WO2015182630A1

WO2015182630A1 - Starter

Info

Publication number: WO2015182630A1
Application number: PCT/JP2015/065162
Authority: WO
Inventors: 龍解; 眞徳渡部; 安部　元幸
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2014-05-30
Filing date: 2015-05-27
Publication date: 2015-12-03
Also published as: JP2015224622A

Abstract

　Provided is a starter whereby vibration and noise occurring when the starter operates can be reduced. A starter is provided with: an electric motor (1) for generating rotational torque; a planetary gear mechanism (2) having a sun gear (21) formed on a motor rotating shaft, an internal gear (23) arranged on a front frame, a planetary gear (22) for meshing with the sun gear and the internal gear, a planetary gear pin for rotatably supporting the planetary gear, and a carrier (24) for holding the planetary gear pin; a one-way clutch (3) arranged along the axial direction of the motor, the one-way clutch transmitting the drive force of the motor in one direction to a pinion; and a pinion (5) integrated with an inner of the one-way clutch, the pinion meshing with a ring gear of the engine, a round hole being formed in the axially central part of the carrier, and the front end part of the motor rotating shaft being rotatably supported via a slip bearing, wherein the starter is configured so that a shaft plate (20) is provided between the motor rotating shaft (12) and the carrier (24).

Description

Starter

The present invention relates to a starter mounted on an automobile.

In recent years, there is an increasing need for quietness in automotive components such as automobile starters from the viewpoint of noise regulation and comfort. As one of the measures for realizing the quiet starter, there is a measure for suppressing the vibration generated in the starter. As a technique related to such starter vibration suppression, there is, for example, one described in Patent Document 1.

JP 2006-170104 A

In the starter disclosed in Patent Document 1, axial vibration can be reduced by installing a thrust washer. However, in such a conventional starter configuration, the front end portion of the motor rotation shaft is supported by a bearing installed in the casing, and the rear end portion of the motor rotation shaft is supported by a bearing installed in the center of the end plate. An eccentric rotation of the motor rotation shaft occurs due to an unbalance of a motor manufacturing error and a force applied to the motor rotation shaft. In such a case, a collision between the front end portion of the motor rotation shaft and the bearing supporting the front end portion occurs, and there is a problem that vibration and noise tend to increase. In addition, the durability of the motor rotation shaft and the bearing may be reduced due to the collision.

Therefore, an object of the present invention is to provide a starter that can reduce vibration and noise during starter operation.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above-described problems. For example, a motor that generates rotational torque, a sun gear formed on the motor rotation shaft, an internal gear installed on the front frame, A planetary gear that meshes with the sun gear and the internal gear, a planetary gear pin that rotates and supports the planetary gear, and a planetary gear mechanism that has a carrier that holds the planetary gear pin, and is arranged in the axial direction of the motor, The carrier includes a one-way clutch that transmits a driving force to the pinion in one direction, and a pinion that is integrated with an inner of the one-way clutch and meshes with a ring gear of the engine. A starter that is formed and supports a front end portion of the motor rotation shaft via a sliding bearing in a freely rotatable manner, the motor rotation shaft And providing a shaft plate between said carrier.
It is characterized by.

According to the present invention, it is possible to provide a starter that can reduce vibration and noise during starter operation. Problems, configurations, and effects other than those described above will become apparent from the description of the following examples.

The axial direction sectional view of a starter. The enlarged view of the axial sectional view of a planetary gear mechanism and a shaft plate. The enlarged view of the front view which looked at the axial plate from the axial direction front. The AA arrow directional cross-sectional view of a shaft plate. The enlarged view of the front view which looked at the improved axial plate from the axial direction front. AA sectional view taken on line AA of the improved shaft plate. The enlarged view of the axial sectional view of the front end surface of the carrier and motor rotating shaft of Example 2. FIG. The enlarged view of the axial sectional view of the front end surface of the carrier and motor rotation shaft of Example 3.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 is an axial sectional view of the starter. The starter of the present embodiment includes a motor 1, a planetary gear mechanism 2, a one-way clutch 3, a pinion shaft 4, a pinion 5, a magnet switch 6, and a shift lever 7.

