JP2002070703A - Starter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a starter small-sized and light in weight. SOLUTION: The conventional inertia in either of a tubular commutator and an armature coil is reduced, and inertia for an armature 540 is reduced, because a lower coil end 537 and an upper coil end 534 which ensure the first connection and the second connection are interconnected to the end at an armature core 500 through an insulating medium. Accordingly when a pinion gear 21 engages with a ring gear 100, impact torque imparted upon an inertia revolution is reduced and a gear use can be reduced to M=0.9. In addition, a diameter of the bearing can be reduced due to the fact that the reaction R1 produced by an armature bearing 570, the portion which is occupied by the weight in the conventional tubular particles, and the support and distribution of the reaction R1 are reduced from the present 1/L to 1'/L'. This indicates that the number of the teeth in a sun gear 310 is reduced to Zs=8 (the bottom: Φ5.85) and the speed reduction ratio: I=8.25 can be set.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a method for starting an engine,
The present invention relates to a starter having a speed reduction mechanism.

[0002]

2. Description of the Related Art Conventionally, Japanese Patent Application Laid-Open No. 2-238171
As shown in the publication, in a starter with a planetary gear reduction mechanism, a planetary gear reduction ratio is increased to 5.45 at the maximum, thereby providing a starter in which a motor is downsized.

[0003] However, in the above-mentioned conventional one,
The aim is merely to reduce the size of the electric motor by increasing the planetary reduction ratio, but does not consider the size of the entire starter at all. That is, as the reduction ratio increases, the number of teeth of the internal gear of the planetary gear reduction mechanism increases, and the outer diameter of the internal gear increases. As a result, the volume of the planetary gear reduction mechanism increases in proportion to the square of the outer diameter of the internal gear. Therefore, by increasing the reduction ratio, it is possible to reduce the size of the electric motor, but on the contrary, there is a disadvantage that the reduction mechanism becomes large.

Further, by increasing the reduction ratio, the rotational energy E of the armature of the electric motor is E = １ ／ Jw ² , and the energy is obtained by the square of the rotational angular velocity (rotational speed) w with respect to the moment of inertia J of the armature. Since E increases, w of the armature increases due to an increase in the reduction ratio, and a large impact torque is generated at the time of a meshing impact at the starter start characteristic, or at the time of re-meshing during rotation of the starter situation, and the torque transmission component of the starter is increased. It may be damaged. Therefore, the gear specification M (module) as one of the reduction ratio increasing means is reduced,
In the method of increasing the reduction ratio while suppressing the outer diameter of the internal gear, the problem of the strength of the teeth remains, and also in the means of reducing the number of teeth of the sun gear and increasing the reduction ratio. In addition, there is a need to further reduce the diameter of the bearing adjacent to the sun gear (below the root diameter of the sun gear and below the sun gear) from the conventional diameter.

Furthermore, with the increase of the reduction ratio, heat radiation from the S-motor surface decreases and occurs. This can be seen from the fact that heat radiation is generally expressed as E = C (T / 100) ⁴ [kj / m ⁴ h] and is proportional to the area of m ² .

[0006] C is the radiation constant T of the object is the absolute thickness.

An object of the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a starter in which the optimum range of the reduction ratio is clarified and the whole starter can be downsized.

[0008]

DISCLOSURE OF THE INVENTION In order to achieve the above object, according to the present invention, an armature core on which an armature coil is wound;
A starter motor having an armature shaft that rotatably holds the armature core, a drive shaft having a pinion that meshes with a ring gear of the engine,
A speed reduction mechanism mounted between the drive shaft and the armature shaft of the starter motor for reducing the rotation of the armature shaft and transmitting the reduced speed to the drive shaft;
To 10 was adopted.

In this configuration, the reduction ratio of the reduction mechanism is set to 6
Since it is set within the range of 10 to 10, it can be set within the optimum range in view of the volume of the motor and the speed reduction mechanism of the starter, and the size and weight of the starter can be set most effectively.

Further, in addition to the above configuration, the armature coil is connected to upper and lower coil sides housed in a slot of the armature core and one end of the lower layer coil side, A first connection portion substantially parallel to the axial end surface and extending in the shaft direction; and a first connection portion connected to one end of the coil side of the upper layer and substantially parallel to the first connection portion. A configuration having a second connection portion connected to the other end is employed.

In this configuration, the first and second connecting portions are provided substantially parallel to the end face of the armature shaft.
Is connected to the other end of the first connection section,
The first and second connection portions are accommodated in a smaller gap that protrudes in the axial direction than the armature core. Therefore, the inertia of the conventional cylindrical commutator and the armature coil can be reduced, and the inertia mainly as an armature can be reduced.

Further, as shown in FIG. 6 which will be described later, the reaction force R ′ = w′l ′ / L ′ of the sun gear side bearing is calculated by subtracting l ′ / L ′ at the conventional l ′ / L ′ shown in FIG. , The receiving shaft reaction force R ′ is equal to l ′ / weight of the cylindrical commutator.
L ′ can also be reduced.

Therefore, since the bearing diameter can be set smaller than before by reducing the inertia of the armature and the reaction force R 'of the bearing, the gear specifications of the sun gear, M (module), and the number of teeth can be reduced. (Reduction of the tooth root diameter) becomes possible, and when the external diameter of the internal gear is within the following range of the conventional motor external diameter, the reduction ratio I =
6 to 10 settings can be made possible.

Further, as shown in FIGS. 19 and 40, which will be described later, the bearing span L can be shortened by the length of the cylindrical splicer L ', so that the deflection of the shaft can be reduced, and the inclination and twisting of the bearing can be reduced. In addition to this, it is possible to greatly contribute to shortening of the axial length of the motor.

Further, in addition to the above configuration, there is provided an insulator provided between the first connection portion and the armature core and between the first connection portion and the second connection portion, In addition, the brush is slidably disposed on the outer periphery of the second connecting portion.

In this configuration, with respect to the problem of heat resistance, the first and second connection portions are brought close to the side surface of the armature core via an insulator, so that the brush and the second connection portion can be connected to each other. By directly transmitting the resistance heat generated therebetween to the armature core, the problem of reduction in motor heat resistance due to downsizing can be solved.

Further, in addition to the above configuration, a cooling fan for cooling the sliding surface of the starter motor with the brush is provided.

In this configuration, by providing the cooling fan, the resistive heat generated in the brush and the second connection portion can be further reliably cooled.

Further, in addition to the above configuration, a groove for insulation formed between the second connecting portions, which is formed so as to protrude in the rotation direction of the armature shaft, is formed by rotation of the armature core. A configuration that is the cooling fan that generates cooling air is employed.

In this configuration, since the cooling fan is a groove formed between the adjacent second connection portions, the number of components can be reduced without separately attaching a cooling fan.

Further, in addition to the above configuration, the speed reduction mechanism includes a sun gear formed at one end of the armature shaft, a planetary gear provided at one end of the drive shaft and meshing with the sun gear, and meshing with the planetary gear. A structure that is a planetary gear reduction mechanism composed of a fixed internal gear is adopted.

According to this configuration, the size and weight can be significantly reduced.

Further, in addition to the above configuration, there is provided a limiting means for limiting the energization of the starter motor to a predetermined time.

[0024] In this configuration, by having the limiting means, a heat-sensing element such as a bimetal is installed in a portion that receives heat of the motor, such as a motor heat generating portion, for example, a yoke, a field device, a brush device, and an end room. However, by preventing the energization of the starter motor with a protection circuit, an abnormal rise in heat can be suppressed.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Next, a device starter according to the present invention will be described with reference to an embodiment shown in FIGS.

