JP4487976B2 - Starter - Google Patents

Description

  The present invention relates to a starter provided with a reverse rotation prevention clutch in which a pinion gear is always meshed with a ring gear on the engine side and a motor armature shaft is prevented from rotating in a direction opposite to that when the engine is driven.

2. Description of the Related Art Conventionally, there is known an always-mesh starter in which a starter pinion gear is always meshed with an engine-side ring gear (see Patent Document 1). In this constant mesh starter, the pinion gear does not disengage from the ring gear after the engine is started, and is always meshed. Therefore, restart before the engine stops is possible.
However, in the always-mesh starter, if the engine rotates reversely, for example, when the vehicle moves backward due to crankshaft swing or climbing path stall that occurs when the engine is stopped, the reverse rotation is changed to a pinion gear that is always meshed with the ring gear. The rotation in the direction opposite to that when the engine is driven is transmitted to the output shaft. As a result, the motor armature is rotated at the number of revolutions multiplied by the gear ratio between the ring gear and the pinion gear (in a starter having a reduction gear, the number of revolutions multiplied by the reduction ratio). There is a concern that the armature may be damaged by force.

Therefore, the present applicant has proposed a starter provided with a reverse rotation prevention clutch that prevents the armature from rotating in the direction opposite to that when the engine is driven (see Patent Document 2).
The reverse rotation prevention clutch includes a clutch inner provided on the armature shaft, a clutch-shaped cam chamber formed between the clutch inner and the clutch inner. When the engine starts, the roller idles to allow the armature shaft to rotate, and when the reverse rotation of the engine is transmitted to the armature shaft, the roller moves in the narrow direction of the cam chamber. The reverse rotation of the armature is prevented by moving to and engaging the clutch inner and the clutch outer.
JP 2004-225544 A Japanese Patent Application No. 2005-38081

By the way, in order to transmit the motor drive torque to the output shaft when the engine is driven, the reverse rotation prevention clutch needs to be held in a state where the roller is slidable between the clutch inner and the clutch outer. However, if the clutch inner is tilted with respect to the shaft center or is eccentric in the radial direction with respect to the clutch outer, the roller is sandwiched between the clutch outer and the clutch inner and locked or a sliding loss occurs. As a result, the starter may be prevented from rotating, and the engine may not be started normally.
Note that the inclination and eccentricity of the clutch inner are caused by a gap between the inner diameter of the bearing that supports both ends of the armature shaft and the outer diameter of the armature shaft, or the position of the bearing itself is displaced in the radial direction.
The present invention has been made based on the above circumstances, and an object thereof is to provide a reverse rotation prevention clutch capable of preventing reverse rotation of the armature shaft, and the clutch inner used in the reverse rotation prevention clutch has inclination and eccentricity. An object of the present invention is to provide a starter that can reliably transmit the driving torque of the motor to the engine side even if it occurs.

(Invention of Claim 1)
The starter of the present invention includes a reverse rotation prevention clutch on the armature shaft of the motor. This reverse rotation prevention clutch is provided between the motor and the planetary gear speed reducer , and is fixed to the clutch inner provided on the armature shaft, the housing, etc., and forms a cam chamber between the clutch inner and the like. A clutch outer and a roller disposed in the cam chamber. When rotation in the direction opposite to that during engine driving is transmitted to the armature shaft, the roller engages with the clutch outer and the clutch inner to Prevent reverse rotation of the slave shaft.
The clutch outer is divided into a cam chamber forming portion that forms a cam chamber with the clutch inner and an outer fixing portion that is fixed to the housing or the like so as not to rotate. It is characterized by being combined with the portion so as not to be relatively rotatable and capable of being eccentric in a predetermined amount in the radial direction.

According to the above configuration, since the cam chamber forming portion of the clutch outer can be eccentric by a predetermined amount in the radial direction with respect to the outer fixing portion, when the clutch inner is inclined or decentered, the cam chamber is formed in the change. The part can follow and tilt or can be eccentric. Accordingly, it is possible to avoid a state in which the roller is sandwiched between the clutch outer and the clutch inner and cannot move when the engine is driven, and a slidable state can be maintained between the clutch outer and the clutch inner. As a result, no sliding loss occurs when the engine is driven, and the driving torque of the motor can be normally transmitted to the output shaft, so that the engine can be started reliably.
Further, by dividing the clutch outer into the cam chamber forming portion and the outer fixing portion, the cam chamber forming portion and the outer fixing portion can be manufactured separately. For example, it is possible to machine a cam chamber forming part having a complicated cam shape by cutting, and cold-forging or pressing the outer fixed part which is a simple shape, compared with the case where both are formed integrally The moldability of the clutch outer is greatly improved, and the cost can be reduced.

