JP2699609B2 - Inertial jump starter - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an inertial dive starter in which a pinion advances by the action of a helical spline and meshes with a ring gear.

2. Description of the Related Art Conventionally, a starter using a rubber clutch has been proposed to absorb an impact generated between a pinion and a ring gear (see Japanese Utility Model Laid-Open No. 62-47770).

 An example of this starter is shown in FIG.

A tubular tube 101 is spline-fitted to the outer periphery of the shaft 100, and a stepped tubular clutch outer
102 is rotatably fitted.

On the inner peripheral portion of the clutch outer 102, the clutch outer 102
An annular elastic body 103 provided so as to mesh with the tube 101 is provided, and the elastic body 103 is fitted to a protrusion 101 a formed on the outer periphery of the tube 101.

Accordingly, when the tube 101 spline-fitted with the shaft 100 rotates by the rotation of the shaft 100, the rotational force is transmitted to the clutch outer 102 via the elastic body 103, and the pinion 104 formed on the outer periphery of the clutch outer 102 is formed.
Rotates.

The pinion 104 is pushed by the elastic body 103 when the tube 101 advances on the shaft 100 by the action of the helical spline, and meshes with the ring gear 105.

At this time, the elastic member 103 disposed between the clutch outer 102 and the tube 101 bends in the axial and rotational directions, so that the shock generated when the pinion 104 and the ring gear 105 are engaged can be absorbed.

[Problems to be Solved by the Invention] However, in the starter employing the rubber clutch described above, the elastic body 103 can be compressed to absorb the impact in the axial direction. The more it is compressed and flexed in the direction, the greater the sliding torque at the contact surface. Therefore, the pinion 104 and the tube 101
The greater the impact torque, the harder it is to rotate, and the impact in the rotational direction is not sufficiently absorbed.

As a result, there is a problem that adversely affects the pinion 104 and the shaft 100. Further, when the slip torque is set in accordance with a large impact torque, the slip becomes liable to occur during normal torque transmission, so that the engine cannot be driven.

The present invention has been made based on the above circumstances, and an object of the present invention is to provide an inertial dive starter that can absorb an impact force in a rotational direction when a pinion moves at a maximum, that is, when a ring gear is driven. is there.

[Means for Solving the Problems] In order to achieve the above object, an inertial diving starter of the present invention comprises an output shaft having a helical spline formed on the outer periphery, and a tube spline-fitted to the output shaft. A pinion rotatably fitted to the output shaft at a distal end side of the tube and meshing with an engine ring gear, and provided so as to rotate integrally with the pinion; A cover rotatably disposed with respect to a shaft, and a first axially disposed cover disposed between the tube and the pinion and having a predetermined coefficient of friction between the tube and the pinion. An elastic body,
A second elastic body disposed between the tube and the cover in the axial direction and having a friction coefficient larger than the predetermined friction coefficient between the tube and the cover. Means.

[Operation] The present invention having the above configuration has the following operation.

The rotational force generated on the output shaft is transmitted to the tube spline-fitted to the output shaft, and further transmitted to the cover and the pinion rotating integrally with the cover via the second elastic body.

The pinion is pushed by the first elastic body as the tube advances on the output shaft by the action of the helical spline, and meshes with the ring gear.

Here, the forward impact force generated when the pinion collides with the ring gear and when the pinion reaches the maximum movement position is absorbed by the first elastic body being bent.

On the other hand, the load of the second elastic body is reduced due to the bending of the first elastic body, and the frictional force between the tube and the cover becomes smaller than the initial set value. As a result, the pinion and the tube are easily rotated, so that the impact force in the rotation direction when the pinion shifts to driving the ring gear is absorbed.

[Effects of the Invention] In the inertial dive starter of the present invention having the above-described action, the larger the forward impact force, the more the first elastic body is bent, and
The load on the elastic body becomes smaller. That is, the space between the second elastic body and the tube and the cover is easily slipped. Therefore,
At the time of the maximum movement of the pinion at which the forward impact force becomes maximum, the impact force in the rotational direction generated when the ring gear is driven can be absorbed and reduced, and the adverse effect on the pinion and the output shaft can be prevented.

Also, during normal torque transmission, the torque of the output shaft transmitted to the tube is transmitted to the pinion via the second elastic body having a larger coefficient of friction than the first elastic body, so that the engine can be reliably driven. Can be.

Embodiment Next, an inertial dive starter of the present invention will be described based on an embodiment shown in the drawings.

Figure 1 shows an inertial dive starter (hereinafter abbreviated as starter).
FIG.

The starter 1 according to the present embodiment is configured such that a rotational force applied to a shaft (output shaft) 2 by a motor (not shown)
And a friction clutch mechanism for absorbing the impact force generated when the pinion 3 and the ring gear 4 mesh with each other.

The friction clutch mechanism includes a tube 5 spline-fitted to a helical spline 2a formed on the outer periphery of a shaft 2 and a distal end side of the tube 5 in the axial direction (left side in FIG. 1).
The first elastic body 6 and the second elastic body 7 disposed on the rear end side and the first elastic body 6 are rotatably fitted to the shaft 2 via the bearing 8 at the distal end side of the first elastic body 6. Clutch outer 9
And a cover 10 rotatably disposed on the rear end side of the second elastic body 7 with respect to the shaft 2.

The tube 5 has a cylindrical portion 5b on the inner peripheral surface of which a tube spline 5a that fits with the helical spline 2a of the shaft 2 is formed, and a large-diameter portion 5c formed in a disk shape around the outer periphery of the cylindrical portion 5b. .