The motor 1 is a direct current motor, and includes a cylindrical yoke 11, a motor rotating shaft 12, and an armature 13 disposed on the radially inner side of the yoke 11. A plurality of permanent magnets 14 are installed on the inner peripheral surface of the yoke 11 in the circumferential direction. An end plate 15 is provided at the rear end of the yoke 11. A rear sliding bearing 16 for rotatably supporting the rear end portion of the motor rotating shaft 12 is provided at the radial center of the end plate 15.

A plurality of teeth (not shown) are formed in the armature 13 in the circumferential direction, and slots (not shown) are formed between adjacent teeth. A coil (not shown) is wound between the two slots. The commutator 17 includes a plurality of segments (not shown) that are mutually insulated, and each segment is coupled to a coil.

The armature 13 and the commutator 17 are fixed to the motor rotating shaft 12, and the rear end portion of the motor rotating shaft 12 is rotatably supported via a sliding bearing 16 installed on the end frame 15.

The planetary gear mechanism 2 is accommodated in a front frame 81 installed in the front part of the yoke 11. The planetary gear mechanism 2 includes a sun gear 21 formed at the front end portion of the motor rotating shaft 12, a plurality of planetary gears 22 that mesh with the sun gear 21, and an internal gear 23 installed on the outer peripheral side of the planetary gear 22. The speed reducer reduces the rotational speed of the motor rotating shaft 12 and amplifies the output torque.

The internal gear 23 is installed on the front frame 81, and teeth (not shown) are formed on the inner peripheral surface. The carrier 24 is engaged with the internal gear 23 and is rotatably supported with respect to the internal gear 23. Planetary gear support pins 25 are erected on the carrier 24 at equal intervals, and the planetary gear 22 is rotatably supported. In addition, a round hole is formed in the radial center of the carrier, and a sliding bearing is press-fitted into the inner peripheral surface of the round hole. The front end portion of the motor rotation shaft is inserted into the slide bearing and is rotatably supported.

The pinion shaft 4 is disposed coaxially with the motor rotation shaft 12, a front end portion is supported by the front frame 81 via a bearing 82 (see FIG. 1), and a rear end portion is formed at the center portion of the carrier 24 of the planetary gear mechanism 2. It is fixed. Thereby, the pinion shaft 4 rotates integrally with the carrier 24. A helical spline 41 formed on the outer periphery of the pinion shaft 4 is engaged with a helical spline 34 of the clutch outer 31. Thereby, the torque of the pinion shaft 4 can be transmitted to the clutch outer 31, and the one-way clutch 3 can move in the axial direction with respect to the pinion shaft 4.

The one-way clutch 3 includes a clutch outer 31, a clutch inner 32 disposed inside the clutch outer 31, a clutch roller 33, and the like. A helical spline 34 is formed on the inner peripheral surface of the clutch outer 31, and the inner peripheral surface meshes with a helical spline 41 formed on the pinion shaft 4. Thereby, the torque of the pinion shaft 4 is transmitted to the clutch outer 31. A clutch roller 33 is disposed between the clutch outer 31 and the clutch inner 32 and transmits torque to the clutch inner 32. A pinion 5 is integrally provided at the tip of the clutch inner 32. The pinion 5 transmits the rotational torque of the pinion shaft 4 to an engine ring gear (not shown).

The magnet switch 6 includes an exciting coil 62 that generates an electromagnetic force when energized from the battery, a plunger 61 that operates the shift lever 7 using this electromagnetic force, and a return that pushes back the plunger 61 when the energization of the exciting coil 62 is stopped. It consists of a spring 63 and the like. Since the magnet switch 6 is well known, further explanation is omitted.