(Invention of Claim 2)
The starter according to claim 1, wherein the clutch outer has a female engagement portion on one side of the cam chamber forming portion and the outer fixing portion, and a male engagement portion on the other side. The engaging portions of the both have a predetermined gap and are engaged with each other so as not to rotate relative to each other.
As a result, the cam chamber forming portion and the outer fixing portion can be combined so that they cannot be rotated relative to each other and can be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 3)
The starter according to claim 2, wherein the cam chamber forming portion has a spline shaft portion having male spline teeth formed on an outer periphery thereof, and the outer fixing portion has a spline tube portion having female spline teeth formed on an inner periphery thereof. The cam chamber forming portion and the outer fixing portion are characterized in that a spline shaft portion is spline-fitted to the inner periphery of the spline tube portion.
As a result, the cam chamber forming portion and the outer fixing portion can be combined so that they cannot be rotated relative to each other and can be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 4)
The starter according to claim 2, wherein the outer fixing portion is formed with a center hole having an uneven shape on the inner periphery as a female engaging portion, and the cam chamber forming portion is provided with a male engaging portion. A concave and convex flange portion is provided on the inner periphery of the concave and convex shape formed in the central hole, and has a predetermined gap and is meshed so as not to be relatively rotatable.
The center hole formed in the outer fixing portion and the flange portion formed in the cam chamber forming portion are fitted to each other so that the concave and convex shapes mesh with each other with a predetermined gap, thereby forming the cam chamber forming portion. The outer fixing portion can be combined with the outer fixing portion so as not to rotate relative to each other and to be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 5)
In the starter according to claim 2, a center hole having an elliptical shape or an elliptical shape is formed on the inner periphery of the outer fixing portion as a female engaging portion, and the cam chamber forming portion has a male shape. As the engaging portion, an elliptical or elliptical flange portion is provided which has a predetermined gap on the inner periphery of the center hole and is fitted so as not to be relatively rotatable.
A flange portion having an oval shape or an oval shape formed in the cam chamber forming portion is fitted with a predetermined gap on the inner periphery of the center hole having an oval shape or an oval shape formed in the outer fixing portion. Thus, the cam chamber forming portion and the outer fixing portion can be combined so that they cannot be rotated relative to each other and can be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 6)
The starter according to claim 2, wherein the outer fixing portion is formed with a center hole having a polygonal shape on the inner periphery as a female engaging portion, and the cam chamber forming portion is provided with a male engaging portion. In addition, a polygonal flange portion is provided on the inner periphery of the center hole so as to be fitted with a predetermined gap so as not to be relatively rotatable.
The cam chamber forming portion is formed by fitting the flange portion having the polygonal shape formed in the cam chamber forming portion with a predetermined gap to the inner periphery of the center hole having the polygonal shape formed in the outer fixing portion. And the outer fixing portion can be combined so that they cannot be rotated relative to each other and can be decentered by a predetermined amount in the radial direction.

(Invention of Claim 7)
3. The starter according to claim 2, wherein the outer fixing portion is formed with a through hole or a recess in the axial direction as a female engaging portion, and the cam chamber forming portion is penetrated as a male engaging portion. A pin or a convex portion that is fitted in the hole or the concave portion with a predetermined gap is provided protruding in the axial direction.
The pin or convex portion formed in the cam chamber forming portion is fitted into the through hole or concave portion formed in the outer fixing portion with a predetermined gap so that the cam chamber forming portion and the outer fixing portion are relative to each other. They can be combined so that they cannot rotate and can be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 8)
3. The starter according to claim 2, wherein the cam chamber forming portion is formed with a through hole or a recess in the axial direction as a female engaging portion, and the outer fixing portion is penetrated as a male engaging portion. A pin or a convex portion that is fitted in the hole or the concave portion with a predetermined gap is provided protruding in the axial direction.
A pin or a convex portion formed on the outer fixing portion is fitted into a through hole or a concave portion formed in the cam chamber forming portion with a predetermined gap so that the cam chamber forming portion and the outer fixing portion are relative to each other. They can be combined so that they cannot rotate and can be eccentric by a predetermined amount in the radial direction.

(Invention of Claim 9)
The starter according to any one of claims 2 to 8, wherein the reverse rotation preventing clutch has a restricting means for restricting the axial movement of the cam chamber forming portion with respect to the outer fixing portion. In this case, even if the clutch outer is divided into the outer fixing portion and the cam chamber forming portion, the axial movement of the cam chamber forming portion is restricted with respect to the outer fixing portion. Can be stabilized. As a result, the roller and the clutch inner can be reliably brought into contact with each other, and the reverse rotation prevention clutch can be operated normally.
Further, it is possible to avoid the cam chamber forming portion and the roller from interfering with other components (for example, a planetary gear or an armature) adjacent to the reverse rotation prevention clutch.

