possible to improve the fixing strength at the time of positioning (temporary fixing) while improving the assembling workability (connecting workability).

Further, a concave groove 42e is formed between the second positioning protrusion 42c and the third positioning protrusion 42d. The concave groove 42e is provided in the gear case 41 and is recessed toward the armature 33. Further, the concave groove 42e is arranged in the vicinity (substantially right beside) of the first connecting portion 72. As a result, a predetermined space SP can be provided in a portion around the first connecting portion 72, which is particularly complicated around the gear case 41. As a result, the operation of connecting the drive shaft 14 to the first connecting portion 72 can be easily performed.

In other words, the second and third positioning protrusions 42c and 42d are arranged so as to be offset from the top T of the arc portion 31a to the pair of flat plate portions 31b side (upper and lower in FIG. 5), thereby forming the top T of the arc portion 31a. The corresponding portion of the gear case 41 can be thinned. Therefore, the first connecting portion 72 of the output shaft 70 can be arranged closer to the gear case 41. Therefore, it is possible to achieve both further miniaturization of the motor 20 with a reduction mechanism and improvement of the connection workability of the drive shaft 14. Further, since the mounting space of the motor 20 with the reduction mechanism can be narrowed, the narrowed space can be allocated to the opening amount of the opening / closing body. Therefore, it is possible to increase the opening amount of the opening / closing body.

As described in detail above, according to the present embodiment, the first helical gear 62 made of resin, the intermediate shaft 60 made of steel, the gear fixing mechanism GF between the first helical gear 62 and the intermediate shaft 60, and The gear fixing mechanism GF is provided on the intermediate shaft 60, and the first and second keys 65a and 65b protruding outward in the radial direction of the intermediate shaft 60 and the first and second keys 65a and 65b are engaged with each other. A steel annular plate in which a pair of engaging recesses 66b to be combined are provided radially inside, and four engaging protrusions 66c to which the axial ends of the first helical gear 62 are engaged are provided radially outward. It has 66 and.

As a result, the resin first helical gear 62 can be fixed to the steel annular plate 66. The engagement portion (engagement convex portion 66c and accommodating concave portion 62b) between the annular plate 66 and the first helical gear 62 is radially outer side as compared with the conventional one in which the radial inside of the gear and the key are directly engaged. Since it can be arranged in, the rigidity of the engaging portion between the annular plate 66 and the first helical gear 62 can be increased. That is, the deformation of the first helical gear 62 is suppressed by preventing the stress from being locally concentrated on the inside in the radial direction of the first helical gear 62. Therefore, the motor 20 with the reduction mechanism can be further reduced in size and weight, and the quietness can be improved while suppressing the cost increase.

Further, according to the present embodiment, a pair of first and second key grooves 64a and 64b are provided on the outer side in the radial direction of the intermediate shaft 60, and the first and second key grooves 64a and 64b are provided with the first and first key grooves 64a and 64b, respectively. The second keys 65a and 65b are attached, and the first and second keys 65a and 65b are engaged with the pair of engaging recesses 66b of the annular plate 66.

As a result, it is possible to adopt a fixing method using "key grooves and keys", which is advantageous in terms of cost, and it is possible to suppress an increase in cost of the motor 20 with a reduction mechanism.

Further, according to the present embodiment, two first and second key grooves 64a and 64b are provided at 180 ° intervals (equal intervals) in the circumferential direction of the intermediate shaft 60, and the engaging recesses 66b are provided around the annular plate 66. Since two pieces are provided at 180 ° intervals (equal intervals) in the direction, the rotational force transmitted between the intermediate shaft 60 and the annular plate 66 can be dispersed.

As a result, the rattling of the annular plate 66 with respect to the intermediate shaft 60 can be suppressed for a long period of time, and the quietness of the motor 20 with a reduction mechanism can be further improved.

Further, according to the present embodiment, the annular plate 66 is provided with the engaging convex portion 66c so as to project outward in the radial direction thereof, and the engaging convex portion 66c is provided at the axial end portion of the first helical gear 62. An accommodating recess 62b for entering is provided.