The starter includes a pinion 200 and a planetary gear mechanism 3 that mesh with a ring gear 100 provided in the engine.
00, a housing 400 containing
End frame 7 containing magnet switch 600
00. Further, inside the starter, a motor partition wall 800 is provided between the housing 400 and the motor 500.
And the motor 500 and the end frame 70
0 is defined by the brush holding member 900.

[Description of Pinion 200] FIG. 1 or FIG.
As shown in A and B, the pinion 200 is formed with a pinion gear 210 that meshes with the ring gear 100 of the engine.

On the inner peripheral surface of the pinion gear 210, a pinion helical spline 211 that fits into a helical spline 221 formed on the output shaft 220 is formed. A flange 213 having a larger diameter than the outer diameter of the pinion gear 210 is formed annularly on the side opposite to the ring gear of the pinion gear 210. On the outer circumference of the flange 213, irregularities 214 are formed over the entire circumference, which are larger than the number of external teeth of the pinion gear 210. This unevenness 214
This is for fitting a regulating claw 231 of a pinion rotation regulating member 230 to be described later. The washer 215 has a structure in which an annular portion 216 formed at the rear end of the pinion gear 210 is bent toward the outer peripheral side, so that the washer 215 is rotatable on the rear surface of the flange 213 and does not come off in the axial direction.

On the other hand, the pinion gear 210 is always urged rearward of the output shaft 220 by a return spring 240 composed of a compression coil spring.

[Explanation of the Pinion Rotation Restriction Member 230] At one end of the rotation restriction portion 232, there is provided a restriction claw 231 serving as a restriction portion extending in the axial direction to be engaged with a large number of irregularities 214 formed on the flange 213 of the pinion gear 210. Is provided. The restricting claw 231 is provided with the unevenness 2 of the pinion gear 210.
14 and bent radially inward to form an L-shaped cross section.

The operation of the pinion rotation restricting member 230 will be described. The cord-shaped member 680 is a transmission means for transmitting the operation of the magnet switch 600 to the regulating claw 231. The actuation of the magnet switch 600 pulls the rotation regulating portion 232 downward, and the irregularities of the regulating claw 231 and the flange 213 of the pinion gear 210. 214 is engaged. At this time, one end 236 of the return spring portion 233 is in contact with the regulation shelf 362 for regulating the position, and the return spring portion 233 is bent. Since the regulating claw 231 is engaged with the unevenness 214 of the pinion gear 210, when the pinion gear 210 is to be rotated via the armature shaft 510 of the motor 500 and the planetary reduction mechanism 300, the pinion gear 210 becomes helical spline of the output shaft 220. Advancing along 221. When the pinion gear 210 abuts on the ring gear 100 and the forward movement of the pinion gear 20 is prevented, the pinion rotation regulating member 230 itself is bent by the further rotating power of the output shaft 220, and the pinion gear 210 slightly rotates, and the ring gear is rotated. Engage with 100. When the pinion gear 210 moves forward, the regulating claw 231 is disengaged from the unevenness 214, and the regulating claw 231 is moved to the pinion gear 21.
0, and the front end of the regulating claw 231 hits the rear surface of the washer 215, and the pinion gear 2
10 is prevented from moving backward due to rotation of the ring gear 100 of the engine.

At the same time as the operation of the magnet switch 600 is stopped and the cord-shaped member 680 stops pulling the rotation restricting portion 232 downward, the rotation restricting portion 232 is returned to the original position by the action of the return spring portion 233. .

[Description of Pinion Locking Ring 250] The pinion locking ring 250 is fixed in an annular groove having a rectangular cross section formed around the output shaft 220. The pinion locking ring 250 is formed by rounding a steel material having a rectangular cross section, and has substantially S-shaped unevenness 251 (an example of an engagement means) formed at each of both ends. Are engaged with the other concave portion, and the other convex portion is engaged with the one concave portion.

[Explanation of Planetary Gear Mechanism 300] As shown in FIG.
Is a speed reduction means for reducing the number of rotations of the motor 500 and increasing the output torque of the motor 500. The planetary gear mechanism 300 includes the motor 5
A sun gear 310 (number of teeth Zs = 8) formed on a front outer periphery of an armature shaft 510 (described later) of No. 00 and three pairs of planetary gears 320 (which mesh with the sun gear 310 and rotate around the sun gear 310) Number of teeth Zp =
25), the planetary gear 320 is connected to the sun gear 31
A planetary carrier 330 integrally formed with the output shaft 220 rotatably supported around 0, and a cylindrical and resin internal gear 340 meshing with the planetary gear 320 on the outer periphery of the planetary gear 320
(The number of teeth Zi = 58).

The reduction ratio of the planetary gear reduction mechanism 300 is shown in FIG.
The description will be made based on the characteristic diagram shown in FIG. 5 with the horizontal axis representing the reduction ratio and the vertical axis representing the volume. Here, D is the outer diameter of the yoke 501 of the starter motor shown in FIG. 1, L is the axial length of the yoke 50, and the volume V1 of the starter motor is V
1 = 1/4 で πD ² · L The volume V2 of the planetary gear reduction mechanism 300, the outside diameter d of the internal gear 340, when the axial length 1 of the internal gear 340, and ^{V2 = 1/4 · πd 2} · L. Therefore, the volume affects the starter VT = V1 + V21 / 4 · πD 2 · L1
/ 4 · πd ² · L.

As is apparent from FIG. 25, the volume V1 of the starter decreases as the reduction ratio increases, as shown by the dotted line, whereas the volume V2 of the planetary gear reducer mechanism 300, as shown by the dashed line, is reduced. , Gradually increasing as the reduction ratio is increased. From now on, the total volume VT
Minimizes a certain reduction ratio (around 8) and increases again at a further reduction ratio.

Therefore, in order to reduce the total volume VT of the starter, it is effective to set the speed reduction ratio to 6 to 10. In particular, a reduction ratio around 8 is effective. The planetary gear reducer described above is used for the planetary gear meshing condition, Zs + Zi / N
(Number of planetary gears) = satisfies rectification, reduction ratio I = Zi / Zs
+1 to I = 8.25. Rated output shown in FIG. 25, 12v-0.6kw-3.0kw.24v-2.0
The optimum range shown in the relationship diagram between the motor size and the reduction gear volume at kw to 5.5 kw, and I within the reduction ratio of 6 to 10
= 8.25 is the optimum value. Table 1 shows the results of selecting the use of the gears of the embodiment.

[0038]

[Table 1]

The restricting condition is that the outer diameter of the motor 1 is Φ68 or less than the conventional diameter and the outer diameter Di of the internal gear 22 is Φ58 or less in terms of configuration from the point of view of downsizing the starter. Also, the sun gear 12
Is set to Zs = 8 sheets which can be usually manufactured, and the armature 540
In the stress distribution established from the inertia reduction of
Up to 0.8, the tooth bottom diameter Zs is Φ5 (mm) or more.

The dislocation is set to 0.5.

[Description of Overrunning Clutch 350] In the overrunning clutch 350, the internal gear 340 is supported so as to be rotatable only in one direction (only in a direction in which the engine rotates by receiving rotation of the engine). The overrunning clutch 350 is connected to the internal gear 34.
0, a clutch outer 351 forming a first cylindrical portion integrally formed on a front side of the front side and a rear surface of a center bracket 360 forming a fixed side for covering the front of the planetary gear mechanism 300,
The second clutch opposing the inner periphery of the clutch outer 351
And a roller 353 housed in a roller housing formed to be inclined on the inner peripheral surface of the clutch outer 351.