(Invention of Claim 10)
The starter according to claim 9, wherein the restricting means includes a clutch cover and an outer plate that are disposed on both sides in the axial direction of the cam chamber forming portion and are respectively fixed to the outer fixing portion, and the cam chamber forming portion is configured by the clutch cover. The movement of the cam chamber is restricted in one axial direction, and the movement of the cam chamber forming portion in the other axial direction is restricted by the outer plate. In this case, since the movement of the cam chamber forming portion in one axial direction can be restricted using the existing clutch cover, the axial movement of the cam chamber forming portion can be restricted only by adding the outer plate. .

(Invention of Claim 11)
The starter according to claim 9 or 10 is characterized in that an axial gap is provided between the restricting means and the cam chamber forming portion.
In this case, since there is a gap in the axial direction between the restricting means and the cam chamber forming portion, even if the movement of the cam chamber forming portion in the axial direction is restricted by the clutch cover and the outer plate, When the inner is tilted, the cam chamber forming portion is not inhibited from tilting, and the cam chamber forming portion can be tilted following the tilt of the clutch inner. As a result, it is possible to avoid a state in which the roller is sandwiched between the clutch outer and the clutch inner and cannot move when the engine is driven, and a slidable state can be maintained between the clutch outer and the clutch inner.

(Invention of Claim 12)
The starter according to claim 11, wherein an elastic body is disposed in a gap provided between the regulating means and the cam chamber forming portion, and the cam chamber forming portion is pressed in the axial direction by the elastic body. To do.
In this case, since the cam chamber forming portion can be prevented from shaking due to vibration or the like, the axial position of the roller can be stabilized even when the clutch outer is divided into the outer fixing portion and the cam chamber forming portion. it can. As a result, the roller and the clutch inner can be reliably brought into contact with each other, and the reverse rotation prevention clutch can be operated normally.
Further, when the clutch inner is tilted, the cam chamber forming portion can be tilted with the deformation of the elastic body, so that the roller is sandwiched between the clutch outer and the clutch inner and cannot move when the engine is driven. In other words, a slidable state can be maintained between the clutch outer and the clutch inner.

  The best mode for carrying out the present invention will be described in detail by the following examples.

FIG. 1 is a half sectional view of a constant mesh starter 1.
As shown in FIG. 1, a starter 1 according to the first embodiment includes an electromagnetic relay that opens and closes a motor 2 that generates rotational force and a main contact (described later) provided in an energization circuit (referred to as a motor circuit) of the motor 2. 3, a speed reducer 4 that decelerates the rotation of the motor 2, an output shaft 5 to which the drive torque of the motor 2 is transmitted via the speed reducer 4, a pinion gear 6 supported by the output shaft 5, and the motor 2 The reverse rotation preventing clutch 7 and the like for preventing the reverse rotation of the motor.
The starter 1 is an engine automatic stop / restart system (for example, an engine automatic stop / restart system that automatically restarts the engine E at the start after the vehicle is temporarily stopped at an intersection or traffic jam and the engine E (see FIG. 2) automatically stops). Generally used for idle stop, eco-run system, etc.).

The motor 2 is composed of a yoke 8 that forms a magnetic circuit, a permanent magnet 9 (which may be a field coil) that forms a magnetic field on the inner periphery of the yoke 8, an armature 10 that rotates by the action of electromagnetic force, and the like. This is a known DC motor.
The yoke 8 has a cylindrical shape, is sandwiched between the front housing 11 and the end frame 12, and is fixed by fastening a plurality of through bolts 13 to the front housing 11 from the rear end of the end frame 12.
The permanent magnets 9 are fixed to the inner peripheral surface of the yoke 8 via the magnet holder 14, and a plurality of permanent magnets 9 are arranged at equal intervals in the circumferential direction of the yoke 8.

The armature 10 includes an armature shaft 15, an armature core 16 that is serrated to the outer periphery of the armature shaft 15, an armature coil 17 wound around the armature core 16, and an armature shaft 15. The commutator 18 is provided on one end side.
The commutator 18 is formed by a plurality of segments arranged in a cylindrical shape around the armature shaft 15 via an insulating material 19, and each segment is electrically and mechanically connected to the armature coil 17. A plurality of carbon brushes 20 are disposed on the outer periphery of the commutator 18.

As shown in FIG. 2, the electromagnetic relay 3 includes an electromagnetic coil 23 that is energized from the in-vehicle battery 22 via the starter relay 21, and when an electromagnet is formed by energization of the electromagnetic coil 23, the plunger 24 is attached to the electromagnet. (See FIG. 1) is sucked to close the main contact of the motor circuit. When the energization of the electromagnetic coil 23 is stopped and the attraction force of the electromagnet disappears, the plunger 24 is pushed back by the reaction force of a return spring (not shown) to open the main contact.
In the starter relay 21, when the driver starts the engine for the first time, the relay switch 21a is energized from the in-vehicle battery 22 by turning on the start switch 25 to the ST position, and the contact 21b is closed. When E is restarted, the relay coil 21a is energized through an idle stop ECU 26 that controls automatic stop and restart of the engine E.

