JP2949899B2 - Inertial dive starter - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an inertial dive type starter, and more particularly to an inertial dive type starter in which the stroke of a pinion meshing with a ring gear is increased to improve the engagement.

[0002]

2. Description of the Related Art In an inertial dive type starting device, when a drive gear of a starting device and a shaft supporting the gear are rotated by rotation of a starting motor, an outer member meshes with the shaft via a helical spline. Due to the inertia of the one-way clutch, the inner member of the one-way clutch and the pinion gear that rotates integrally with the inner member protrude in the axial direction of the shaft, and the pinion gear is fixed to the crankshaft of the internal combustion engine. Colliding with the ring gear, the pinion gear meshes with the ring gear while sliding on the end face of the ring gear. This state will be described with reference to FIG. FIG. 8 is a view illustrating a state in which the arrangement of the ring gear teeth 71, 71 along the peripheral surface of the ring gear is developed in a plane, and the pinion gear teeth 72 mesh with the ring gear teeth 71. The teeth 72 of the pinion gear advance in the direction of the arrow from a position spaced from the ring gear in the axial direction of the shaft, collide with the end face of the ring gear at the position shown by the broken line 73, and slide in the direction of the arrow in the circumferential direction of the ring gear. The teeth 72 of the pinion gear then advance in the axial direction as indicated by the dashed line 74 with the chamfers of the teeth 72 along the chamfers of the teeth 71 of the ring gear, and the adjacent teeth 71 of the ring gear at the position indicated by the dashed line 75. Collide with From this state, the pinion gear teeth 72 are prevented from sliding in the circumferential direction of the ring gear, advance in the axial direction along the colliding ring gear teeth 71, and meshing is completed.

In FIG. 8, the greater the meshing depth h (FIG. 8) when the pinion gear tooth 72 collides with the ring gear tooth 71 at the position indicated by the dashed line 75, the better the meshing performance. It is generally known that the damage to the pinion gear and the ring gear is relatively small. As a means for obtaining the engagement depth, as shown in FIG. 9, a one-way clutch 82 provided on a shaft 81 of a starting device is used.
The clutch outer 83 is screwed into the shaft 81 via a helical spline 84, and a cylindrical clutch inner 86 forming a driven side is provided inside a bowl-shaped enlarged diameter portion of the clutch outer 83 via a roller 85. The inner circumference of the sleeve 86 is the sleeve 8 of the pinion gear 87.
8 is interlocked with a straight spline, and a buffer device 89 made of an elastic material such as rubber or synthetic resin is interposed between the sleeve 88 of the pinion gear 87 and the bottom of the bowl-shaped enlarged diameter portion of the clutch outer 83. Kosho 56-1
No. 1074 is disclosed. According to the above device,
After the pinion gear 87 collides with a ring gear (not shown) (broken line 73 in FIG. 8), the forward movement of the pinion gear 87 is stopped, and the clutch outer 83 moves forward while compressing the shock absorber 89 so that the shock absorber 89 is located. After bending by a fixed amount, slide the pinion gear 87 on the end face of the ring gear,
Then, the pinion gear 87 can be ejected by the elasticity stored in the shock absorber 89 after sliding at the chamfered portions (broken line 74 in FIG. 8).

[0004]

As described above, in the inertial dive type starting device in which the shock absorber is disposed between the clutch outer of the one-way clutch and the pinion gear, when the pinion gear collides with the ring gear, the aforementioned engagement depth is reduced. In order to make h sufficiently large, a shock absorber having a spring characteristic of a relatively high load and a long stroke is more advantageous. However, in the case of the structure shown in FIG. 9, in order to use a shock absorber having a spring characteristic of a high load and a long stroke,
Considering that the shock absorber must be provided with a spring stress that can withstand the set load, the size of the shock absorber increases the size of the one-way clutch, making it unsuitable for mounting on an internal combustion engine. SUMMARY OF THE INVENTION It is an object of the present invention to provide an inertial dive starter having good engagement of a pinion gear with a ring gear without increasing the size of a one-way clutch.