The shift lever 7 is rotatably supported by a lever pin 71 fixed to the front case 81. The upper end portion of the shift lever 7 is connected to the front end portion of the plunger 61 of the magnet switch 6, and the lower end portion of the shift lever 7 is engaged with a washer 72 that contacts the one-way clutch 3. By transmitting the movement of the plunger 61 to the one-way clutch 3 via the washer 72, the one-way clutch 3 can move in the axial direction.

When the engine start switch is turned on, the exciting coil 62 of the magnet switch 6 is energized. The plunger 61 is attracted rearward by the electromagnetic force generated by the exciting coil 62, and the upper end of the shift lever 7 connected thereto is drawn. As a result, the lower end of the shift lever 7 moves to the ring gear and pushes the one-way clutch 3 forward.

Also, due to the movement of the plunger 61, the movable contact (not shown) of the magnet switch 6 moves to the fixed contact side and contacts the fixed contact. Then, the battery voltage is applied to the armature 13 to start energization, and a magnetic field is generated. The armature 13 is rotated by electromagnetic force generated between the magnetic field and the permanent magnet 14 provided on the yoke 11. As the armature 13 rotates, the rotational torque of the armature 13 is transmitted to the pinion shaft 4 via the planetary gear speed reduction mechanism 2, and the pinion shaft 4 rotates. When the pinion shaft 4 rotates, the clutch outer 31 meshing with the pinion shaft 4 is rotated, and the pinion 5 integrated with the clutch inner 32 is rotated via the clutch roller 33. Then, while the pinion 5 rotates, it is pushed out to the ring gear side and meshes with the ring gear. After the pinion 5 and the ring gear mesh with each other, rotational torque is transmitted from the pinion 5 to the ring gear to crank the engine.

When the engine start switch is turned off, the electromagnetic force generated for stopping energization of the exciting coil 62 is reduced. The plunger 61 is returned to the original position by the reaction force of the return spring 63, the movable contact of the magnet switch 6 is separated from the fixed contact, and the energization to the motor 1 is stopped. When the plunger 61 is returned, the one-way clutch 3 is returned via the shift lever 7, so that the pinion 5 is returned away from the ring gear.

Here, when the motor 1 rotates, both ends of the motor rotating shaft 12 are supported via the sliding bearing 16 and the sliding bearing 26, respectively, so that a gap between the shaft and the bearing becomes large. Further, since there are manufacturing errors of the armature 13 and the motor rotating shaft 12, eccentric rotation occurs in the motor rotating shaft 12. On the other hand, as shown in FIG. 1, the eccentric rotation of the motor rotating shaft 12 can be suppressed by installing the shaft plate 20 at the front end portion of the motor rotating shaft 12. Hereinafter, the shaft plate 20 that characterizes this embodiment will be described in detail with reference to FIGS. 2, 3, and 4.

FIG. 2 is an enlarged view of an axial sectional view of the planetary gear mechanism 2 and the shaft plate 20. FIG. 3 is an enlarged view of a front view of the shaft plate 20 as viewed from the front in the axial direction. FIG. 4 is a cross-sectional view of the shaft plate 20 taken along line AA.

As shown in FIG. 3, the shaft plate 20 is composed of a wear-resistant disk-shaped member having a round hole at the center. Of the dimensions in the radial direction of the shaft plate 20, the diameter of the shaft plate 20 is set to be the maximum in a range where the outer periphery of the shaft plate 20 does not contact the outer periphery of the planetary gear support pin 25. The axial dimension of the shaft plate 20 is set so that the rear end surface of the shaft plate 20 comes into light contact with the front end surface of the planetary gear 22 (see FIG. 2). Further, the shaft plate 20 may be installed so that the front end surface of the shaft plate 20 and the rear end surface of the carrier 24 are in light contact with each other in the axial direction.