The main contact is formed between a pair of fixed contacts 29 connected to the motor circuit via two external terminals 27 and 28 (see FIG. 1) and a set of fixed contacts 29 that are movable together with the plunger 24. The main contact is closed when the pair of fixed contacts 29 is conducted through the movable contact 30, and the conduction between the pair of fixed contacts 29 is cut off. The contact is opened.
The two external terminals 27 and 28 are a B terminal 27 connected to the in-vehicle battery 22 via a battery cable 31 (see FIG. 2) and an M terminal 28 to which a motor lead wire 32 taken out from the motor 2 is connected. And is fixed to the cover 3 a of the electromagnetic relay 3.

The speed reducer 4 is a well-known planetary gear speed reducer that can decelerate on the same axis as the armature shaft 15, and a sun gear 33 formed on the other end side (the anti-commutator side) of the armature shaft 15 and the sun gear 33 are concentric. And an internal gear 34 whose rotation is restricted via the torque limiter described below, and a plurality of planetary gears 35 meshing with both gears 33, 34.
The torque limiter has a rotating disk 36 whose rotation is restricted by a frictional force. When an excessive torque exceeding the stationary torque of the rotating disk 36 is applied to the internal gear 34, the rotating disk 36 slides against the frictional force ( Rotation), the rotation of the internal gear 34 is allowed and the excessive torque is absorbed.

The output shaft 5 is disposed on the same axis as the armature shaft 15, one end side is connected to the armature shaft 15 via the speed reducer 4, and the other end side is rotatably supported by the front housing 11 via a bearing 37. Has been.
The pinion gear 6 is rotatably fitted to the outer periphery of the output shaft 5 via a bearing 38, is connected to the output shaft 5 via an impact absorbing device described below, and is always meshed with a ring gear 39 on the engine side. ing.

The shock absorber includes a first rotating body 40 that is serrated and fitted to the outer periphery of the output shaft 5, a second rotating body 41 that is serrated and fitted to the outer periphery of the cylindrical portion 6 a provided integrally with the pinion gear 6, It is comprised from elastic bodies 42, such as rubber | gum arrange | positioned between the rotary bodies 40 and 41. FIG. A plurality of elastic bodies 42 are arranged in series between the rotating bodies 40 and 41 via the intermediate member 43 (in FIG. 1, a total of 6 pieces of 3 × 2 per stage).
When the engine E having a large inertial energy is started, the shock absorbing device absorbs the shock torque transmitted to the starter 1 by compressing and deforming the elastic body 42.

  The reverse rotation prevention clutch (hereinafter abbreviated as “clutch 7”) is a clutch inner 44 provided on the armature shaft 15, and a cam chamber 45 formed between the clutch inner 44 and a clutch fixed to the front housing 11. An outer (described later), a roller 46 disposed in the cam chamber 45, a spring 47 that urges the roller 46 in a narrow direction (left direction in the drawing) of the cam chamber 45, and the like.

The clutch inner 44 is provided between the sun gear 33 formed on the armature shaft 15 and the armature core 16 fixed to the armature shaft 15, and is formed integrally with the armature shaft 15. Alternatively, a cylindrical member separate from the armature shaft 15 may be fixed to the outer periphery of the armature shaft 15 by press fitting or the like.
As shown in FIG. 3, the cam chamber 45 is formed in a wedge shape in which a gap formed between the outer circumferential surface of the clutch inner 44 is gradually narrowed from one circumferential side (right side in the drawing) toward the other side. The outer diameter D of the roller 46 is formed wider on one side in the circumferential direction, and the outer diameter D of the roller 46 is narrower on the other side in the circumferential direction.

4A, when the clutch inner 44 is driven in the clockwise direction indicated by the arrow in the drawing, that is, when the engine is driven, the roller 46 compresses the spring 47 while compressing the spring 47. The clutch inner 44 is allowed to rotate by moving to one side (wide side) 45 and idling between the clutch inner 44 and the clutch outer.
On the other hand, as shown in FIG. 4B, when the clutch inner 44 is driven in the counterclockwise direction indicated by the arrow in FIG. Since it moves to the other side (narrow side) 45 and is sandwiched between and engaged with the clutch inner 44 and the clutch outer, the rotation of the clutch inner 44 is prevented. As a result, the armature shaft 15 is prevented from rotating in the direction opposite to that when the engine is driven.