[Description of Center Bracket 360] The center bracket 360 is disposed inside the rear side of the housing 400. One end of the housing 400 and the center bracket 360 is locked by the housing 400, and the other end is connected by a ring spring 390 locked by the center bracket 360, and a rotational reaction force received by a clutch inner 352 constituting the overrunning clutch 350. Is absorbed by the ring spring 390 and the reaction force is not transmitted directly to the housing 400.

[Description of Planet Carrier 330] The planet carrier 330 has a planetary gear 3 at its rear end.
20 is provided with a flange-shaped protrusion 331 extending in the radial direction to support the same. A pin 332 extending backward is fixed to the flange-shaped protrusion 331.
2 is a planetary gear 320 via a metal bearing 333.
Is rotatably supported.

The planet carrier 330 includes a housing bearing 440 having a front end fixed inside the front end of the housing 400 and a center bracket bearing 370 fixed inside the inner cylindrical portion 365 on the inner periphery of the center bracket 360. , Rotatably supported.

The planet carrier 330 has an annular groove at the front end position of the inner cylindrical portion 365.
, A retaining ring 335 is fitted. A washer 336 rotatably mounted on the planet carrier 330 is provided between the retaining ring 335 and the front end of the inner cylindrical portion 365, and the retaining ring 335 is attached to the washer 33.
The rearward movement of the planet carrier 330 is restricted by abutting the front end of the inner cylindrical portion 365 via 6. Further, the rear end of the center bracket bearing 370 supporting the rear side of the planet carrier 330 includes a flange portion 371 sandwiched between the rear end of the inner cylindrical portion 365 and the flange-shaped protrusion 331. 3
When the 31 abuts on the rear end of the inner cylindrical portion 365 via the flange portion 371, the forward movement of the planet carrier 330 is restricted.

The rear surface of the planet carrier 330 is provided with a concave portion 337 extending in the axial direction.
The front end of the shaft 510 is rotatably supported via a planet carrier bearing 380 disposed therein.

[Description of Housing 400] Housing 4
00 supports the output shaft 220 with a housing bearing 440 fixed inside the front end of the housing 400,
In order to minimize the entry of rainwater or the like from the opening 410, a water blocking wall 460 is provided below the opening 410 to minimize the gap between the housing 400 and the outer diameter of the pinion gear 210 (see FIG. 1). .

[Explanation of Shutter 420] Shutter 420
Is made of a resinous material (eg, nylon) and has an output shaft 2
Ring body 421 that is mounted around pin 20 and is sandwiched between return spring 240 and pinion gear 210
And a water blocking part 422 that opens and closes the opening 410 of the housing 400. As shown in FIG. 12, the water-blocking portions 422 are provided to bend from two sides into two axially extending slide grooves (not shown) formed at the lower portion of the front end of the housing 400. . Thereby, the water blocking part 422 can be moved only in the axial direction with respect to the housing 400 together with the ring body 421. In addition,
A washer 480 is provided between the shutter 420 and the pinion gear 210.

The operation of the shutter 420 is such that when the starter is activated and the pinion gear 210 moves forward along the output shaft 220, the ring body 421 moves forward together with the pinion gear 210. Then, the water blocking part 422 integrated with the ring body 421 moves forward, and opens the opening 410 of the housing 400. When the operation of the starter is stopped and the pinion gear 210 moves rearward along the output shaft 220, the ring body 421 also moves rearward together with the pinion gear 210. Then, the water blocking part 422 integrated with the ring body 421 also moves rearward, and closes the opening 410 of the housing 400. As a result, the shutter 420 serving as the opening / closing means prevents rainwater or the like scattered by the centrifugal force of the ring gear 100 or the like from entering the housing 400 by the water blocking part 422 when the starter is not operated.

[Description of Motor 500] The motor 500
It is configured to be surrounded by a yoke 501, a motor partition wall 800, and a brush holding member 900 described later. The motor partition 8
00 accommodates the planetary gear mechanism 300 with the center bracket 360, and also serves to prevent the lubricating oil in the planetary gear mechanism 300 from entering the motor 500.

The motor 500 includes an armature shaft 510, as shown in FIG.
Armature 540 composed of an armature core 520 and an armature coil 530 which are fixed to and integrally rotated.
And a fixed magnetic pole 550 for rotating the armature 540. The fixed magnetic pole 550 is fixed to the inner periphery of the yoke 501.

[Description of Armature Shaft 510] The armature shaft 510 is rotatably supported by a planet carrier bearing 380 inside the planet carrier 330 and a brush holding member bearing 564 fixed to the inner periphery of the brush holding member 900. You. The front end of the armature shaft 510 is inserted inside the planetary gear mechanism 300, and the sun gear 310 of the planetary gear mechanism 300 is formed around the front end of the armature shaft 510 as described above.

[Description of Armature Core 520] Armature core 5
Reference numeral 20 denotes a structure in which a large number of core plates 521 shown in FIG. 7 are laminated, and an armature shaft 510 is press-fitted and fixed in a hole 522 provided at the center. Core plate 521
Is formed by punching a thin steel plate by press working, and the surface is subjected to insulation treatment. On the inner diameter side of the core plate 521 (around the hole 522), a plurality of punched holes 523 for reducing the weight of the core plate 521 are formed. A plurality (for example, 25) slots 52 for accommodating the armature coils 530 are provided on the outer periphery of the core plate 521.
4 are formed. Further, a fixing claw 525 for fixing the armature coil 530 stored in the slot 524 to the inside of the slot 524 is formed between the slots 524 on the outer peripheral end of the core plate 521. This fixing claw 525 will be described in a fixing means of the armature coil 530 described later.

[Description of Armature Coil 530] In this embodiment, the armature coil 530 uses a plurality of (for example, 25) upper coil bars 531 and the same number of lower coil bars 532 as the upper coil bars 531. A two-layer coil in which the coil bar 531 and the lower coil bar 532 are laminated in the radial direction is employed. Then, each upper coil bar 531 and each lower coil bar 532 are combined, and the end of each upper coil bar 531 and each lower coil bar 532 are combined.
Are electrically connected to each other to form an annular coil.

[Description of Upper Layer Coil Bar 531] The upper layer coil bar 31 is made of a material having excellent electrical conductivity (eg, copper), extends in parallel with the fixed magnetic pole 550, and has a slot 52.
4 and two upper layers forming a second connection portion bent inward from both ends of the upper coil side 533 and extending in the direction perpendicular to the axial direction of the armature shaft 510. And a coil end 534. The upper coil side 533 and the two upper coil ends 534 are formed as separate parts, whether they are integrally formed by cold casting or bent into a U-shape by pressing. It may be formed by joining the upper coil side 533 and the two upper coil ends 534 by a joining technique such as welding.

The upper coil side 533 is shown in FIGS.
As shown in FIG. 11, the lower coil side 536 to be described later is a linear rod having a rectangular cross-section and covered with an upper insulating film 125 (for example, a resin thin film such as nylon or paper) as shown in FIG. At the same time, it is firmly accommodated in the slot 524.

As shown in FIG. 10, the two upper coil ends 5
34, one upper coil end 534 is provided to be inclined forward with respect to the rotation direction, and the other upper coil end 534 is provided to be inclined backward with respect to the rotation direction. The inclination angle of the two upper coil ends 534 with respect to the radial direction is the same inclination angle with respect to the upper coil side 533.
Further, the two upper coil ends 534 are provided in the same shape. Thus, even if the upper coil bar 531 is inverted by 180 ° around the center, the upper coil bar 531 has the same shape as before the inversion. That is, two upper coil ends 5
Since there is no distinction between the armature cores, the workability when assembling the upper coil bar 531 to the armature core 520 is excellent.