By providing the shaft plate 20 in this manner, when the motor rotating shaft 12 rotates eccentrically, the front and rear end surfaces of the shaft plate 20 are in contact with the rear end surface of the carrier 24 and the front end surface of the planetary gear 22, respectively. The gear 22 can apply a force to the shaft plate 20 to suppress the eccentric rotation of the motor rotating shaft 12. This action can reduce vibration and stress caused by the collision between the tip of the motor rotating shaft 12 and the bearing 26.

The shape of the shaft plate 20 for obtaining the same effect is not limited to this. For example, even if the shape is as shown in FIG. Furthermore, in the case of the shape as shown in FIG. 5, the vibration of the motor rotating shaft 12 can be absorbed and the frictional force between the shaft plate and the planetary gear can be reduced in order to suppress the eccentric rotation of the motor rotating shaft 12. FIG. 5 is an enlarged front view of the improved shaft plate 50 as viewed from the front in the axial direction. FIG. 6 is a cross-sectional view of the improved shaft plate 50 taken along the line AA.

As shown in FIG. 5, the improved shaft plate 50 is composed of a wear-resistant disk-shaped member, and a disk portion 501 having a round hole in the center and a disk surface at equal intervals on the outer periphery of the disk portion 501. And a plurality of bent portions 502 that are bent toward the outside, and an elastic structure is formed. FIG. 5 shows four bent portions, but the number of bent portions is not limited to this. Each bending portion 502 is formed to be bent forward in the axial direction (direction toward the rear end face of the carrier 24). In addition, a circular protrusion 503 is processed in the disk portion 501 in the circumferential direction rearward in the axial direction (direction toward the front end face of the planetary gear 22) (see FIG. 6).

Regarding the radial dimension of the improved shaft plate 50, the diameter of the improved shaft plate 50 is set to the maximum as long as the outer periphery of the improved shaft plate 50 does not contact the outer periphery of the planetary gear support pin 25. The axial dimension of the improved shaft plate 50 is set so that the ring-shaped protrusion 503 comes into light contact with the front end surface of the planetary gear 22. Further, the improved shaft plate 50 may be installed so that the front end surface of the bent portion 502 of the improved shaft plate and the rear end surface of the carrier 24 are in light contact with each other in the axial direction.

By providing the shaft plate 50 in this way, when the motor rotating shaft 12 rotates eccentrically, the ring-shaped protrusion 503 and the bent portion 502 of the shaft plate 50 contact the front end surface of the planetary gear 22 and the rear end surface of the carrier 24, respectively. By doing so, the carrier 24 and the planetary gear 22 can apply a force to the shaft plate 50 to suppress the eccentric rotation of the motor rotating shaft 12. Since the diameter of the shaft plate 50 is set as large as possible, the shaft plate 50 can receive a larger torque, and the effect of suppressing the eccentric rotation of the motor rotating shaft 12 can be improved. Thereby, the vibration and stress which arise from the collision of the front-end | tip part of the motor rotating shaft 12 and the bearing 26 can be reduced. In addition, by forming an elastic structure in the bent portion 502, vibrations of the carrier 24, the planetary gear 22, and the motor rotating shaft 12 themselves can be absorbed, and noise can be reduced. Furthermore, by installing the bent portion 502 and the ring-shaped protrusion 503 on the improved shaft plate 50, the contact area between the carrier 24 and the planetary gear 22 is reduced, and the frictional force is reduced.

In the second embodiment, the configurations of the motor 1 and the planetary gear mechanism 2 are the same as those in the first embodiment, and the following description is different from the first embodiment. The same parts as those in the first embodiment are denoted by the same reference numerals.

FIG. 7 is an enlarged view of an axial sectional view of the front end face of the carrier 24 and the motor rotating shaft 12 of the second embodiment. A spherical concave portion 28 is formed on the bottom surface of the round hole formed at the center of the carrier 24, and a spherical convex portion 27 is formed on the front end surface of the motor rotating shaft 12. The spherical convex part 27 and the spherical concave part 28 have the same diameter, and the spherical convex part 27 and the spherical concave part 28 are coaxially installed. After the planetary gear mechanism 2 is assembled, the spherical convex portion 27 and the spherical concave portion 28 are curvedly fitted. Thereby, when the eccentric rotation of the motor rotation shaft occurs, the spherical recess 28 can suppress the eccentric rotation of the motor rotation shaft 12 by applying a force to the spherical projection 27. Thereby, the vibration which arises from the collision of the front-end | tip part of the motor rotating shaft 12 and the bearing 26 can be reduced.