As shown in FIG. 5, the clutch outer according to the present invention includes a cam chamber forming portion 48 that forms a cam chamber 45 between the clutch inner 44 and a disc-shaped outer fixing portion 49 that is fixed to the front housing 11. It is divided into and.
The outer fixing portion 49 is formed with a center hole 49a in the central portion in the radial direction, and an uneven shape is formed in the inner periphery of the center hole 49a on the entire periphery. On the other hand, the cam chamber forming portion 48 is provided with a flange portion 48a fitted to the inner periphery of the center hole 49a, and an uneven shape is formed on the outer periphery of the flange portion 48a.
This clutch outer is configured such that the flange portion 48a is fitted to the inner periphery of the center hole 49a so that the uneven shapes formed in the center hole 49a and the flange portion 48a mesh with each other with a predetermined gap. The chamber forming portion 48 and the outer fixing portion 49 are combined so as not to rotate relative to each other and to be eccentric by a predetermined amount in the radial direction.

Next, the operation and effect of the starter 1 will be described.
When the main contact of the motor circuit is closed by the electromagnetic relay 3, the armature coil 17 is energized from the in-vehicle battery 22, and a rotational force is generated in the armature 10 by the electromagnetic force acting on the armature coil 17. The rotation of the armature 10 is not blocked by the clutch 7 but is transmitted to the output shaft 5 via the speed reducer 4 and further transmitted from the pinion gear 6 to the ring gear 39 to crank the engine E. At this time, the impact torque generated in the starter 1 is absorbed by the impact absorbing device. An excessive impact that cannot be absorbed by the impact absorbing device (that is, when the elastic body 42 is fully compressed) is cut by the torque limiter.

When the engine E completes explosion and the engine speed exceeds the starter speed, for example, a one-way clutch (not shown) built in the ring gear 39 idles and the ring gear 39 is disconnected from the crankshaft of the engine E. Therefore, the rotation of the engine E is not transmitted to the pinion gear 6, and overrun of the armature 10 can be prevented.
Further, when the engine E reversely rotates, such as when the vehicle moves backward due to the swing of the crankshaft or the climbing path that occurs when the engine E stops, the reverse rotation is transmitted to the pinion gear 6 that is always meshed with the ring gear 39, The rotation in the direction opposite to that during engine driving is transmitted to the output shaft 5. When this reverse rotation of the output shaft 5 is transmitted to the armature shaft 15 via the speed reducer 4, the roller 46 of the clutch 7 is locked between the clutch inner 44 and the clutch outer, That is, since the reverse rotation of the armature shaft 15 is prevented, the armature 10 can be prevented from rotating in the direction opposite to that when the engine is driven.

(Effect of Example 1)
In the clutch 7 of this embodiment, the clutch outer is divided into a cam chamber forming portion 48 and an outer fixing portion 49, and both of them are combined so that they cannot be rotated relative to each other and can be eccentric in a predetermined amount in the radial direction. Yes. As a result, when the clutch inner 44 is tilted or decentered, the cam chamber forming portion 48 can be tilted or decentered according to the change, so that the roller 46 moves between the clutch inner 44 and the clutch outer when the engine is driven. It is possible to avoid a state where the belt cannot be moved due to being sandwiched between the clutch inner 44 and the clutch inner 44 and the clutch outer. As a result, no sliding loss occurs when the engine is driven, and the driving torque of the motor 2 can be normally transmitted to the output shaft 5, so that the engine E can be started reliably.

Further, since the clutch outer is divided into the cam chamber forming portion 48 and the outer fixing portion 49, the cam chamber forming portion 48 and the outer fixing portion 49 can be manufactured separately. For example, the cam chamber forming portion 48 having a complicated cam shape can be processed by cutting, and the outer fixing portion 49 having a simple shape can be manufactured by cold forging or pressing. On the other hand, when the cam chamber forming portion 48 and the outer fixing portion 49 are integrally formed, the cam shape formed on the inner periphery of the cam chamber forming portion 48 is a complicated shape (wedge shape), and the cam Since the outer diameters of the chamber forming portion 48 and the outer fixing portion 49 are greatly different, it is difficult to produce the entire clutch outer by forging.
Therefore, in this embodiment, compared with the case where the cam chamber forming portion 48 and the outer fixing portion 49 are formed integrally, the moldability of the clutch outer is improved and the cost can be reduced.

FIG. 6 is a perspective view of the clutch 7 according to the second embodiment.
In the clutch 7 according to the second embodiment, as shown in FIG. 6, the center hole 49 a formed in the outer fixing portion 49 and the flange portion 48 a provided in the cam chamber forming portion 48 are each in a substantially oval shape. And an oval shape or an elliptical shape.
Also in this case, the flange portion 48a is fitted to the inner periphery of the center hole 49a with a predetermined gap so as not to be relatively rotatable, so that the cam chamber forming portion 48 and the outer fixing portion 49 are not relatively rotatable. They can be combined in such a manner that they can be eccentric by a predetermined amount in the radial direction.