Of the two upper coil ends 534, the upper coil end 534 located on the magnet switch 600 side.
Is in direct contact with a brush 910 described later to energize the armature coil 86. Therefore, at least the surface of the upper coil end 534 with which the brush 910 contacts is smoothed. In the starter of the present embodiment, there is no need to provide an independent commutator for energizing the armature coil 530. That is, since an independent commutator is not required, the number of parts can be reduced, and the number of manufacturing steps of the starter can be reduced, so that the manufacturing cost can be suppressed. In addition, since there is no need to dispose an independent commutator in the starter, there is an effect that the size of the starter in the axial direction can be reduced.

Further, the upper coil end 534 is
By directly contacting the upper layer 0, heat generated by sliding contact between the upper coil end 534 and the brush 910 is transmitted from the upper coil end 534 to the upper coil side 533, the armature core 520, the armature shaft 510, and the like. Since the heat capacities of the armature coil 530, the armature core 520, the armature shaft 510, and the like are much larger than those of the conventional independent commutator, the temperature of the sliding contact portion between the upper coil end 534 and the brush 910 is kept low. be able to.

As shown in FIG. 12, the shape of the upper coil end 534 is provided so as to be widened in the radial direction, and the interval between the upper coil ends 534 in the circumferential direction is substantially from the inner circumference to the outer circumference. It is provided constantly. Therefore, the contact area between the upper coil end 534 in contact with the brush 910 and the brush 910 becomes very large. As a result, the heat of the brush 910 is easily transmitted to the coil bar, and the temperature of the brush 910 can be kept very low. FIG. 12 is for the purpose of explaining the shape of the upper coil end 534 for easy understanding, and the number of the upper coil ends 534 does not match the number of the slots 524 in FIG.

As shown in FIG. 12, the shape of the groove 535 at the interval between the upper coil ends 534 in contact with the brush 910 is provided in a substantially spiral shape that retreats in the rotational direction toward the outer diameter. I have. By inclining the shape of the groove 535 in this manner, the brush 910 sequentially contacts from the inside of the upper coil end 534 having a low rotation speed to the outside having a high rotation speed. As a result, it is possible to prevent the brush 910 sliding on the upper coil end 534 from jumping at the upper coil end 534.

When the armature coil 530 rotates,
Centrifugal wind is generated from the inner diameter to the outer diameter by the groove 535 of the upper coil end 534. The centrifugal wind generated by the rotation of each groove 535 of each upper coil end 534 in contact with the brush 910 cools the heat generated by the sliding contact between the brush 910 and the upper coil end 534 and cools the brush powder as described later. Used for emissions. Two upper coil ends 534
Is provided with a small-diameter projection 534a protruding in the axial direction on surfaces facing each other on the outer peripheral side. The protrusion 534a is disposed between the upper coil end 534 and a lower coil end 537 described later, and is fitted into a hole 561 provided in an insulating spacer 560 that insulates the upper coil end 534 from the lower coil end 537. (See FIG. 13).

[Description of Lower Layer Coil Bar 532] Like the upper layer coil bar 531, the lower layer coil bar 532 is made of a material having excellent electrical conductivity (eg, copper), extends parallel to the fixed magnetic pole 550, and is held inside the slot 524. A lower coil side 536 to be formed, and two lower coil ends 537 forming a first connection portion bent inward from both ends of the lower layer coil side 536 and extending in a direction perpendicular to the axial direction of the shaft 510. The lower coil side 536 and the two lower coil ends 537 may be integrally formed by cold casting similarly to the upper coil bar 531.
Even if it is formed by bending into a U-shape by pressing, it is formed by joining a lower coil side 536 and two lower coil ends 537 formed of separate parts by a joining technique such as welding. Is also good.

The insulation between each upper coil end 534 and each lower coil end 537 is ensured by an insulating spacer 560, and the insulation between each lower coil end 537 and the armature core 520 is made of resin (for example, nylon or phenol). (Resin).

The lower coil side 536 is shown in FIGS.
As shown in FIG. 19, with a linear rod having a rectangular cross section, as shown in FIG.
It is firmly housed inside. Note that the lower coil side 536 is
Upper coil side 533 covered with upper insulating film 125
At the same time, it is accommodated in the slot 524 while being covered with the lower insulating film 105 (for example, nylon or paper).

Of the two lower coil ends 537, the lower coil end 537 located on the front side of the starter is provided to be inclined in the direction opposite to the direction of inclination of the upper coil end 534, and the rear lower coil end 537 is also provided. The upper coil end 534 is provided to be inclined in a direction opposite to the inclination direction. The two lower coil ends 537 have the same inclination angle with respect to the radial direction with respect to the lower coil side 536, and the two lower coil ends 537 are provided in the same shape. Thereby, like the upper coil bar 531, the lower coil bar 53
Even if the lower coil bar 10
2 has the same shape as before inversion. That is, since there is no distinction between the two lower coil ends 537, the lower coil bar 53
2 is excellent in workability when assembling to the armature core 520.

The inner peripheral ends of the two lower coil ends 537 are provided with a lower inner extension 539 extending in the axial direction. The outer peripheral surface of the lower inner extension 539 is
0 and an upper inner extension 538 at the end of the upper coil end 534.
And are electrically and mechanically connected by a joining technique such as welding. The inner peripheral surface of the lower inner extension 539 is insulated and spaced apart from the armature shaft 510.

The inner peripheral ends of the two upper coil ends 534 are provided with an upper internal extension 538 extending in the axial direction. The inner peripheral surface of the upper inner extension 538 is superposed on the outer periphery of a lower inner extension 539 provided at the inner end of a lower coil bar 532 described later, and is electrically and mechanically connected by a joining technique such as welding. You. Also, the upper inner extension 5
The outer peripheral surface of the fixing member 380 is in contact with the inner surface of the outer peripheral annular portion 571 of the fixing member 570 press-fitted and fixed to the armature shaft 510 via the insulating cap 580.

[Description of Insulating Spacer 560] The insulating spacer 560 is a thin plate ring made of resin (for example, epoxy resin, phenol resin, or nylon). As shown in FIG. A plurality of holes 561 into which are fitted are formed. Also,
The inner periphery of the insulating spacer 560 has a concave portion 56 into which a lower internal extension 539 inside the lower coil end 537 is fitted.
2 are formed. The hole 56 of the insulating spacer 560
1 and the concave portion 562 are used for positioning and fixing the armature coil 530 as described later.

[Description of Fixing Member 570] Fixing Member 570
Is an iron-made annular body. As shown in FIG. 14, an inner peripheral annular portion 572 press-fitted into the armature shaft 510, and an upper coil end 534 and a lower coil end 537 are prevented from spreading in the axial direction. Regulation ring 57 extending vertically
3 and an outer annular portion 571 that includes the upper inner extension portion 538 of the upper coil end 534 and prevents the inner diameter of the armature coil 530 from spreading due to centrifugal force. In order to ensure insulation between the upper coil end 534 and the lower coil end 537, the fixing member 570 is disposed between the upper coil end 534 and the lower coil end 537 in FIG.
8, a resin-made (for example, nylon) disk-shaped insulating cap 580 is interposed.

The fixing member 57 arranged on the front side of the starter
Reference numeral 0 abuts on the rear surface of the motor partition wall 800 adjacent to the front of the fixing member 570, and also functions as a thrust receiving portion for restricting the forward movement of the armature 540. On the other hand, a fixing member 570 disposed on the rear side of the starter is a brush holder 900 adjacent to the rear of the fixing member 570.
Abuts on the front surface of the armature 540 to act as a thrust receiving portion for restricting the rearward movement of the armature 540.

As described above, since each fixing member 570 for fixing the inner end of the armature coil 530 acts as a thrust receiving portion of the armature 540, it is not necessary to separately provide a thrust receiving portion of the armature 540. . For this reason, the number of parts of the starter can be reduced and the number of assembling steps can be reduced.