As a result, the engaging portion between the annular plate 66 and the first helical gear 62 can be arranged on the outer side in the radial direction thereof, and the rigidity of the engaging portion between the engaging convex portion 66c and the accommodating concave portion 62b is further increased. Can be done.

Further, according to the present embodiment, four engaging protrusions 66c are provided at 90 ° intervals (equal intervals) in the circumferential direction of the annular plate 66, and the accommodating recesses 62b are provided in the circumferential direction of the first helical gear 62. Four are provided at 90 ° intervals (equal intervals).

As a result, the rotational force transmitted between the annular plate 66 and the first helical gear 62 can be dispersed in four places while the rigidity of the engaging portion between the annular plate 66 and the first helical gear 62 is increased. it can. Therefore, the deformation of the first helical gear 62 can be further suppressed, and the quietness of the motor 20 with the reduction mechanism can be maintained for a longer period of time.

Further, according to the present embodiment, since the gear fixing mechanism GFs are provided on both sides of the first helical gear 62 in the axial direction, a total of eight rotational forces transmitted between the annular plate 66 and the first helical gear 62 are provided. Can be dispersed in. Therefore, the deformation of the first helical gear 62 can be further suppressed, and the quietness of the motor 20 with the reduction mechanism can be maintained for a longer period of time.

It goes without saying that the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the gist thereof. In the above embodiment, the intermediate shaft 60 is provided with a pair of first key grooves 64a and a pair of second key grooves 64b, respectively, and the first and second key grooves 64a and 64b are provided with the first and second keys 65a and 65b. However, the present invention is not limited to this. For example, through holes are provided on both sides of the gear mounting portion 64 (see FIG. 10) in the axial direction in a direction orthogonal to the axial direction of the intermediate shaft 60 and function as a key groove, and rod-shaped keys are provided in these through holes. You may insert each of them. In this case, the assembly process of the motor 20 with the reduction mechanism can be further simplified.

Further, in the above embodiment, four engaging protrusions 66c of the annular plate 66 are provided at 90 ° intervals, and four accommodating recesses 62b of the first helical gear 62 are provided at 90 ° intervals. The invention is not limited to this, and two, three, or even five or more may be provided. However, the rigidity of the engaging portion between the annular plate 66 and the first helical gear 62 is sufficiently ensured. Further, the engaging convex portion 66c and the accommodating concave portion 62b are arranged at equal intervals in the circumferential direction of the annular plate 66 and the first helical gear 62.

Further, in the above embodiment, the second helical gear 71 is integrally provided at the central portion in the axial direction of the output shaft 70, and the second helical gear 71 is made of steel. However, the present invention is not limited to this. The second helical gear 71 may also be made of resin like the first helical gear 62, and may adopt the same gear fixing mechanism GF as the first helical gear 62. In this case, the weight of the motor 20 with a reduction mechanism can be further reduced.

Further, in the above embodiment, the sunshade 12 (see FIG. 1) as an opening / closing body provided on the roof of the vehicle is opened / closed driven by the rotation of the output shaft 70, but the present invention is not limited to this. The sunroof may be used as an opening / closing body, and the sunroof may be driven to open / close by rotation of the output shaft 70.

Further, in the above embodiment, the present invention has been shown in which the present invention is applied to a drive source of an electric sunshade device 10 mounted on a vehicle roof, but the present invention is not limited to this, and is mounted on, for example, a vehicle door. It can also be applied to a drive source such as a sliding door device or a power window device.

In addition, the material, shape, dimensions, number, installation location, etc. of each component in the above embodiment are arbitrary as long as the present invention can be achieved, and are not limited to the above embodiment.