FIG. 7 is a perspective view of the clutch 7 according to the third embodiment.
In the clutch 7 according to the third embodiment, as shown in FIG. 7, a center hole 49a formed in the outer fixing portion 49 and a flange portion 48a provided in the cam chamber forming portion 48 are formed in polygonal shapes, respectively. It is an example.
Also in this case, the flange portion 48a is fitted to the inner periphery of the center hole 49a with a predetermined gap so as not to be relatively rotatable, so that the cam chamber forming portion 48 and the outer fixing portion 49 are not relatively rotatable. They can be combined in such a manner that they can be eccentric by a predetermined amount in the radial direction.

FIG. 8 is a perspective view of the clutch 7 according to the fourth embodiment.
As shown in FIG. 8, the clutch 7 according to the fourth embodiment has a plurality of through holes 49 b (or concave portions) formed in the outer fixing portion 49 in the axial direction, and the cam chamber forming portion 48 has a through hole 49 b ( Alternatively, a plurality of pins 48b (or convex portions) that are fitted with a predetermined gap in the concave portion are provided in a protruding manner in the axial direction.
Also in this case, the cam chamber forming portion 48 and the outer fixing portion 49 cannot be relatively rotated by fitting the pin 48b (or the convex portion) with a predetermined gap into the through hole 49b (or the concave portion). In addition, they can be combined so as to be eccentric by a predetermined amount in the radial direction.
Note that the relationship between the through hole 49b and the pin 48b (or the concave portion and the convex portion) may be reversed. In other words, the through hole 49 b (or concave portion) can be formed in the cam chamber forming portion 48, and the pin 48 b (or convex portion) can be provided in the outer fixing portion 49.

FIG. 9 is a half sectional view of the starter 1 according to the fifth embodiment.
In the clutch 7 according to the fifth embodiment, the cam chamber forming portion 48 and the outer fixing portion 49 are combined by spline coupling, and the restriction that restricts the axial movement of the cam chamber forming portion 48 with respect to the outer fixing portion 49. It is an example which provided the means (after-mentioned).
The cam chamber forming portion 48 described in the first to third embodiments has a flange portion 48a protruding in the outer diameter direction, but the cam chamber forming portion 48 of the present embodiment does not have the flange portion 48a. In addition, a spline shaft portion 48c having the same outer diameter in the entire axial direction and having male spline teeth formed on the outer periphery thereof (see FIG. 10).

On the other hand, the outer fixing portion 49 is provided with a spline tube portion 49c that is spline-fitted on the outer periphery of the spline shaft portion 48c, and female spline teeth are formed on the inner periphery of the spline tube portion 49c.
As shown in FIG. 10, the outer fixing portion 49 and the cam chamber forming portion 48 include a female spline tooth formed on the inner periphery of the spline cylinder portion 49c, and a male spline tooth formed on the outer periphery of the spline shaft portion 48c. Are engaged with each other so that they cannot be rotated relative to each other and can be decentered by a predetermined amount in the radial direction.

As shown in FIG. 11, the restricting means includes a clutch cover 50 and an outer plate 51 that are disposed on both sides in the axial direction of the cam chamber forming portion 48.
The clutch cover 50 is press-fitted into the outer periphery of the spline cylinder portion 49 c and covers one end side (right side in the drawing) of the clutch 7 via the washer 52. The washer 52 is disposed on the open side (the right side in FIG. 11) of the cam chamber 45 and prevents the roller 46 and the spring 47 from jumping out of the cam chamber 45.
The outer plate 51 is disposed on the inner periphery of the other end side of the outer fixing portion 49, and is caulked and fixed to the end portion of the spline cylinder portion 49c.

  With the above configuration, the movement of the cam chamber forming portion 48 in the axial direction (right direction in FIG. 11) is restricted by the clutch cover 50, and the movement in the other axial direction is restricted by the outer plate 51. The axial distance between the clutch cover 50 and the outer plate 51 is set slightly larger than the axial dimension of the cam chamber forming portion 48. That is, the cam chamber forming portion 48 is not completely blocked in the axial direction between the clutch cover 50 and the outer plate 51, but can move slightly in the axial direction.

According to the present embodiment, even if the clutch outer is divided into the outer fixing portion 49 and the cam chamber forming portion 48, the movement of the cam chamber forming portion 48 in the axial direction is caused by the clutch cover 50 and the outer plate 51. Since it is regulated, the position of the roller 46 is not greatly displaced in the axial direction, and the axial position of the roller 46 can be stabilized. As a result, the roller 46 and the clutch inner 44 can be reliably brought into contact with each other, so that the clutch 7 can be normally operated.
Further, when the movement of the cam chamber forming portion 48 in the axial direction is restricted, the cam chamber forming portion 48 interferes with other components (for example, the planetary gear 35 and the armature 10 shown in FIG. 9) adjacent to the clutch 7. Can be avoided.