[Description of Fixing of Armature Coil 530] As a means for positioning and fixing the upper coil bar 531 and the lower coil bar 532 of the armature coil 530 to the armature core 520, a slot 524 of the armature core 520 is used.
And a fixing claw 525, a hole 561 and a concave portion 562 of the insulating spacer 560, and a fixing member 570 that is press-fitted and fixed to the armature shaft 510.

The slot 524 of the armature core 520 accommodates the upper coil side 533 and the lower coil side 536,
By bending the fixing claw 525 to the inner diameter side as shown by the arrow in FIG. 11, the upper coil side 533 and the lower layer coil side 536 are firmly fixed in each slot 524, and the upper coil side 533 and the lower layer coil Even if the side 536 receives centrifugal force, it is prevented from moving to the outer diameter side. Since the outer peripheral surface of the upper coil side 533 is insulated by the two layers of the lower insulating film 125 and the upper insulating film 105, sufficient insulation can be ensured even if the fixing claws 525 are firmly bent inward.

The concave portion 562 on the inner periphery of the insulating spacer 560
The lower layer coil extension 539 is fitted into the lower layer coil end 537 to position the lower layer coil end 537, and the lower layer coil end 537 moves to the outer diameter side by receiving the centrifugal force applied to the lower layer coil end 537. prevent.

Hole 561 on the outer peripheral side of insulating spacer 560
Are fitted into the protrusions 534a of the upper coil end 534 to position the upper coil end 534 and to prevent the upper coil end 534 from moving to the outer diameter side due to the centrifugal force applied to the upper coil end 534. .

The fixing member 570 holds the joined upper inner extension 538 and lower inner extension 539 from the periphery,
This prevents the inner diameter portion of the armature coil 530 from moving to the outer diameter side due to centrifugal force.

Further, the fixing member 570 regulates the movement of the axial end portions of the joined upper internal extension portion 538 and lower internal extension portion 539, and prevents the axial dimension of the armature coil 530 from becoming longer. If the upper coil end 534 and the lower coil end 537 increase in axial dimension during use of the starter, it is necessary to secure a space for the deformation in the starter in advance, but the fixing member 570 causes the upper coil end 534 and the lower layer Since the coil end 537 is prevented from being lengthened in the axial direction, the starter of this embodiment can eliminate a spare space, and as a result, the axial size of the starter can be reduced.

[Description of Yoke 501] The yoke 501 is
As shown in FIG. 16, a cylindrical body formed by rolling a steel plate,
A plurality of concave grooves 502 that are concave toward the inner periphery extending in the axial direction are formed in the periphery. The concave groove 502 is used for arranging a through bolt and for positioning the fixed magnetic pole 550 on the inner periphery of the yoke 501.

[Description of Fixed Magnetic Pole 550] Fixed magnetic pole 550
In the present embodiment, a permanent magnet is used, and as shown in FIG. 16, a plurality of (for example, six) main magnetic poles 551 and an interpole magnetic pole 552 disposed between each of the main magnetic poles 551 are used. Be composed. Note that a field coil that generates a magnetic force by energization may be used as the fixed magnetic pole 550 instead of a permanent magnet.

The main magnetic pole 551 is positioned by both ends inside the concave groove 502 of the yoke 501 described above.
With the inter-pole 552 disposed between the main poles 551, the fixed sleeve 5 disposed on the inner periphery of the fixed pole 550
With 53, it is fixed inside the yoke 501.

[Explanation of Magnet Switch 600] As shown in FIGS. 1, 17, and 18, the magnet switch 600 is held by a brush holder 900 described later, is arranged in an end frame 700 described later, and has an armature. It is fixed so as to be substantially perpendicular to the shaft 510. Also, the magnet switch 600
The armature shaft 510 is arranged orthogonal to the axial direction.

The magnet switch 600 drives the plunger 610 upward when energized, and the plunger 61
The two contacts (the lower movable contact 611 and the upper movable contact 612) that move integrally with 0 are sequentially brought into contact with the head portion 621 of the terminal bolt 620 and the contact portion 631 of the fixed contact 630. A battery cable (not shown) is connected to the terminal bolt 620.

The magnet switch 600 is formed inside a bottomed cylindrical magnet switch cover 640 made of a magnetic material (for example, iron). The magnet switch cover 640 is formed, for example, by pressing a soft steel plate into a cup shape, and has a hole 641 in the center of the bottom of the magnet switch cover 640 through which the plunger 610 is vertically movably inserted. Also, the magnet switch cover 6
The upper opening of 40 is closed by a stationary core 642 made of a magnetic material (for example, iron).

The stationary core 642 includes an upper large diameter portion 643, a lower middle diameter portion 644, and a lower small diameter portion 645. The outer periphery of the large diameter portion 643 is formed on the upper end of the magnet switch cover 40. The stationary core 642 is fixed in the upper opening of the magnet switch cover 640 by caulking inward. Medium diameter part 6
The upper end of the suction coil 650 is mounted around 44. An upper end of a compression coil spring 660 for urging the plunger 610 downward is mounted on the outer periphery of the small diameter portion 645 of the stationary core 642.

The attraction coil 650 generates a magnetic force when energized and attracts the plunger 610. The attraction coil 650 has a stationary core 6 at its upper end.
A sleeve 651 is attached to the middle diameter portion 644 and covers the plunger 610 in a vertically slidable manner. The sleeve 651 is formed by rolling and processing a thin plate of a non-magnetic material (for example, a copper plate, brass, or stainless steel). An insulating washer 652 made of resin or the like is provided at the upper end and the lower end of the sleeve 651. An insulating film (not shown) made of a thin resin (for example, cellophane, nylon film) or paper is wound around the sleeve 651 between the two insulating washers 652, and a thin enamel wire is wound around the insulating film. Are wound a predetermined number of times to form a suction coil 650.

The plunger 610 is made of a magnetic metal (for example, iron) and has a substantially cylindrical shape having an upper small-diameter portion 613 and a lower large-diameter portion 614. The small-diameter portion 613 has the lower end of the compression coil spring 660 attached thereto, and the relatively-diameter-long large-diameter portion 614 is held in the sleeve 651 so as to be movable in the vertical direction.

A plunger shaft 615 extending above the plunger 610 is fixed above the plunger 610. The plunger shaft 615 protrudes upward from a through hole provided at the center of the stationary core 642. An upper movable contact 612 is provided above the stationary core 642 of the plunger shaft 615.
Are slidably inserted in the vertical direction along the plunger shaft 615. This upper movable contact 612 corresponds to FIG.
As shown in FIG. 1, a retaining ring 616 attached to the upper end of the plunger shaft 615 restricts the plunger shaft 615 from moving upward from the upper end.

As a result, the upper movable contact 612 is vertically slidable along the plunger shaft 615 between the retaining ring 616 and the stationary core 642. The upper movable contact 612 is constantly urged upward by a contact pressure spring 670 formed of a leaf spring attached to the plunger shaft 615.

The upper movable contact 612 is made of a metal having excellent conductivity such as copper. When both ends of the upper movable contact 612 move upward, the upper movable contact 612 comes into contact with two contact portions 631 provided on the fixed contact 630. Further, the respective lead wires 910a of the pair of brushes 910 are electrically and mechanically fixed to the upper movable contact 612 by caulking, welding, or the like.
Further, in the groove of the upper movable contact 612, the end of the resistor 617 serving as a plurality (two in this embodiment) of limiting means is provided.
It is inserted and is fixed electrically and mechanically. In addition, although each lead wire 910a of the brush 910 is electrically and mechanically fixed to the upper movable contact 612 by caulking, welding, or the like, the upper movable contact 612 and each lead wire 910a of the brush 910 are connected to each other. They may be formed integrally.