[0005]

According to the present invention, a pinion gear is provided on a drive shaft so as to be rotatable and axially movable with respect to the shaft, and a drive-side member is screwed onto the drive shaft via a helical spline. An inertial plunger having a one-way clutch having a driven side member for pushing the pinion gear in the axial direction and integrally rotating the pinion gear based on the relative rotation between the drive shaft and the driving side member at the time of starting operation. In the starting apparatus, a first spring is sandwiched between a driving side member and a driven side member of the one-way clutch, and the relative movement of the two members by a predetermined dimension a in the axial direction of the driving shaft. A base is attached to one of the two members, between the first gap portion to be allowed and the driving-side member and the driven-side member, and the other portion is provided. A second gap having a free end facing the second shaft, and a second clearance portion in which both members are relatively close to and movable in an axial direction of the drive shaft. The spring constant is set to be smaller than the spring constant of the second spring, and the free end of the second spring faces the free end of the second spring in a free extension state of the second spring. And a member having a dimension c smaller than the dimension a.

[0006]

FIG. 1 is a partially cutaway side view of an embodiment of the present invention, and FIG. 2 is a sectional view of a main part thereof. In the drawing, a drive shaft 1 of a starting device is provided with a helical spline 2 on a part of its peripheral surface, and a drive side member 4 of a one-way clutch 3 is screwed onto the helical spline 2, and a driven side of the one-way clutch 3 is driven. The member 5 is rotatably and slidably supported on the drive shaft 1 via a bearing 6. The driven member 5
Has a pinion gear 7 integrally and coaxially formed at one end thereof. The drive-side member 4 of the one-way clutch 3 has a small-diameter cylindrical portion 41 having an inner peripheral surface formed with a spline portion meshing with the helical spline 2 as shown in FIG. 2, and a larger diameter than the small-diameter cylindrical portion 41. The large-diameter cylindrical part 42, the two cylindrical parts 41,
An annular portion 43 extending in the radial direction of the drive shaft 1 by connecting the shafts 42 is formed. The driven member 5 is a driving member 4.
Of the large-diameter cylindrical portion 41, a base cylindrical portion 51 having an inner peripheral surface that performs a one-way clutch function together with the roller 40, and a support cylindrical portion 52 having the pinion gear 7 formed therein. The drive shaft 1 is supported by bearings 6. A drive gear 8 is coaxially mounted on the drive shaft 1 at a position adjacent to the helical spline 2 so as to rotate integrally with the drive shaft 1 by a serration or a key. The drive gear 8 is a starting motor (not shown). ) Is engaged with the gear 91 formed on the shaft 9 which is rotated. At the other end of the drive shaft 1, a support cylinder 5 of a driven member 5 on which the pinion gear 7 is formed
2 is supported by a snap ring 12 fitted in a circumferential groove 11 formed in the drive shaft 1, and a support cylinder portion 5 of the driven side member 5 is formed.
A return spring 13 is interposed between the stopper 2 and the stopper 10. In this embodiment, when the starting motor is connected to the power source and the shaft 9 is rapidly rotated, the gear 9 is rotated.
1, the drive shaft 1 is rotated via the drive gear 8, and the engagement between the small-diameter cylindrical portion 41 of the drive side member 4 corresponding to the outer member of the one-way clutch 3 and the helical spline 2 of the drive shaft 1 and one direction. Due to the inertia of the clutch 3, together with the driven-side member 5 corresponding to the inner member, the shaft 3 suddenly starts moving in the axial direction of the drive shaft 1 against the urging force of the return spring 13, and a part of the tooth end surface of the pinion gear 7 Collide with a ring gear (not shown) coaxially fixed to the crankshaft of the internal combustion engine.

