JP2947025B2 - Starter - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a starter used for starting an internal combustion engine.

[0002]

2. Description of the Related Art Conventionally, a starter used for starting an internal combustion engine is configured as shown in FIG. The conventional starter shown in FIG. 3 has an armature 2 of a DC motor and an overfitted slidably on an output rotary shaft 3.
The running clutch 4 and the rotational force of the DC motor are reduced by the sun gear 5a, the planetary gear 5b, and the internal gear 5c on the armature 2 to reduce the rotational force of the DC motor.
And a planetary gear mechanism 5 for transmitting to the clutch outer 4a via the output rotary shaft 3. Further, a shift lever 8 is provided for sliding the overrunning clutch 4 on the output rotary shaft 3, and this shift lever 8 is provided for a plunger 6b of a magnet switch 6 disposed on the side of the DC motor. One end is engaged with the joint 6a, and the other end is engaged with the overrunning clutch 4 and the annular member 7 attached thereto.

As another starter, Japanese Utility Model Laid-Open No.
As shown in FIG. 1 of Japanese Patent Application Laid-Open No. 3-147565, an overrunning clutch is built in an inner peripheral portion of an armature rotating shaft 16 of a DC motor 15, and a planetary gear reduction mechanism 3 is provided.
9, there is a starter (hereinafter referred to as a coaxial starter) in which the armature rotary shaft 16 of the DC motor and the magnet switch 43 are arranged on the same axis.

[0004]

However, the conventional starter shown in FIG. 3 has a low torque and high rotation speed in response to a demand for downsizing the starter in recent years due to an increase in engine accessories. Although the size has been reduced by combining the DC motor and the planetary gear reduction mechanism 5, the overrunning clutch 4 is disposed at the subsequent stage of the planetary gear reduction mechanism 5 to which a large torque load is applied, so that a strong clutch is required. Required, and there is a problem that the clutch cannot be downsized.

In the coaxial starter described above, the outer and inner shafts 27, which are the armature rotating shafts 16 constituting the clutch, are supported at one end through the same bearing 28, and at the other end. Since the structure is supported by separate members via the bearings 20 and 30, inclination tends to occur between the center axes of the outer and inner members, which causes a problem that clutch performance during high-speed rotation is reduced.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a starter capable of reducing the size of a clutch and maintaining the clutch performance up to a high-speed rotation range.

[0007]

In order to achieve the above object, according to the present invention, a driving side member integrated with an armature is provided.
When the real armature shaft in having a gear at the tip protrudes at both sides in the axial direction from the raw Dogawa member performs only transmission of torque to the armature shaft from raw Dogawa member
Ku, the overrunning clutch having a torque transmission member abuts against the outer periphery of the armature shaft, the A
An output rotating shaft to which driving force is transmitted from the armature shaft, a pinion gear spline-coupled to the output rotating shaft and meshing with a ring gear of the internal combustion engine ;
A speed reduction mechanism for transmitting the output rotation shaft by decelerating the rotation of the gear and meshing said armature shaft of Yafuto, said protruding from the driving-side member to both sides in the axial direction Amachashi
The arcs projecting from both projecting portions of the shaft to both axial sides .
The configuration is characterized by comprising first and second bearings respectively supporting the respective projecting portions of the mach shaft , and an armature having the overrunning clutch provided therein.

According to a second aspect of the present invention, torque is applied only from the driving side member to the driven side member between the driving side member and the driven side member which protrudes axially from both sides in the axial direction and has a gear at the tip. An overrunning clutch having a torque transmitting member for transmitting, an output rotating shaft to which a driving force is transmitted from the driven side member, a pinion gear spline-coupled to the output rotating shaft and meshing with a ring gear of the internal combustion engine;
A speed reduction mechanism that meshes with the gear of the driven side member to reduce the rotation of the driven side member and transmits the rotation to the output rotation shaft; and a reduction mechanism located on both sides of the torque transmission member in the axial direction of the driven side member, and Third and fourth bearings disposed between the driven member and the driving member, and an armature having the overrunning clutch and the third and fourth bearings therein. The configuration is characterized by the provision.