The resistor 617 is for rotating the motor 500 at a low speed at the initial stage of start-up of the starter, and is formed by winding a plurality of metal wires having a large resistance value. A lower movable contact 611 located below the head 621 of the terminal bolt 620 is fixed to the other end of the resistor 617 by caulking or the like.

The lower movable contact 611 is made of a highly conductive metal such as copper, and contacts the upper surface of the stationary core 642 when the magnet switch 600 is stopped and the plunger 610 is located below, and the lower movable contact 611 is connected to the resistor 617. Moves upward with the movement of the plunger shaft 615,
The upper movable contact 612 is provided to contact the head 621 of the terminal bolt 620 before contacting the contact portion 631 of the fixed contact 630.

The string-shaped member 6 is provided on the lower surface of the plunger 610.
A sphere 681 provided at the rear end of 80 (for example, a wire)
Is provided. A female screw 683 is formed on the inner peripheral wall of the recess 682. This female screw 6
The fixing screw 684 for fixing the spherical body 681 in the concave portion 682 is screwed into the 83. The fixing screw 684 is a female screw 6
The length of the cord-like member 680 is also adjusted by adjusting the amount of screwing into the 83 by 25. Note that the length of the string-shaped member 680 is adjusted by moving the plunger shaft 615 upward and moving the lower movable contact 611 to the terminal bolt 620.
When the pinion gear 210 is brought into contact with the pinion gear 210, the regulating claw 231 of the pinion rotation regulating member 230 is adjusted so as to fit into the unevenness 214 on the outer periphery of the pinion gear 210. The female screw 683 and the fixing screw 684 form an adjustment mechanism.

[Description of End Frame 700] As shown in FIG. 19, the end frame 700 is a magnet switch cover made of resin (for example, phenol resin) and houses the magnet switch 600 therein.

On the rear surface of the end frame 700, a spring holding column 710 for holding a compression coil spring 914 for urging the brush 910 forward is provided to protrude forward according to the position of the brush 910.

Further, the compression coil spring 914 is connected to the plunger 6 of the magnet switch 600 as shown in FIG.
It is arranged on the outer peripheral side in the radial direction with respect to the axial direction of 10.

The terminal bolt 620 is connected to the end frame 70.
0 is inserted from the inside of the end frame 700 and protrudes rearward of the end frame 700.
0 is provided with a head portion 621 that abuts on the inner surface. The caulking washer 622 is attached to the terminal bolt 620 protruding rearward of the end frame 700,
Terminal bolt 620 is fixed to end frame 700. A fixed contact 630 made of copper is fixed to the front end of the terminal bolt 620 by caulking. Fixed contact 63
0 includes one or more (two in this embodiment) contact portions 631 located at the upper end inside the end frame 700, and the lower surface of the contact portions 631
The upper surface of the upper movable contact 612 that moves up and down by the operation of 00 is provided so as to be able to abut.

[Explanation of Brush Holder 900] The brush holder 900 is provided between the inside of the yoke 501 and the end frame 70.
In addition to the role of partitioning the inner end of the armature shaft 510 and rotatably supporting the rear end of the armature shaft 510 via a brush holder bearing 564, the role of a brush holder, the role of holding the magnet switch 600, and the cord-shaped member 680 Serves to hold the pulley 690 that guides the vehicle. The brush holder 900 has a hole (not shown) through which the string member 680 passes.

The brush holder 900 is a partition formed by casting a metal such as aluminum by a casting technique. As shown in FIGS. 35 to 37, a plurality of brush holding holes 911 and 912 for holding the brush 910 in the axial direction are provided. In the embodiment, two are provided on the upper side and two are provided on the lower side. Upper brush holding hole 91
Reference numeral 1 denotes a hole for holding a brush 910 that receives a positive voltage. The upper brush holding hole 911 holds the brush 910 via an insulating cylinder 913 made of resin (for example, nylon or phenol resin). 20 is a sectional view taken along line AA of FIG. 20, and FIG. 22 is a sectional view taken along line BB of FIG. 20). The lower brush holding hole 912 is a hole for holding a brush 910 that is grounded.
12 holds the brush 910 directly inside the hole.

As described above, since the brush 910 is held by the brush holder 900, there is no need to provide an independent brush holder in the starter. For this reason,
The number of parts of the starter can be reduced, and the number of assembling steps can be reduced.

Further, the brush 910 is provided with the compression coil spring 9.
14, the front end face is urged to the rear face of the upper coil end 534 on the rear side of the armature coil 530.

The lead wire 91 of the upper brush 910
Oa is electrically and mechanically coupled to the upper movable contact 612 moved by the magnet switch 600 by a joining technique such as welding or caulking. Further, the lead wire 910a of the lower brush 910 is caulked into a concave portion 920 formed on the rear surface of the brush holder 900, and is electrically and electrically connected.
And are mechanically connected. In this embodiment, one pair of lower brushes 910 is provided, one pair of lower brushes 910 is joined to one lead wire 910a, and the center of the lead wire 910a is a brush holder. 900 is crimped in a recess 920 on the rear surface.

On the rear surface of the brush holder 900, two pedestals 930 with which the front surface of the magnet switch 600 abuts.
And two fixing columns 940 that hold the periphery of the magnet switch 600.

The pedestal 930 is provided so as to match the outer shape of the magnet switch 600 in order to abut the magnet switch 600 having an outer diameter of a cylindrical shape. Further, the two fixed columns 940 are formed by caulking the rear ends of the magnet switches 600 inward in a state where the magnet switches 600 are in contact with the pedestals 930, respectively.
Holding.

Under the rear surface of the brush holder 900, the moving direction of the string member 680 is indicated by the magnet switch 600.
A pulley holding portion 950 that holds a pulley 690 that converts the vertical direction from the vertical direction to the axial direction is formed.

A holding section 96 for holding a temperature switch (not shown) for overheating protection is provided on the rear surface of the brush holding body 900.
0 is provided. The holding section 960 holds the temperature switch between the upper brush holding hole 911 and the lower brush holding hole 912 and near the magnet switch 600. When the temperature switch reaches a predetermined temperature, the temperature switch turns off the magnet switch 600,
The power supply to the starter motor is stopped to protect the starter.

The front surface of the brush holder 900 is
It is provided close to the rear surface of the upper coil end 534 that contacts the zero. Therefore, centrifugal wind generated by rotation of the groove 535 between the upper coil ends 534 is forcibly guided in the outer radial direction. That is, centrifugal air is generated between the rear upper coil end 534 and the brush holder 900.

As shown in FIG. 24, the starter has a cooling air passage for guiding air to the inside between the upper coil end 534 on the rear side and the brush holder 900 and discharging centrifugal wind to the outside of the starter. Is formed.

This cooling air passage is provided in the brush holder 900.
An inlet 970 which is opened at an inner peripheral portion of the end frame 70 and guides the air inside the end frame 700 to the inside between the upper coil end 534 on the rear side and the brush holder 900;
0, and the main magnetic pole 551 and the main magnetic pole 55 in the yoke 501 are opened.
1 and a brush holder communicating hole 980 communicating with the gap between
And the main magnetic pole 5 communicating with the brush holder communicating hole 980.
A gap 590 between the main magnetic pole 551 and the main magnetic pole 551, and a gap 5
90 and a center bracket 360 that communicates with the motor partition wall communication hole 810.
, And the inside of the housing 400. Then, the air sucked from the opening 410 of the housing 400 is supplied to the inside of the housing 400 → the cutout 364 on the upper side of the center bracket 360 → the communication hole 810 of the motor partition wall → the gap 590 between the main magnetic poles 551 → the communication hole 980 of the brush holder → the end Inside the frame 700 → introduction port 970
Through the rear upper coil end 534 and the brush holder 9
Lead inside between 00.