The free end 53 of the base cylinder portion 51 of the driven side member 5 of the one-way clutch 3 has a stepped portion formed by axially removing the end face of the outer peripheral portion and projecting the center of the free end 53 in an annular shape. The wall 54 is formed, and the annular portion 43 of the driving side member 4 is formed.
A concave bottom wall 44 is formed on the surface facing the step wall 54 by removing the inner diameter side, and the annular spring 14 (in the space formed between the step wall 54 and the bottom wall 44). This is referred to as a first spring), and the elastic force of the spring 14 is urged in the direction in which the driven member 5 is separated from the driving member 4.
A roller 4 is attached to the open end of the large-diameter cylindrical portion 42 of the driving side member 4.
A ring-shaped end plate (flat washer) 45 for preventing falling-off of the spring 0 is abutted, two semi-annular washers 46 are abutted on the outside thereof, and a spring 15 having a semi-circular outer shape is provided on the outside thereof. (This is referred to as a second spring) is brought into contact with two sheets, and the edge of the substantially bowl-shaped cover 16 made of a metal plate is attached to the entire outer peripheral surface of the large-diameter cylindrical portion 42. 15 and is caulked to the annular portion 43 side and fixed to the large-diameter cylindrical portion 42. The first spring 14 is a wave washer-shaped leaf spring having a plan shape shown in FIG. 3 and a cross section along a diameter line shown in FIG.
The annular inner peripheral edge makes contact with the step wall 54 of the driven-side member 5, and the annular outer peripheral edge makes contact with the bottom wall 44 of the drive-side member 4. The second spring 15 has a planar shape as shown in FIG. 5 and a side shape as shown in FIG. 6, and has a semicircularly extending peripheral connecting portion 6 in the planar shape.
A plurality of spring portions 63 having a trapezoidal planar shape are formed through a plurality of linear gaps 62 extending in the radial direction from 1, and a plate spring is formed in a dish shape having the peripheral connecting portion 61 as a peripheral edge. The semi-annular washer 46 at the opening end of the large-diameter cylindrical portion 42 of the drive-side member 4 and the cover 16 at the peripheral edge connecting portion 61
The free end 64 of the trapezoidal spring portion 63 is radially outwardly formed on the pinion gear 7 side of the base cylinder portion 51 of the driven side member 5 or on the base of the pinion gear. Is opposed to the supporting wall 55 toward the center. These springs 14 and 15 have a spring constant of the first spring 14
Is set to be much smaller than the spring constant of the spring 15 of FIG.

[0010] Between the free end 53 of the base cylinder portion 51 of the driven-side member 5 of the one-way clutch 3 and the bottom wall 44 of the driving-side member 4, when the first spring 14 is freely extended, the driving is performed. The shaft 1 has a gap of a predetermined dimension a in the axial direction (this is referred to as a first gap portion). The dimension between the semi-annular washer 46 fixed to the driving side member 4 and the support wall 55 formed on the driven side member 5 is larger than the dimension a in the free extension state of the first spring 14. A gap having a dimension b (this is referred to as a second gap);
And in the free extension state of the second springs 14, 15,
Free edge 6 of trapezoidal spring portion 63 of second spring 15
Between the support wall 4 and the support wall 55, a gap having a dimension c that is not larger than the dimension a is formed. Then, as described above, the starting motor is connected to the power source, and the driving side member 4 of the one-way clutch 3 is rapidly driven with the driven side member 5 due to the engagement with the helical spline 2 and the inertia of the one-way clutch 3. When the shaft 1 moves in the axial direction and a part of the tooth end surface of the pinion gear 7 collides with the ring gear (not shown), the shaft of the drive shaft 1 is moved between the base cylinder portion 51 of the driven member 5 and the roller 40. The driven member 5 starts to move relative to the driving member 4 in the axial direction, and the stepped wall 54 formed at the end of the base cylinder portion 51 of the driven member 5 and the driving member 4 The first shock-absorbing spring 14 starts to bend between the bottom wall 44 formed on the annular portion 43 and the free end 53 of the base cylinder portion 51 and the bottom wall formed on the annular portion 43 of the driving-side member 4. 4
4, the dimension a of the first gap portion decreases. When the amount of relative movement of the driven member 5 with respect to the drive member 4 in the axial direction reaches the dimension c, the support wall 55 formed on the base cylinder portion 51 of the driven member 5 becomes the spring portion 63 of the second spring 15. Abuts against the free edge 64 of the spring portion 63 and starts to deflect the spring portion 63. The elastic force due to the bending of the first spring 14 and the second spring 15 acts as a pressing force (load) of the tooth end surface of the pinion gear 7 with the ring gear, and the pressing force is indicated by a solid line X in FIG. As shown in the drawing, the first movement indicated by the alternate long and short dash line Y until the relative movement amount (spring stroke) of the driven side member 5 with respect to the driving side member 4 after the tooth end surface of the pinion gear 7 abuts on the ring gear reaches the dimension c. When the relative displacement exceeds the pressing force (spring load) generated by the spring 14 and the relative movement amount exceeds the dimension c, the pressing force (spring load) generated by the first spring 14 and the second spring 15 indicated by the broken line Z. Are synthesized.