[0009]

According to the present invention, according to the first aspect of the present invention, by disposing the overrunning clutch in the armature, the overrunning clutch is interposed before the deceleration, and the load capacity of the clutch is greatly reduced. As a result, the pinion gear is rotated from the ring gear of the internal combustion engine, and the armature is reduced via a reduction mechanism.
When the shaft is rotated at high speed, both ends of the armature shaft projecting in the axial direction from the driving member are supported by the first and second bearings, and between the driving member and the armature shaft. Since the torque transmission member is located, the armor
The central axis of the tea shaft and the driving side member is less likely to shift,
There is an effect that the clutch performance can be maintained up to the high speed rotation range.
Also, the member with which the torque transmitting member abuts is replaced with a solid armature.
The shaft from the torque transmission member
There is an effect that it can be reliably received.

According to the second aspect, similarly to the first aspect, an overrunning clutch is interposed in the stage prior to deceleration, and the load capacity of the clutch can be greatly reduced, so that the clutch can be downsized. Further, since both members are supported by third and fourth bearings between the driven side member and the driving side member, the two members are located on both sides of the torque transmitting member in the axial direction of the driven side member. As in the case of 1, there is an effect that the center axes of the driven side member and the driving side member are hardly shifted.

According to the third aspect, both ends of the driven member protruding in the axial direction from the driving member are supported by the first and second bearings, and a third member is provided between the driven member and the driving member. ,
Since both members are supported by the fourth bearing, the center axes of the driven-side member and the driving-side member are more unlikely to shift, and there is an effect that the clutch performance can be maintained up to the high-speed rotation range. According to claim 4, since the inner member forming the driven side member has no other member interposed in the inner member, the inner member becomes a solid shaft having high rigidity, and thus the outer diameter of the inner member can be further reduced. There is an effect that the centrifugal force of the roller arranged in the outer formed can be reduced.

According to a fifth aspect of the present invention, the plurality of bearings are used as knees.
Since a dollar bearing or a sintered metal impregnated with oil is used, the outer diameter of the bearing can be reduced, and the clutch disposed in the armature can be downsized. According to the sixth aspect, the driven member is a high-strength member to which heat treatment is applied, so that there is an effect that the durability of the driven member can be improved against centrifugal force during high-speed rotation.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to an embodiment shown in the drawings. FIG. 1 is a sectional view showing an embodiment of the present invention.
FIG. 2 is a sectional view taken along line AA of FIG. In the figure, 1 is a starter motor, and 6 is a magnet switch having a return spring (not shown). On the inner periphery of the cylindrical stator 21 of the starter motor 1, an iron core 22 around which an exciting coil 22a is wound is mounted. The armature 2 that is driven to rotate is disposed on the inner peripheral side of the iron core 22.

The armature 2 includes a driving-side member 11 made of a high-strength material subjected to a hollow heat treatment, an armature core 14 disposed on the outer periphery of the driving-side member 11, and an outer peripheral portion of the armature core. It comprises a buried armature coil 14a and a driven-side member 13 which is solid and has a small inner diameter and which has projections on both sides in the axial direction from the driving-side member 11. A plurality of cam surfaces 11a are formed radially on the inner peripheral surface of the hollow portion of the driving-side member 11.

One of the driven side members 13 is the rear bracket 1
Nine first bearings 15 rotatably supported. A commutator 23 is provided on one of the driven side members 13.
Is fixed by a resin member 23a.
A brush 24 is slidably provided on the outer periphery of the brush. A sun gear 5 a is formed on the outer periphery of the other portion of the driven side member 13. On the other side of the driven side member 13, a rotation output shaft 3 is disposed on the same axis as the driven side member 13, and the starter motor which is one end side of the rotation output shaft 3 is provided. One side is rotatably supported by a second bearing 16 provided between the other side of the driven side member 13, and the other side of the driven side member 13 is connected to a front bracket 25 via another bearing 26. It is pivoted.