In the third embodiment, the configurations of the motor 1 and the planetary gear mechanism 2 are the same as those in the first embodiment, and the differences from the first embodiment will be described below. The same parts as those in the first embodiment are denoted by the same reference numerals.

FIG. 8 is an enlarged view of an axial sectional view of the front end face of the carrier 24 and the motor rotating shaft 12 of the third embodiment. An axial frustum-shaped protrusion 209 is provided on the bottom surface of the round hole formed in the center of the carrier 24, and an axial bottomed press-fitting hole 210 is provided on the front end surface of the motor rotating shaft 12. The inner diameter of the bottomed press-fitting hole 210 is slightly larger than the outer diameter of the circular trapezoidal protrusion 209, and the circular trapezoidal protrusion 209 is inserted into the bottomed press-fitting hole 210. When the eccentric rotation of the motor rotating shaft 12 occurs, the outer surface of the frusto-conical protrusion 209 applies a force to the inner surface of the bottomed press-fitting hole 210, thereby suppressing the eccentric rotation of the motor rotating shaft 12. Vibration generated by the collision between the tip of the motor rotating shaft 12 and the bearing 26 can be reduced.

As described above, in the present invention, the shaft plate is installed at the front end of the motor rotation shaft. When the motor rotation shaft rotates eccentrically, the carrier and the planetary gear apply a force to the shaft plate to suppress the eccentric rotation of the motor rotation shaft, thereby reducing the vibration of the motor rotation shaft and the noise and stress resulting from this vibration. Can be reduced. This will be described in detail below.

A motor for generating rotational torque, a sun gear formed on a motor rotating shaft, an internal gear installed on a front frame, a planetary gear meshing with the sun gear and the internal gear, and a planetary gear pin for rotationally supporting the planetary gear And a planetary gear mechanism having a carrier for holding the planetary gear pin, a one-way clutch arranged in the axial direction of the motor and transmitting the driving force of the motor to the pinion in one direction, and an inner of the one-way clutch, The carrier includes a pinion that meshes with the ring gear of the engine, and the carrier has a round hole formed in the center in the axial direction, and rotatably supports the front end of the motor rotating shaft via a sliding bearing. A shaft plate is provided between the motor rotation shaft and the carrier.

The shaft plate is composed of a wear-resistant disk-shaped member, and is bent to the outside of the disk surface at equal intervals around the disk part having a round hole in the radial center part and the outer peripheral part of the disk part. It has a plurality of bent portions, and each of the bent portions is formed by being bent forward in the axial direction (direction toward the rear end surface of the carrier) and has elasticity.

The shaft plate is fixed to the motor rotation shaft, and after the motor rotation shaft enters the sliding bearing, the front end surface of the bent portion and the rear end surface of the carrier are in axial contact with each other. Determine the axial position of the plate.

The shaft plate diameter is set so as to be maximized in a range where the outer periphery of the shaft plate does not contact the outer periphery of the planetary gear support pin.

In the circumferential direction of the disc part, a ring-shaped protrusion is formed on the rear side in the axial direction (direction toward the front end face of the planetary gear).

After the planetary gear mechanism is assembled, the annular protrusion is set so as to contact the front end surface of the planetary gear.

Further, a spherical convex portion is formed on the front end surface of the motor rotation shaft, and a spherical concave portion is formed on the bottom surface of the round hole formed in the center portion of the carrier, and the spherical convex portion and the spherical concave portion are fitted into a curved surface.