10 Electric sunshade device 11 Guide rail 11a Sliding groove 12 Sunshade (opening and closing body)
12a Sliding member 13 Drive mechanism 14 Drive shaft 15 Drive chain 20 Motor with deceleration mechanism 30 Motor part 31 York 31a Arc part 31b Flat plate part 31c Bottom part 31d York flange 31e 1st positioning recess 31f 2nd positioning recess 31g 3rd positioning recess 32 Permanent magnet 33 Armature 34 Armature axis (rotation axis)
35 Armature core 36 Coil 37 Commitator 37a Segment 40 Gear part 41 Gear case 41a Ceiling wall part 41b Bottom wall part 41c Side wall part 42 Worm shaft accommodating part 42a Yoke fixing part 42b 1st positioning protrusion 42c 2nd positioning protrusion 42d 3rd positioning protrusion 42e Recessed groove 43 Intermediate shaft accommodating part 43a First opening 43b First cover member 44 Output shaft accommodating part 44a Second opening 44b Second cover member 44c First flange part 44d Second flange part 45 First mount fixing part 45a No. 1 mount 46 2nd mount fixing part 46a 2nd mount 50 Warm shaft (rotating shaft)
51 Connecting member 52 First worm (worm)
60 Intermediate axis (driven axis)
61 1st ball bearing 61a Inner race 61b Outer race 61c Steel ball 62 1st helical gear (gear)
62a Plate accommodating part 62b Accommodating recess (recess)
63 2nd worm 64 Gear mounting part 64a 1st key groove (key groove)
64b 2nd keyway (keyway)
65a 1st key (protrusion member, key)
65b 2nd key (protrusion member, key)
66 Ring plate (plate member)
66a Main body 66b Engagement recess (protrusion engagement)
66c Engagement convex part (gear engagement part)
67 Circular groove 70 Output shaft 71 2nd helical gear 72 1st connecting part 73 2nd connecting part 74 2nd ball bearing 74a Inner race 74b Outer race 74c Steel ball AR1 Armature shaft extension area AR2 Output shaft extension area AR3 Gap area B1 1st Radial bearing B2 2nd radial bearing B3 3rd radial bearing B4 4th radial bearing B5 5th radial bearing BR mounting bracket DP insertion recess GF gear fixing mechanism MG sensor magnet S1 fixing screw S2 fixing screw S3 fixing screw SD1 1st deceleration mechanism SD2 2nd deceleration mechanism SF plane SP space SR1 1st snap ring SR2 2nd snap ring SR3 3rd snap ring T top W washer

Claims (6)

A motor with a reduction mechanism that decelerates the rotation of the rotating shaft and outputs it.
The worm rotated by the rotation axis and
A resin gear that meshes with the worm and
A steel driven shaft to which the gear is fixed,
A gear fixing mechanism provided between the gear and the driven shaft,
Have,
The gear fixing mechanism is
A protruding member provided on the driven shaft and projecting radially outward of the driven shaft,
A steel plate member in which a protrusion engaging portion with which the protrusion member is engaged is provided on the inside in the radial direction and a gear engaging portion on which the axial end of the gear is engaged is provided on the outside in the radial direction.
Equipped with a,
The gear engaging portion is an engaging convex portion protruding outward in the radial direction of the plate member.
A recessed portion into which the engaging convex portion enters is provided at the axial end portion of the gear.
The protrusion engaging portion and the engaging convex portion are provided at the same position in the circumferential direction of the plate member.
The tip portion of the engaging protrusion is, that extends up to the tooth portion of said gear,
Motor with reduction mechanism. In the motor with a reduction mechanism according to claim 1,
A keyway is provided on the radial outer side of the driven shaft.
The protrusion member is a key to be mounted on the key groove.
The protrusion engaging portion is an engaging recess into which the key enters.
Motor with reduction mechanism. In the motor with a reduction mechanism according to claim 2,
A plurality of the key grooves are provided at equal intervals in the circumferential direction of the driven shaft.
A plurality of engaging recesses are provided at equal intervals in the circumferential direction of the plate member.
Motor with reduction mechanism. The motor with a reduction mechanism according to any one of claims 1 to 3 .
A plurality of the engaging protrusions are provided at equal intervals in the circumferential direction of the plate member.
A plurality of the recessed portions are provided at equal intervals in the circumferential direction of the gear.
Motor with reduction mechanism. The motor with a reduction mechanism according to any one of claims 1 to 4 .
The gear fixing mechanism is provided on both sides of the gear in the axial direction.
Motor with reduction mechanism. The motor with a reduction mechanism according to any one of claims 1 to 5 .
It has an output shaft that is rotated by the driven shaft.
The output shaft opens and closes and drives an opening and closing body provided on the ceiling of the vehicle.
Motor with reduction mechanism.

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