At one end of the rotary output shaft 3, there is formed a flange-shaped projection 3a projecting in the outer peripheral direction.
A plurality of through holes 3b are provided in the protruding portion 3a in the circumferential direction, and pins 5d engaging with the through holes 3b are arranged. These pins 5d are connected to the planetary gear 5 via bearings 5e.
b is rotatably held. These planet gears 5b mesh with the outer periphery of the sun gear 5a.

Further, an internal gear 5c is arranged on the outer periphery of the flange-shaped protrusion 3a. The internal gear 5c has a tooth portion that meshes with the planetary gear 5b in about half of the inner circumference on the armature 2 side. Therefore,
The sun gear 5a, the planetary gear 5b, and the internal gear 5
The speed reduction mechanism 5 is constituted by c. Further, on the inner periphery of the internal gear 5c, for example, eight notches (not shown) are formed at equal intervals in the circumferential direction, which are located on the side opposite to the tooth portion.

A disk 31 is inserted between the internal gear 5c and the stator 21. This disk 31
This prevents the planetary gear 5b from coming out of the pin 5d in the axial direction. Reference numeral 27 denotes a center bracket, which has a first cylindrical portion 27a on the center side and a second cylindrical portion 27c formed on the outer peripheral side so as to protrude in the same direction as the first cylindrical portion 27a. A disk portion 27b is provided between the first cylindrical portion 27a and the second cylindrical portion 27c.

The first cylindrical portion 27a is rotatably mounted on the other end of the protruding portion 3a of the output rotary shaft 3 via a bearing 28. A thread groove 27f is formed on the outer peripheral surface of the first cylindrical portion 27a. The second cylindrical portion 27c located on the outside is fitted on the end face of the stator 21, and the internal gear 5c is housed on the inner peripheral side of the second cylindrical portion 27c.

For example, three positioning projections 27d are formed on the disk portion 27b at equal intervals in the circumferential direction. Reference numeral 37 denotes a disk-shaped rotary disk, which is provided with eight projecting portions 2 at equal intervals around the circumference.
7c are inclined and cut up, and these protrusions 2
Reference numeral 7c denotes eight notches 51 of the internal gear 5c.
c.

Therefore, the rotary disk 37 cannot rotate with respect to the internal gear 5c, that is, the internal gear 5c.
It is designed to rotate integrally with c. Numeral 34 denotes a disk-shaped fixed disk. The fixed disk 34 has a locking hole 34a formed opposite to the disk portion 27b of the center bracket 27. The parts 34a are fitted.

The fixed disk 34 is pressed by the disc spring 33 toward the disk portion 27b of the center bracket 27, and the disc spring 33 is fitted into the first cylindrical portion 27a. A nut 32 is screwed into the first cylindrical portion 27a, and the nut 32 is fixed to the fixed disk 34 and the center bracket 2.
The rotating disk 37 is pressed between the rotating disk 37 and the disk portion 27b.

In this case, by adjusting the pressing force of the nut 32 against the disc spring 33, the fixed disk 34, the disk portion 27b of the center bracket 27 and the rotating disk 3 are adjusted.
7 is adjusted. The output rotary shaft 3 is covered by a front bracket 25, and is connected between the front bracket 25 and the rear bracket 19 by a through bolt 39. When the front bracket 25 and the rear bracket 19 are fixed by the through bolt 39, the stator 21 and the second cylindrical portion 27c of the center bracket 27 are sandwiched between the front bracket 25 and the rear bracket 19. , The internal gear 5c also includes the center bracket 27, the stator 21, and the center bracket 27.
The second cylindrical portion 27c is clamped and fixed. At this time, a wave washer 38 is inserted between the groove of the disk portion 27b of the center bracket 27 and the internal gear 5c to receive a thrust load.