Accordingly, when the chamfered portions of the teeth of the pinion gear 7 are rotated to a position where they can be engaged with the chamfered portions of the ring gear (the position indicated by a broken line 74 in FIG. 8), the driven side member 5 of the pinion gear 7 and the one-way clutch 3 is moved. First, the first spring 14 moves forward so as to protrude with a strong pressing force of the second spring 15, and the first spring 14 pushes out the driven side member 5 so as to compensate for the excess force. Further, the rotation of the drive shaft 1 causes the pinion gear 7 to rotate.
Of the pinion gear 7 or the driven cylindrical member 52 of the driven side member 5 after the tooth a of the contact gear abuts on the tooth adjacent to the tooth that has come into contact with the end face of the ring gear (at the position indicated by the one-dot chain line 75 in FIG. 8).
Is advanced until the end surface of the pinion abuts against the stopper 10, and the meshing of the pinion gear 7 with the ring gear is completed. The rotation of the drive shaft 1 after the pinion gear 7 meshes with the ring gear rotates the crank shaft of the internal combustion engine through the pinion gear 7 and the ring gear by the clutch action of the one-way clutch 3, and when the internal combustion engine starts, the one-way clutch 3 rotates. The driven side member 5 overruns the driving side member 4, and the one-way clutch 3 is returned to its original position by the return spring 13 by disconnecting the connection between the starting motor and the power source.

In the above embodiment, the pinion gear 7 is formed integrally with the driven member 5 corresponding to the clutch inner of the one-way clutch 3. However, the base cylinder in which the pinion gear 7 in the embodiment is formed integrally. The portion 51 and the clutch inner which abuts on the roller 40 may be formed separately, and both may be connected so as to rotate integrally by a serration or a key parallel to the axial direction of the drive shaft 1,
Further, the second spring 15 is formed by forming a semicircular inner edge connecting portion on the inner periphery in a planar shape and forming a plurality of spring portions radially outward from the inner edge connecting portion. The end of the spring portion may be fixed to the support wall 55 of the driven side member 5 so as to face the side surface of the semi-annular washer 46. Further, as the first and second springs 14 and 15, instead of the leaf springs shown, springs having different shapes such as coil springs or elastic springs having different materials such as rubber and synthetic resin can be used.

[0011]

According to the present invention, a pinion gear provided on a drive shaft so as to be rotatable and axially movable with respect to the drive shaft, and a drive-side member screwed to the drive shaft via a helical spline are provided. An inertial dive starter having a one-way clutch having a driven member for pushing the pinion gear in the axial direction and rotating integrally with the pinion gear based on the relative rotation between the drive shaft and the drive member during operation; It is about. When the driving shaft is rapidly rotated from the stationary state by the starting motor during the starting operation of the starting device, the one-way clutch has its inertia and the driving side member of the one-way clutch screwed into the driving shaft via the helical spline. By being mounted, the driven shaft abruptly advances in the axial direction of the drive shaft with the driven-side member of the one-way clutch and the pinion gear, and collides with the ring gear fixed to the crankshaft of the internal combustion engine, It is known that an internal combustion engine is started by rotating the pinion gear while meshing with the ring gear while rotating the pinion gear.

In the present invention, a first spring is sandwiched between a driving side member and a driven side member of the one-way clutch, and a relative distance between the two members by a predetermined dimension a in the axial direction of the driving shaft. A base is attached to one of the two members between the driving side member and the driven side member of the one-way clutch in addition to the first gap portion allowing the proximity movement and the first gap portion. A second spring having a free end directed to the other member is provided, and a second gap is provided in which both members are relatively movable in the axial direction of the drive shaft. When the pinion gear advanced with the one-way clutch collides with the ring gear during the starting operation, the axial movement of the pinion gear is stopped at the end face of the ring gear, but the driving-side member and the driven-side member of the one-way clutch include: The driving side member is first movable in the axial direction of the driving shaft with respect to the driving side member of the one-way clutch within the range of the dimension a allowed by the first clearance. Flex the spring of
Next, when it advances by the dimension c of the second gap, the second gap
To further advance. At this time, the pressing force of the pinion gear against the ring gear is increased by the bending load of both springs. Thus, the impact force in the axial direction when the pinion gear collides with the ring gear is absorbed by the first and second springs. At this time, since the combined spring characteristics of the two springs are set, for example, as shown in FIG. 7, the combined amount of flexure with the same flexure load and the same amount of flexure is achieved by a single spring. The space for the spring can be reduced.