The centrifugal air generated between the upper coil end 534 on the rear side and the brush holder 900 cools the sliding surface of the brush 910 and its periphery, and then the yoke 501 along with the brush powder generated on the sliding surface. Discharge hole 50 provided at the lower end of the
3 to the outside of the starter.

As described above, the upper coil end 534 acting as a commutator acts as a centrifugal fan to generate centrifugal air, thereby causing the upper coil end 53 acting as a commutator.
The temperature of the sliding portion between the brush 4 and the brush 910 can be kept low. Also, brush powder generated by the abrasion of the brush 910 is carried to the discharge hole 503 by centrifugal wind, and
Since it is discharged from the starter to the outside of the starter, the occurrence of a failure or the like due to brush powder is prevented.

[Operation of Embodiment] Next, the operation of the starter will be described with reference to the electric circuit diagrams of FIGS. 23A to 23C.

When the occupant sets the key switch 10 at the start position, electricity is supplied from the battery 20 to the attraction coil 650 of the magnet switch 600. When the attraction coil 650 is energized, the plunger 610 is attracted to the magnetic force generated by the attraction coil 650, and the plunger 610 rises upward from a lower position.

When the plunger 610 starts to rise, the upper movable contact 6 is moved with the rise of the plunger shaft 615.
12 and the lower movable contact 611 rise, and the rear end of the string-like member 680 also rises upward. String member 680
When the rear end rises, the front end of the string-shaped member 680 is pulled downward, and the pinion rotation regulating member 230 descends. The lower movable contact 611 is moved to the head 6
21 (see FIG. 23A). 25 and the voltage of the battery 20 are applied to the terminal bolt 620, and the voltage of the terminal bolt 620 is changed from the lower movable contact 611 to the resistor 61.
7 → upper movable contact 612 → transmitted to upper brush 910 via lead wire 910a. That is, the resistor 617
Is transmitted to the armature coil 530 via the upper brush 910. Then, the lower brush 910
Is always grounded via the brush holder 900, so that the armature coil 530 formed into a coil by combining each upper coil bar 531 and each lower coil bar 532 is supplied with a low voltage. Then, armature coil 530 generates a relatively weak magnetic force, and this magnetic force acts on (attracts or repels) the magnetic force of fixed magnetic pole 550, and armature 540 rotates at a low speed. Armature shaft 51
When 0 rotates, the planetary gear 320 of the planetary gear mechanism 300 is rotationally driven by the sun gear 310 at the front end of the armature shaft 510. Planetary gear 3
20 is the ring gear 1 via the planet carrier 330.
In the case where a rotational torque in the direction of driving the rotation of the internal gear 340 is applied to the internal gear 340, the rotation of the internal gear 340 is restricted by the operation of the overrunning clutch 350. That is, since the internal gear 340 does not rotate 5, the planet carrier 320 rotates at a reduced speed due to the rotation of the planetary gear 320. When the planet carrier 330 rotates, the pinion gear 210
However, since the rotation of the pinion gear 210 is restricted by the pinion rotation restricting member 230, the pinion gear 210 moves forward along the helical spline 221 of the output shaft 220.

As the pinion gear 210 advances, the shutter 420 also advances and opens the opening 410 of the housing 400. When the pinion gear 210 advances, the pinion gear 210 completely meshes with the ring gear 100 of the engine, and thereafter, when the pinion gear 210 advances,
The regulating claw 231 is disengaged from the unevenness 214 of the pinion gear 210, and then the front end of the regulating claw 231 is
0 falls behind the washer 215 provided on the rear surface.

On the other hand, with the pinion gear 210 advanced, the upper movable contact 612 is brought into contact with the contact portion 63 of the fixed contact 630.
Contact 1 Then, the battery voltage of the terminal bolt 620 is directly transmitted to the upper brush 910 via the upper movable contact 612 → the lead wire 910a. That is, a high current flows through the armature coil 530 including the upper coil bar 531 and the lower coil bar 532, and the armature coil 530 generates a strong magnetic force to rotate the armature 540 at high speed.

The rotation of the armature shaft 510 is reduced by the planetary gear mechanism 300 to increase the rotational torque, thereby driving the planet carrier 330 to rotate. At this time, the front end of the pinion gear 210 abuts on the pinion locking ring 250, and rotates integrally with the planet carrier 330.

Since the pinion gear 210 meshes with the ring gear 100 of the engine, the pinion gear 210 drives the ring gear 100 to rotate, thereby rotating the output shaft of the engine.

Next, when the engine is started and the ring gear 100 of the engine rotates faster than the rotation of the pinion gear 210, a backward force is generated in the pinion gear 210 by the action of the helical spline. However, the rotation restricting claw 231 that has fallen to the rear of the pinion gear 210 prevents the pinion gear 210 from retreating, prevents the pinion gear 210 from coming off early, and starts the engine reliably (see FIG. 23B).

Further, when the ring gear 100 of the engine is rotated faster than the rotation of the pinion gear 210 by starting the engine, the rotation of the ring gear 100 drives the pinion gear 210 to rotate. Then, the rotation torque transmitted from the ring gear 100 to the pinion gear 210 is transmitted to the pins 332 that support the planetary gear 320 via the planet carrier 330. That is, the planetary gear 320 is driven by the planet carrier 330. Then, the internal gear 34
0, the reverse running torque is applied when starting the engine.
Allow rotation of 00. That is, when a torque is applied to the internal gear 340 in a direction opposite to that at the time of engine start, the roller 353 of the overrunning clutch 350 is disengaged outside the concave portion 355 of the clutch inner 352, and the rotation of the internal gear 340 becomes possible. Become.

That is, when the engine is started, the relative rotation of the ring gear 100 of the engine to rotate the pinion gear 210 is absorbed by the overrunning clutch 350, and the armature 540 is not rotationally driven by the engine.

When the engine is started, the occupant removes the key switch 10 from the start position, and the power supply to the attraction coil 650 of the magnet switch 600 is stopped. When the energization of the suction coil 650 is stopped, the plunger 610 is returned downward by the action of the compression coil spring 660.

Then, the upper movable contact 612 becomes the fixed contact 6
30, the lower movable contact 611 also separates from the head 621 of the terminal bolt 620, and the power supply to the upper brush 910 stops.

When the plunger 610 is returned downward, the pinion rotation restricting member 230 is returned upward by the action of the return spring portion 236 of the pinion rotation restricting member 230, and the restricting claw 231 is disengaged from behind the pinion gear 210. . Then, the pinion gear 210 is returned to the return spring 24.
As a result, the pinion gear 210 is disengaged from the ring gear 100 of the engine, and the rear end of the pinion gear 210 contacts the flange-shaped protrusion 222 of the output shaft 220. That is, the pinion gear 210 is returned before the starter is started (see FIG. 23C).

Further, when the plunger 610 is returned downward, the lower movable contact 611 contacts the upper surface of the stationary core 642 of the magnet switch 600, and the lead wire 910a of the upper brush 910 is connected to the upper movable contact 612 → Resistor 617 → lower movable contact 611 → stationary core 642 → magnet switch cover 6
Conduction is performed in the order of 40 → brush holder 900. That is, the upper brush 910 and the lower brush 910 are short-circuited via the brush holder 900. On the other hand, armature 540
, An electromotive force is generated in the armature coil 530. Then, the electromotive force is short-circuited via the upper brush 910, the brush holder 900, and the lower brush 910, so that a braking force is given to the inertial rotation of the armature 540. As a result, the armature 540 stops quickly.