Reference numeral 36 denotes a circlip inserted into a groove provided on the output rotary shaft 3, and 35 denotes a circlip disposed between the circlip 36 and the disk portion 27b of the center bracket 27. Washer. By the way, the driving member 11 is an outer member, the driven member 13 is an inner member, the torque transmitting member 12 is a roller, and a spring 18 is provided.
This constitutes an overrunning clutch. That is, the cam surface 11 formed on the inner peripheral surface of the hollow portion of the outer 11
a and a space above the wedge formed between the driven side member 13 and
A roller 12 pressed by a spring 18 is provided. In addition, a row is provided between the driven side member 13 and the outer 11.
A third bearing 17 and a fourth bearing 29 are disposed in the front-rear direction (the left-right direction in FIG. 1) of the roller 12, respectively, to suppress the eccentricity of the driven member 13 and the spring 18.

The first bearing 15 and the second bearing 1
The sixth, third and fourth bearings 17 and 29 are needle bearings or sintered metal impregnated with oil. On the front bracket 25 side of the output rotary shaft 3, a pinion gear 20 that meshes with a ring gear of an engine (not shown) and transmits motor torque is engaged via a helical spline 3c of the output rotary shaft 3. The shift lever 8 has one end engaged with the annular member 7 attached to the pinion gear 20 and the other end engaged with the joint 6 a of the plunger 6 b of the magnet switch 6.

Next, the operation of the above configuration will be described. When a key switch (not shown) is turned on, the magnet switch 6 is activated, and the plunger 6b is sucked.
The shift lever 8 engaged with the joint 6a is pulled toward the magnet switch 6. The rotation of the shift lever 8 advances the pinion gear 20 through the helical spline 3c. When the pinion gear 20 comes into contact with the ring gear, the contact of the magnet switch 6 closes, and a large current flows through the exciting coil 22a of the starter motor 1.

The armature 2 is rotated by the exciting magnetic flux of the exciting coil 22a. The rotation of the armature 2 is transmitted to the driven member 13 via the roller 12 from the outer 11 which is the driving member integrated with the armature core 14, and the rotation of the driven member 13 which also functions as the inner member. The rotation is transmitted to the planetary gear 5b via the sun gear 5a. In this case, the internal gear 5c is provided between the fixed disk 34 receiving the force of the disc spring 33 and the disk portion 37b of the center bracket 27, with the rotating disk 37 engaged so as to rotate integrally therewith. , The rotation is blocked below a predetermined rotation torque.

For this reason, the rotation of the driven-side member 13 causes the planetary gear 5b meshing between the sun gear 5a and the internal gear 5c to rotate at a reduced speed. And rotate it. Then, the reduced rotation is transmitted to the pinion gear 20 via the helical spline 3c. Also, the pinion gear 2
The rotation of 0 is transmitted to the ring gear, and the engine starts.

After the engine is started, the driven member 13 is driven by the ring gear via the pinion gear 20 and the planetary gear mechanism 5.
Is reversely urged and rotates higher than the outer 11, the overrunning clutch action releases the connection between the driven side member 13 and the outer 11, the outer 11 idles, and the armature 2 becomes over-rotated. Is prevented. When the key switch is turned off by the completion of the start, the power supply to the magnet switch 6 is stopped, the plunger 27 is returned by the return spring, and the contact in the magnet switch 6 is opened accordingly, and the starter motor is started. One excitation coil 22
The power supply to a is stopped. Then, the pinion gear 20 separates from the ring gear.

FIG. 4 shows another embodiment of the present invention. In this embodiment, one of the driven members 13 is supported by a first bearing 15 of a rear bracket.
The other is provided with a bearing 30 on a center bracket 27. According to each of the above-described embodiments, since the overrunning clutch is provided in the armature core 14 at the stage prior to deceleration, the load capacity of the clutch can be extremely reduced, and the clutch can be downsized.