Furthermore, an axial bottomed press-fitting hole is provided on the front end surface of the motor rotation shaft, and an axial frusto-conical protrusion is provided on the bottom surface of the round hole formed in the center of the carrier, and the frustoconical protrusion is the bottomed It is inserted into the press-fitting hole and is rotatably supported.

With the configuration as described above, when the motor rotation shaft rotates eccentrically, eccentric rotation of the motor rotation shaft can be suppressed. Vibration and noise caused by eccentric rotation can be reduced.

In addition, this invention is not limited to the above-mentioned Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

1 Motor
11 York
12 Motor rotating shaft
13 Armature
14 Permanent magnet
15 End plate
16 Motor rotating shaft rear sliding bearing
17 Commutator
2 Planetary gear mechanism
21 Sungear
22 Planetary gear
23 Internal gear
24 Career
25 planetary gear support pin
26 Motor rotating shaft front sliding bearing
27 Spherical convex
28 Spherical recess
209 Round trapezoidal protrusion
210 Press-fit hole
20 axis plate
3 One-way clutch
31 Clutch outer
32 Clutch inner
33 Clutch roller
34 Helical spline of clutch outer
4 Pinion shaft
41 Helical spline of pinion shaft
5 Pinion
50 Improved shaft plate
501 disc part
502 bending part
503 Ring-shaped protrusion
6 Magnet switch
61 Plunger
62 Excitation coil
63 Return spring
7 Shift lever
71 Lever pin
72 washer
81 Front frame
82 Pinion shaft sliding bearing

Claims

A motor that generates rotational torque;
A sun gear formed on a motor rotation shaft, an internal gear installed on a front frame, a planetary gear meshing with the sun gear and the internal gear, a planetary gear pin that rotatably supports the planetary gear, and the planetary gear pin are held. A planetary gear mechanism having a carrier;
A one-way clutch arranged in the axial direction of the motor and transmitting the driving force of the motor to the pinion in one direction;
A pinion that is integral with the inner of the one-way clutch and meshes with an engine ring gear;
The carrier is a starter having a round hole formed in a central portion in the axial direction, and rotatably supporting a front end portion of the motor rotation shaft via a sliding bearing,
A starter provided with a shaft plate between the motor rotation shaft and the carrier.
The starter according to claim 1,
The shaft plate is composed of a wear-resistant disk-shaped member, and includes a disk portion having a round hole in a radially central portion, and a plurality of bends provided radially outward at equal intervals on the outer peripheral portion of the disk portion. Each of the bent portions is bent and formed forward in the axial direction (direction toward the rear end surface of the carrier), and has elasticity.
The starter according to claim 1 or 2,
The shaft plate is fixed to the motor rotation shaft, and after the motor rotation shaft enters the sliding bearing, the front end surface of the bent portion and the rear end surface of the carrier are in axial contact with each other. A starter in which the axial position of the plate is determined.
The starter according to any one of claims 1 to 3,
A starter set to a maximum within a range in which the outer periphery of the shaft plate does not contact the outer periphery of the planetary gear support pin 25.
The starter according to any one of claims 1 to 4,
A starter having a ring-shaped protrusion formed axially rearward (in a direction toward the front end surface of the planetary gear) in the circumferential direction of the disk portion.
The starter according to any one of claims 1 to 5,
After the planetary gear mechanism is assembled, the ring-shaped protrusion is set to come into contact with the front end surface of the planetary gear.
The starter according to claim 1,
A starter in which a spherical convex portion is formed on a front end surface of the motor rotation shaft, a spherical concave portion is formed on a bottom surface of a round hole formed in the center portion of the carrier, and the spherical convex portion and the spherical concave portion are curvedly fitted.
The starter according to claim 1,
An axial bottomed press-fitting hole is provided on the front end surface of the motor rotation shaft, and an axial frustum-shaped projection is provided on a bottom surface of the round hole formed in the center of the carrier, and the frustum-shaped projection is the bottomed press-fitting hole. A starter that is inserted into and supported rotatably.