JP2000170882A - Involute gear device, starter and starting mechanism of engine - Google Patents

Involute gear device, starter and starting mechanism of engine

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Publication number
JP2000170882A
JP2000170882A JP11278162A JP27816299A JP2000170882A JP 2000170882 A JP2000170882 A JP 2000170882A JP 11278162 A JP11278162 A JP 11278162A JP 27816299 A JP27816299 A JP 27816299A JP 2000170882 A JP2000170882 A JP 2000170882A
Authority
JP
Japan
Prior art keywords
tooth
intersection
gear
driven gear
involute
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP11278162A
Other languages
Japanese (ja)
Inventor
Yasuhiko Maruhashi
康彦 丸橋
Original Assignee
Hitachi Ltd
株式会社日立製作所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP27694498 priority Critical
Priority to JP10-276944 priority
Application filed by Hitachi Ltd, 株式会社日立製作所 filed Critical Hitachi Ltd
Priority to JP11278162A priority patent/JP2000170882A/en
Publication of JP2000170882A publication Critical patent/JP2000170882A/en
Pending legal-status Critical Current

Links

Abstract

(57) [Summary] [PROBLEMS] To prevent wear of teeth end faces and significantly improve durability of a gear device without deteriorating meshing properties of gears. When a ridge line between a chamfered portion in the anti-rotational direction of a tooth of a drive gear and an end face and a ridge line between a chamfered portion in a rotational direction of a tooth of a driven gear and an end surface are viewed from the axial direction, A chamfered portion is provided so as to form an involute curve having the same shape as each tooth profile involute curve.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an involute gear device, a starter, and an engine starting mechanism, and more particularly, to an involute in which at least one of a driving gear and a driven gear slides in an axial direction to engage and disengage. The present invention relates to a gear device, and a starter and an engine starting mechanism using the same.

[0002]

2. Description of the Related Art A drive gear and a driven gear are provided. The drive gear is slid in the axial direction, meshes with each other, disengages, and is chamfered in a counter-rotating direction of a tooth surface of the drive gear and a ridge of an end surface. 2. Description of the Related Art An involute gear device having a chamfer in a rotational direction of a ridge portion between a tooth surface and an end surface of a driven gear is used for a starting mechanism of an engine of an automobile or the like. The size of the chamfered portion in the anti-rotational direction of the teeth of the pinion as the drive gear and the chamfered portion in the rotational direction of the teeth of the ring gear as the driven gear are the end faces of the teeth when viewed from the axial direction of the teeth. A large chamfer from about 30% of the area of the part to 50% or more in some cases is provided. As an example in which the involute gear device is applied to a starter for starting an engine, a technique described in Japanese Patent Application Laid-Open No. 62-85172 is known. In this starter, a pinion of a starter, which is a drive gear, slides and rotates in an axial direction, meshes with a ring gear, which is a driven gear, and starts the engine.

Japanese Patent Laid-Open No. 3-285 discloses a chamfered shape of a gear of such an involute gear device.
No. 65, Japanese Unexamined Patent Publication No.
There are JP-A-4-146022 and JP-A-2-152719.

[0004]

Problems to be Solved by the Invention
In the prior art described in Japanese Patent Laid-Open Publication No. H10-260, the anti-rotational tooth bevel chamfers of the teeth of the pinion serving as the driving gear, and the rotational direction tooth chamfers of the teeth of the ring gear serving as the driven gear are provided with the center line of the tooth. When the starter operates, when the pinion as the drive gear and the end face of the tooth of the ring gear as the driven gear collide, the contact area of the contact portion of the tooth end face is small, and the contact area of the contact part is small. The contact surface pressure increases. For this reason, wear of the end faces of the teeth is promoted, which is disadvantageous in durability.

Therefore, when the pinion and the end face of the tooth of the ring gear collide with each other, the contact area of the contact portion of the tooth end surface is increased to reduce the contact surface pressure of the contact portion. It is conceivable to reduce the rotation direction tooth chamfer and the ring gear tooth chamfer in the rotation direction, but from the position where the pinion starts rotating and the collision between the pinion and the end face of the ring gear tooth is released. In addition, the angle at which the pinion can rotate before the teeth of the pinion and the ring gear mesh with each other becomes small, and a new problem arises in that the meshing performance of the pinion is reduced.