Each of the first elastic body 6 and the second elastic body 7 has an annular shape, and is fitted to a step between the cylindrical portion 5b and the large-diameter portion 5c of the tube 5. The first elastic body 6 has its rear end face (the right side face in FIG. 1) disposed in contact with the distal end face of the large-diameter portion 5c, and the second elastic body 7 has its distal end face formed of a large-diameter portion. 5c is arranged in contact with the rear end face.

The clutch outer 9 has a pinion 3 integrally formed on the outer periphery thereof, and a flat plate portion 9 a having an outer diameter slightly larger than the large diameter portion 5 c of the tube 5 is provided on the rear end side of the pinion 3. The clutch outer 9 has a rear end surface of the flat plate portion 9a in contact with a front end surface of the first elastic body 6. The clutch outer 9 is urged rearward by a return spring 11 for returning the pinion 3.

The cover 10 has a cup-like shape, and includes a flat surface portion 10a having a disk shape around the outer periphery of the shaft 2 and a cylindrical portion 10b extending from the outer peripheral edge of the flat surface portion 10a to the distal end side of the shaft 2. The outer periphery of the clutch outer 9 is swaged at the tip of the cylindrical portion 10b so that the cover 10 encloses the tube 5, the first elastic body 6, and the second elastic body 7, and is integrally formed with the clutch outer 9. It is provided to rotate. The cover 10 is disposed such that the front end surface of the flat portion 10a is in contact with the rear end surface of the second elastic body 7.

A stopper 12 for restricting the advance of the pinion 3 is externally fitted to the tip of the shaft 2, and the stopper 12 is engaged with a snap ring 13 fitted in a circumferential groove 2 b formed on the outer periphery of the shaft 2. Have been. The above-described return spring 11 is fitted between the outer periphery of the shaft 2 and is disposed between the stopper 12 and the clutch outer 9.

In this friction clutch mechanism, the friction coefficient at each contact surface between the first elastic body 6, the large diameter portion 5c of the tube 5, and the flat plate portion 9a of the clutch outer 9 is set to a relatively small predetermined value. is there.

The friction coefficient at each contact surface between the second elastic body 7 and the large-diameter portion 5c of the tube 5 and the flat portion 10a of the cover 10 is set to be larger than the predetermined value.

 Next, the operation of the present embodiment will be described.

When a starter switch (not shown) is closed, the rotation force applied to the shaft 2 by the rotation of the motor is transmitted to the tube 5 spline-fitted to the shaft 2, and further, a large coefficient of friction is generated between the tube 5 and the cover 10. The power is transmitted to the cover 10 and the pinion 3 that rotates integrally with the cover 10 via the second elastic body 7.

The tube 5 to which the rotational force of the shaft 2 has been transmitted advances on the shaft 2 by the action of the helical spline. As a result, the pinion 3 advances while rotating via the first elastic body 6 and the second elastic body 7 and abuts against the end face of the ring gear 4. At this time, an impact is applied in the axial direction, but the first elastic body 6 is compressed and flexed in the axial direction, thereby absorbing the impact force.

Further, the pinion 3 is pushed in the axial direction while rotating on the end face of the ring gear 4, thereby meshing with the ring gear 4 and moving forward until it contacts the end face of the stopper 12. At this time, an impact in the axial direction also occurs, but as in the above case, the first elastic body 6 bends to absorb the impact.

Since the first elastic body 6 is compressed and bent in the axial direction, the load in the second elastic body 7 is reduced in the axial direction.
The pressing force applied to each contact surface between the large-diameter portion 5c of the tube 5 and the flat portion 10a of the cover 10 is reduced. As a result, the frictional force at each contact surface becomes smaller than the initially set slip torque, and the pinion 3 (cover 10) and the tube 5
Can easily rotate, so that it is possible to absorb a shock in the rotational direction generated when the operation shifts to driving of the ring gear 4, and to prevent adverse effects on the pinion 3 and the shaft 2.

Further, at the time of normal torque transmission, the torque of the shaft 2 transmitted to the tube 5 is transmitted to the pinion 3 via the second elastic body 7 having a larger coefficient of friction than the first elastic body 6, so that the engine can be surely transmitted. Can be driven.

In this embodiment, the example in which the clutch outer 9 is swaged with the cover 10 is shown, but the clutch outer 9 and the cover 10 may be fixed with a circlip (retaining ring) or the like. Alternatively, if the strength permits, the clutch outer 9 and the cover are provided.
10 and may be fixed by press fitting.

Also, the cover 10 is formed in a cup shape, and the tube 5,
Although the first elastic body 6 and the second elastic body 7 are provided so as to surround them, the cover 10 may be formed in a disk shape with only the flat portion 10a by forming the clutch outer 9 in a cup shape.

[Brief description of the drawings]

FIG. 1 shows an embodiment of the present invention and is a sectional view of an inertial dive starter. FIG. 2 is a sectional view of a conventional inertial dive starter. In the drawing, 1 ... Inertial jump starter 2 ... Shaft (output shaft) 3 ... Pinion 4 ... Ring gear 5 ... Tube 6 ... First elastic body 7 ... Second elastic body 10 ... Cover

Claims (1)

(57) [Claims] (A) an output shaft having a helical spline formed on the outer periphery thereof; (b) a tube spline-fitted to the output shaft; and (c) a tube connected to the output shaft at a tip end side of the tube. A pinion movably fitted and meshing with a ring gear of the engine; and (d) provided to rotate integrally with the pinion;
A cover disposed at the rear end side of the tube so as to be rotatable with respect to the output shaft; and (e) disposed between the tube and the pinion in the axial direction, the tube and the pinion. A first elastic body having a predetermined coefficient of friction between the tube and the cover; and (f) being disposed between the tube and the cover in the axial direction, and being provided between the tube and the cover. And a second elastic body having a coefficient of friction greater than the coefficient of friction.