[Effects of Embodiment] In the above embodiment,
Since the lower coil end 537 and the upper coil end 534 forming the first and second connection portions are in contact with the end face of the armature core 500 via an insulator, the inertia of the conventional cylindrical commutator and armature coil is reduced. Is reduced and armature 5
At 40, the inertia is greatly reduced. Therefore, when the pinion gear 21 meshes with the ring gear 100, the impact torque at the time of inertia rotation or the like is reduced, the gear use can be reduced to M = 0.9, and the reaction force R1 of the armature bearing 570 is reduced to the conventional cylindrical shape. The weight distribution of the particles and the support distribution of the reaction force R1 are 1 / L of the conventional one.
To 1 ′ / L, the bearing diameter can be reduced. From this, the number of teeth of the sun gear 310 is set to Zs = 8
(The tooth bottom diameter Φ5.85), and the reduction ratio I = 8.25 can be set and set. Therefore, as shown in FIG. 25, the motor volume is I = 8.
25, and the size was reduced.

The grooves 5 at the intervals between the upper coil ends 534 are also provided.
35, when the armature coil 530 rotates, centrifugal wind is generated from the inner diameter to the outer diameter by the groove 535 of the upper coil end 534. Then, the air sucked from the opening 410 of the housing 400 in each groove 535 of each upper coil end 534 that comes into contact with the plush 910 is removed from the inside of the housing 400 →
Notch 364 on the upper side of center bracket 360 → motor partition wall communication hole 810 → gap 590 between main magnetic poles 551 → brush holder communication hole 980 → in end frame 700 → via rear inlet coil end 534 via inlet 970 It leads to the inside between the brush holder 900.

The centrifugal air generated between the upper coil end 534 on the rear side and the brush holder 900 cools the sliding contact surface of the brush 910 and its periphery, and then the yoke 501 along with the brush powder generated on the sliding contact surface. Discharge hole 50 provided at the lower end of the
3 to the outside of the starter.

As described above, the upper coil end 534 acting as a commutator acts as a centrifugal fan to generate centrifugal air, thereby causing the upper coil end 53 acting as a commutator.
The temperature of the sliding portion between the brush 4 and the brush 910 can be kept low.

Thus, at the reduction ratio I = 8.25, the heat radiation shortage due to the decrease in the motor surface area can be eliminated by the air cooling effect, and the starter can be downsized with sufficient heat resistance.

As another example, as means for sensing the heat generated by the motor and restricting the current to the starter motor 500 to a predetermined time, the heat sensing portion, the brush device 900, the field device 550, the yoke 501, the end A heat sensitive element such as a bay metal is arranged near the frame 700, and when the motor temperature reaches the set temperature, the power supply to the attraction coil 650 of the magnet switch 600 is turned off, and a protection device that cuts off the power supply to the starter motor is used. You may. Bimetal
It is also possible to use a self-holding type which is a normal type and holds an open state when opened. When the protection device is used together, an armature having a substantially spiral rectifying piece in the armature core does not need to be used in combination, and a conventional armature may be used. Further, a timer device may be incorporated in the starter operation circuit to limit the energization time to the starter.

Accordingly, the present invention provides a high reduction ratio range I = 6, which has not been conventionally implemented, and an optimum range of 6 to
By clarifying 10 and setting I = 8.25, the starter was significantly reduced in size and weight compared to the conventional starter.

As shown in the embodiment, since the size of the starter can be significantly reduced, a method for mounting the starter which has not been used in the related art is employed. Numerous effects occur, including the possibility of use.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing Embodiment 1 of a starter of the present invention.

FIGS. 2A and 2B are a front view and a partial cross-sectional side view when a pinion rotation restricting member is assembled to a pinion portion.

FIG. 3 is a rear view of the center bracket.

FIG. 4 is a side sectional view of a center bracket.

FIG. 5 is a front view of a center bracket.

FIG. 6 is a side sectional view of the armature.

FIG. 7 is a plan view of a core plate.

FIG. 8 is a side view of the upper coil bar.

FIG. 9 is a front view of the upper coil bar.

FIG. 10 is a schematic perspective view showing an arrangement state of an upper coil bar and a lower coil bar.

FIG. 11 is a sectional view of an upper coil side and a lower coil side accommodated in a slot.

FIG. 12 is a front view of an end of an upper coil immersed in an armature core.

FIG. 13 is a front view of an insulating spacer.

FIG. 14 is a side sectional view of a fixing member.

FIG. 15 is a front view of the insulating cap.

FIG. 16 is a front view of the yoke.

FIG. 17 is an exploded perspective view of a plunger and a fixed contact of the magnet switch.

FIG. 18 is a perspective view showing a plunger of the magnet switch.

FIG. 19 is a sectional view showing an end frame and a brush spring.

FIG. 20 is a front view showing a brush holder.

FIG. 21 is a sectional view taken along the line AA of FIG. 26;

FIG. 22 is a sectional view taken along the line BB of FIG. 26;

FIGS. 23A, 23B and 23C are electrical diagrams showing the operating state of the pinion.

FIG. 24 is a side sectional view of a starter showing a cooling air passage.

FIG. 25 is a characteristic diagram showing a relationship between a volume and a reduction ratio.

FIG. 26 is a sectional view showing a conventional armature.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) H02K 7/116 H02K 7/116 5H623 9/28 9/28 A 11/00 23/68 23/68 11 / 00 E (72) Inventor Masanobu Omi 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso, Inc. Reference) 5H603 AA09 AA12 AA15 BB01 BB04 BB12 CA02 CA05 CB02 CB03 CB04 CB11 CB18 CB19 CC03 CC17 CD02 CE02 CE13 EE01 FA21 FA24 FA29 5H604 BB01 BB07 CC02 CC05 CC13 CC16 DA15 DA19 DB02 DB03 P0301BB13 CCB CCB CCB CCB CCB CCB CC DD02 DD09 EE21 EE33 FF02 FF04 JJ04 5H609 BB06 BB12 PP02 PP05 PP06 PP07 PP09 PP13 PP17 QQ02 QQ11 RR02 RR42 5H611 AA01 AA03 BB03 PP01 QQ04 SS01 UA01 5H623 BB07 GG03 GG11 LL14

Claims (5)

[Claims] A starter motor having an armature core on which an armature coil is wound, an armature shaft rotatably holding the armature core, a drive shaft having a pinion meshed with a ring gear of an engine, and the drive shaft And a single reduction mechanism mounted between the armature shaft of the starter motor and reducing the rotation of the armature shaft and transmitting the rotation to the drive shaft. A planetary gear reduction mechanism including a sun gear formed at one end, a planetary gear provided at one end of the drive shaft and meshing with the sun gear, and an internal gear forming a fixed side meshing with the planetary gear; and Reducer ratio of reduction mechanism from 6 to 10 A starter characterized by: 2. The starter according to claim 1, wherein the armature coil is connected to upper and lower coil sides housed in a slot of the armature core and one end of the lower layer coil side, A first connecting portion that is substantially parallel to the axial end surface of the armature core and extends in the shaft direction; and a first connecting portion that is connected to one end of a coil side of the upper layer and that is substantially parallel to the first connecting portion and a first connecting portion. And a second connection portion connected to the other end of the connection portion. 3. The starter according to claim 1, wherein a cooling fan for cooling a sliding surface of the starter motor with a brush is provided. 4. The starter according to claim 3, wherein an insulating groove formed between the second connection portions and formed in the armature shaft so as to protrude in a rotation direction of the armature shaft is provided with an armature core. A starter for generating cooling air by rotation of the starter. 5. The starter according to claim 1, further comprising a limiter for controlling the power supply to said starter motor for a predetermined time.