  Further, since the cam chamber forming portion 48 can move slightly in the axial direction between the clutch cover 50 and the outer plate 51, the cam is formed by the clutch cover 50 and the outer plate 51 when the clutch inner 44 is inclined. The inclination of the chamber forming portion 48 is not hindered, and the cam chamber forming portion 48 can be inclined following the inclination of the clutch inner 44. As a result, it is possible to avoid a state in which the roller 46 is sandwiched between the clutch outer and the clutch inner 44 and cannot move when the engine is driven, and a slidable state can be maintained between the clutch outer and the clutch inner 44.

FIG. 12 is a half sectional view of the starter 1 according to the sixth embodiment.
As shown in FIG. 12, the clutch 7 according to the sixth embodiment is an example in which the axial direction of the cam chamber forming portion 48 is arranged in the opposite direction. In the clutch 7 described in the fifth embodiment, the right side of the cam chamber 45 shown in FIG. 9 is opened. However, in the clutch 7 of this embodiment, the open side of the cam chamber 45 is opposite, that is, the left side shown in the drawing. Is open.
Also in this case, the movement of the cam chamber forming portion 48 in the axial direction is restricted by the clutch cover 50 and the outer plate 51 arranged on both sides in the axial direction of the cam chamber forming portion 48. The axial position of the roller 46 and the clutch inner 44 can be reliably brought into contact with each other.

Further, as in the fifth embodiment, since the axial distance between the clutch cover 50 and the outer plate 51 is set slightly larger than the axial dimension of the cam chamber forming portion 48, the clutch inner 44 is inclined. In this case, the inclination of the cam chamber forming portion 48 is not hindered by the clutch cover 50 and the outer plate 51, and the cam chamber forming portion 48 can be inclined following the inclination of the clutch inner 44.
Furthermore, in the configuration of the present embodiment, the outer plate 51 can also serve as a retaining mechanism for the roller 46 and the spring 47, so that the washer 52 described in the fifth embodiment can be eliminated.

FIG. 13 is a cross-sectional view of the clutch outer according to the seventh embodiment.
In the starter 1 described in the fifth embodiment, the clutch 7 according to the seventh embodiment includes a spring 53 in an axial gap provided between the cam chamber forming portion 48 and the outer plate 51 as shown in FIG. It is an example of arrangement.
As a result, the cam chamber forming portion 48 is urged by the spring 53 and pressed against the washer 52, so that the cam chamber forming portion 48 can be prevented from rattling due to vibration or the like. As a result, the axial position of the roller 46 can be stabilized even in a configuration in which an axial gap is provided between the restricting means (the clutch cover 50 and the outer plate 51) and the cam chamber forming portion 48. Since the clutch inner 44 can be reliably brought into contact with the clutch inner 44, the clutch 7 can be operated normally.

Further, when the clutch inner 44 is inclined, the cam chamber forming portion 48 can be inclined with the deformation of the spring 53, so that the roller 46 is sandwiched between the clutch outer and the clutch inner 44 when the engine is driven. Therefore, it is possible to maintain a slidable state between the clutch outer and the clutch inner 44.
In the configuration of the clutch 7 described in the sixth embodiment, that is, the configuration in which the outer plate 51 is disposed on the opening side of the cam chamber 45, the spring 53 is disposed between the cam chamber forming portion 48 and the clutch cover 50. You can also.
Further, instead of the spring 53, an elastic body such as rubber or a disc spring can be used.

(Example 1) which is a half sectional view of a constant meshing starter. It is an electric circuit diagram of a starter. It is sectional drawing which shows the cam chamber of a clutch. (A) Operation | movement explanatory drawing of the clutch at the time of engine drive, (b) Operation | movement explanatory drawing of the clutch when the rotation of the reverse direction is carried out at the time of engine driving. (Example 1) which is a perspective view of a clutch. (Example 2) which is a perspective view of a clutch. (Example 3) which is a perspective view of a clutch. (Example 4) which is a perspective view of a clutch. (Example 5) which is a half sectional view of a starter. (Example 5) which is a front view which shows the structure of a clutch. (Example 5) which is sectional drawing of a clutch outer. (Example 6) which is a half sectional view of a starter. (Example 7) which is sectional drawing of a clutch outer.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Starter 2 Motor 4 Planetary gear speed reducer 5 Output shaft 6 Pinion gear 7 Reverse rotation prevention clutch 11 Front housing 15 Armature shaft 16 Armature iron core 39 Ring gear 44 Clutch inner 45 Cam chamber 46 Roller 48 Cam chamber formation part (clutch outer)
48a Flange part 48b Pin or convex part 48c Spline shaft part 49 Outer fixing part (clutch outer)
49a Center hole 49b Through hole or recess 49c Spline cylinder 50 Clutch cover (regulator)
51 Outer plate (regulation means)
53 Spring (elastic body)