The drive side member moves forward with respect to the driven side member within the range of the dimension a of the first gap portion, and the advance force is larger than the bending load of the first and second springs. When it comes, it advances by the dimension a, when the driven side member and the drive side member come into contact with each other, and when it becomes smaller,
When the forward force balances the load of the first and second springs, the one-way clutch rotates with the rotation of the shaft by the action of the helical spline, and a position where the pinion gear properly meshes with the ring gear is determined. , Slide the end face of the ring gear. Thereby, when the teeth of the pinion are brought to the positions where they mesh properly with the teeth of the ring gear, the driven member of the one-way clutch for pushing the pinion gear is pushed by the bending load of the first and second springs. Since the pressure is acting, the pinion gear and the driven member first advance so as to jump out by the load stored in the second spring, and the load stored in the first spring is compensated by the load stored in the first spring. And the driven member is pushed forward.
As a result, the one-way clutch is further rotated, and the engagement depth h (see FIG. 8) of the pinion gear with the ring gear when the pinion gear contacts the next tooth of the ring gear can be increased. Next, since the pinion gear abuts on the next tooth of the ring gear, circumferential sliding is prevented, and the pinion gear advances in the axial direction along the teeth of the ring gear to complete meshing.

As described above, according to the present invention, in the starting operation of the starting device, the impact force of the collision against the ring gear due to the rapid advance of the pinion gear is determined by the driven member of the one-way clutch pushing the pinion gear and the one-way clutch of the one-way clutch. A pinion spring that can be absorbed by the first and second springs provided between the driving side member and obtains a meshing depth when meshing with the ring gear is provided by a long stroke, low load first spring and a short stroke, high pinion spring. By using in combination with the second spring of load, each spring can be used within the allowable stress without increasing the size of the pinion spring, and the spring characteristics of a long stroke and high load can be obtained. This has the effect of improving the engagement and durability of the starting device.

[Brief description of the drawings]

FIG. 1 is a partially cutaway side view of one embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part thereof.

FIG. 3 is a plan view of a first spring.

FIG. 4 is a cross-sectional view along the diameter line.

FIG. 5 is a plan view of a second spring.

FIG. 6 is a side view thereof.

FIG. 7 is a diagram showing a combined load of the first and second springs.

FIG. 8 is an explanatory diagram of a state where a pinion gear meshes with a ring gear.

FIG. 9 is a cross-sectional view of a main part of a one-way clutch in a conventional inertial dive starter.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 drive shaft 2 helical spline 3 one-way clutch 4 its drive side member 5 its driven side member 7 pinion gear 14 first spring 15 second spring 40 roller 41 small diameter cylindrical portion of drive side member 42 large diameter cylindrical portion 43 thereof Annular part 44 Its bottom wall 51 Base cylinder part of driven side member 52 Its support cylinder part 53 Free end 54 Its step wall 55 Its support wall

Claims (1)

(57) [Claims] 1. A pinion gear provided on a drive shaft so as to be rotatable and axially movable with respect to the drive shaft,
A drive-side member is screwed into the drive shaft via a helical spline, and at the time of a start operation, the pinion gear is pushed in the axial direction and integrally rotated based on a relative rotation between the drive shaft and the drive-side member. An inertial diving starter having a one-way clutch having a driven member to be driven, wherein a first spring is sandwiched between a driving member and a driven member of the one-way clutch, and a shaft of the driving shaft is provided. A first gap portion allowing relative approach movement of both members by a predetermined dimension a in the direction, and a base portion attached to one of the two members, between the driving side member and the driven side member, A second spring having a free end directed to the other member is disposed, and both members are relatively movable in the axial direction of the drive shaft.
The first spring sets the spring constant of the first spring to be smaller than the spring constant of the second spring, and in the free extension state of the second spring, An inertial dive type starting device characterized in that a space of a dimension (c) smaller than the dimension (a) is separated between a free end and the other member facing the free end.