Further, since only the pinion gear 20 slides on the output rotary shaft 3, the attractive force of the magnet switch 6 can be greatly reduced, and the size of the magnet switch can be reduced. Further, in the case where the outer 11 idles and the inner 13 rotates at a considerably high speed, the third bearing 1 is provided on the roller 12 disposed between the outer 11 and the inner 13 in the front-rear direction.
7, the fourth bearing 29 is provided, and the inner 13 is supported at both ends by the first bearing 15 and the second bearing 16, so that the center axes of the outer 11 and the inner 13 are less likely to shift, and Since the driven-side member 13 also serving as an inner member is solid and small in diameter, the centrifugal force on the roller 12 in the outer 11 is suppressed to a small value, so that the clutch performance can be maintained up to a high-speed rotation range.

In the above-described embodiment, a roller clutch is used as the over-running clutch, but another clutch such as a sprag clutch may be used.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a sectional view of the armature section taken along line AA of FIG. 1;

FIG. 3 is a sectional view showing a conventional starter.

FIG. 4 is a sectional view showing another embodiment of the present invention.

[Explanation of symbols]

 Reference Signs List 2 armature 3 output rotating shaft 3c spline 5 reduction mechanism 5a sun gear 5b planetary gear 11 driving member (inner) 11a cam surface 12 torque transmitting member (roller) 13 driven member (outer) 15 first bearing 16th Second bearing 17 Third bearing 20 Pinion gear 29 Fourth bearing

──────────────────────────────────────────────────続 き Continuation of the front page (56) References Japanese Utility Model 63-147565 (JP, U) Japanese Utility Model 63-168276 (JP, U) (58) Fields surveyed (Int. Cl. ⁶ , DB name) F02N 15/02

Claims (6)

(57) [Claims] 1. A driving-side member integrated with an armature , a solid armature shaft protruding from both sides of the driving-side member in the axial direction and having a gear at a tip, and from the driving-side member to the armature shaft . Contact the outer circumference of the armature shaft to transmit torque only
And over-running clutch having a torque transmission member that, an output rotary shaft to which the driving force from the armature shaft is transmitted, is splined to the output rotary shaft, a pinion gear meshing with the ring gear of an internal combustion engine, the gear of the armature shaft The armature meshing
A speed reduction mechanism for transmitting the output rotation shaft by decelerating the rotation of the shaft, said protruding from the driving gear member to both sides in the axial direction armor
First, the starter of the second bearing, and an armature that internally provided the overrunning clutch, comprising the supporting each protrusion tea shaft respectively. 2. A driving-side member and a driven-side member having a gear at a distal end thereof, which protrudes from both sides of the driving-side member in the axial direction,
An overrunning clutch having a torque transmitting member that transmits torque only from the driving side member to the driven side member, an output rotating shaft to which a driving force is transmitted from the driven side member, and a spline coupling to the output rotating shaft; A pinion gear that meshes with a ring gear of the internal combustion engine; a reduction mechanism that meshes with a gear of the driven side member to reduce the rotation of the driven side member and transmits the rotation to the output rotation shaft; and the torque transmission in the axial direction of the driven side member. Third and fourth bearings located on both sides of the member and disposed between the driven side member and the driving side member, and the overrunning clutch and the third and fourth bearings are internally provided. A starter comprising: an armature; 3. located on opposite sides of said torque transmitting member with respect to the axial direction of the armature shaft, and said Amachi
The starter according to claim 1, further comprising: a third and a fourth bearing disposed between the shaft and the driving-side member, and disposed in the armature. 4. The driven-side member is a solid and small-diameter inner, the driving-side member is an outer having a cam surface in a radial direction of an inner peripheral surface, and a roller having a cylindrical shape is disposed on the cam surface. The starter according to claim 2, wherein: 5. The starter according to claim 1, wherein said first, second, third, and fourth bearings are needle bearings or sintered metal impregnated with oil. 6. The starter according to claim 1, wherein the driving-side member is a high-strength member subjected to heat treatment.