Claims (12)

A motor that generates rotational force on the armature shaft;
A planetary gear reducer for reducing the rotation of the armature shaft;
An output shaft to which the driving torque of the motor is transmitted via the reduction gear;
A pinion gear that is provided on the output shaft, always meshes with a ring gear on the engine side, and rotates integrally with the output shaft to drive the ring gear;
An engine having a clutch inner provided on the armature shaft, a clutch outer fixed to a housing or the like and forming a cam chamber with the clutch inner, and a roller disposed in the cam chamber; A reverse rotation preventing clutch that engages the clutch outer and the clutch inner to prevent reverse rotation of the armature shaft when rotation in a direction opposite to that of driving is transmitted to the armature shaft; A starter with which
The reverse rotation prevention clutch is provided between the motor and the planetary gear reducer,
The clutch outer is divided into a cam chamber forming portion that forms the cam chamber between the clutch inner and an outer fixing portion that is non-rotatably fixed to the housing or the like, and the cam chamber forming portion A starter characterized in that the outer fixing portion and the outer fixing portion are combined so as not to rotate relative to each other and to be eccentric by a predetermined amount in the radial direction. The starter according to claim 1,
The clutch outer is provided with a female engagement portion on one side of the cam chamber forming portion and the outer fixing portion, and a male engagement portion on the other side. Has a predetermined gap and is engaged so as not to be relatively rotatable. The starter according to claim 2,
The cam chamber forming portion has a spline shaft portion in which male spline teeth are formed on the outer periphery,
The outer fixing part has a spline cylinder part in which female spline teeth are formed on the inner periphery,
The starter characterized in that the cam chamber forming portion and the outer fixing portion are combined with the spline shaft portion by spline fitting to the inner periphery of the spline tube portion. The starter according to claim 2,
A center hole having an irregular shape on the inner periphery is formed in the outer fixing portion as the female engagement portion, and the male chamber engagement portion is formed in the center hole as the male engagement portion. A starter characterized in that an uneven flange portion is provided on the inner periphery of the formed uneven shape and has a predetermined gap so as to be engaged with each other so that relative rotation is impossible. The starter according to claim 2,
A central hole having an oval shape or an elliptical shape is formed on the inner periphery of the outer fixing portion as the female engaging portion, and the male chamber engaging portion is formed as the male engaging portion. A starter characterized in that an ellipse-shaped or oval-shaped flange portion is provided on the inner periphery of the center hole so as to be fitted with a predetermined gap so that relative rotation is impossible. The starter according to claim 2,
The outer fixing portion is formed with a center hole having a polygonal shape on the inner periphery as the female engaging portion, and the cam chamber forming portion is formed with the male hole as the male engaging portion. A starter characterized in that a polygonal flange portion having a predetermined gap on the inner periphery and fitted so as not to be relatively rotatable is provided. The starter according to claim 2,
The outer fixing portion is formed with a through hole or a recess in the axial direction as the female engaging portion, and the cam chamber forming portion is formed in the through hole or the recessed portion as the male engaging portion. A starter characterized in that a pin or a convex portion to be fitted with a predetermined gap protrudes in the axial direction. The starter according to claim 2,
The cam chamber forming portion is formed with a through hole or a recess in the axial direction as the female engaging portion, and the outer fixing portion is formed in the through hole or the recessed portion as the male engaging portion. A starter characterized in that a pin or a convex portion to be fitted with a predetermined gap protrudes in the axial direction. The starter according to any one of claims 2 to 8,
2. The starter according to claim 1, wherein the reverse rotation prevention clutch has a restricting means for restricting an axial movement of the cam chamber forming portion with respect to the outer fixing portion. The starter according to claim 9, wherein
The restricting means is composed of a clutch cover and an outer plate that are disposed on both sides in the axial direction of the cam chamber forming portion and are respectively fixed to the outer fixing portion.
Movement of the cam chamber forming portion in one axial direction is restricted by the clutch cover,
The starter characterized in that movement of the cam chamber forming portion in the other axial direction is restricted by the outer plate. The starter according to claim 9 or 10,
A starter characterized in that an axial gap is provided between the restricting means and the cam chamber forming portion. The starter according to claim 11, wherein
An elastic body is disposed in the gap provided between the restricting means and the cam chamber forming portion,
The starter characterized in that the cam chamber forming portion is pressed in the axial direction by the elastic body.

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