[0006] Further, the technology related to the shape of the chamfer of the gear of the involute gear device described in the above-mentioned Japanese Patent Application Laid-Open No. 3-28565 is a technology in which the tooth tip is simply obliquely deleted. The point cannot be solved.

SUMMARY OF THE INVENTION An object of the present invention is to prevent wear of the end faces of the teeth and significantly improve the durability of the gear device without deteriorating the meshing properties of the gear.

[0008]

SUMMARY OF THE INVENTION The object of the present invention is to provide a driving gear in which the ridge line between the tooth surface chamfered in the anti-rotational direction and the end face, and the ridge line between the tooth surface chamfered in the rotation direction of the driven gear tooth and the end surface. This is achieved by providing a chamfered portion so as to have an involute curve having the same shape as each tooth profile involute curve when viewed from the axial direction.

The above object is also achieved at the point where the first ridge line between the chamfer of the tooth of the drive gear in the anti-rotation direction and the end face intersects the second ridge line between the chamfer of the tooth tip and the end face. Is the first intersection, passing through the first intersection, the involute curve of the same shape as the tooth profile involute curve of the drive gear, and the distance obtained by subtracting the tip circle radius of the driven gear from the center distance between the drive gear and the driven gear The point at which the drive gear having the radius intersects the virtual cylinder on the same axis as the second intersection, the point at which the first ridge line intersects with the virtual cylinder is the third intersection, and the first intersection and the second intersection The anti-rotation of the teeth of the drive gear is performed so that the angle formed by the virtual line segment formed between the intersection and the virtual line formed between the first intersection and the third intersection is 2 degrees or less. This is achieved by providing a configuration in which a directional tooth surface chamfer is provided.

The object of the present invention is to determine a point at which a first ridge line between the chamfered portion and the end face in the rotational direction of the tooth of the driven gear intersects a second ridge line between the chamfered portion and the end face of the tooth. The first intersection, the involute curve passing through the first intersection and having the same shape as the tooth profile involute curve of the driven gear, and the distance obtained by subtracting the tip circle radius of the driving gear from the center distance between the driving gear and the driven gear is the radius. The point at which the driven gear intersects the virtual cylinder on the same axis as the second intersection, the point at which the first ridgeline intersects with the virtual cylinder is the third intersection, and the first intersection and the second intersection And the rotation direction tooth of the driven gear so that the angle formed by the virtual line segment formed between the first intersection point and the virtual line segment formed between the first intersection point and the third intersection point is 2 degrees or less. This is achieved by providing a configuration in which a chamfer is provided.

As a result, the shapes of the chamfers in the anti-rotational direction of the teeth of the pinion as the drive gear and the chamfers in the rotational direction of the teeth of the ring gear as the driven gear are optimized.
From the position where the collision between the pinion and the end face of the ring gear tooth is released, while ensuring the angle at which the pinion can rotate until the pinion and the ring gear tooth mesh, the contact area of the contact portion of the tooth end face is secured, By reducing the surface pressure, it is possible to prevent wear of the end surfaces of the teeth and improve durability.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

The definitions of symbols related to figures in the drawings are collectively described below.

La: the center distance between the driving gear 1 and the driven gear 2 R1: the radius of the addendum circle of the drive gear 1 R2: the radius of the addendum circle of the driven gear 2 B1: between the bevel 1b and the end face 1d of the tooth 1a Ridge line B2 ... Ridge line between tip chamfered portion 1c of tooth 1a and end surface 1d P1 ... Intersection point of ridge line B1 and ridge line B2 C1 ... Distance L1 (L1 = La-R2) obtained by subtracting tip radius R2 of driven gear 1 from center distance La. ) Is a virtual cylinder coaxial with the drive gear 1 having a radius of G1... A base circle of the drive gear 1. A1... An involute curve passing through the intersection P1 with an involute curve having the same shape as the tooth shape involute curve of the drive gear 1. Intersection point with the cylinder C1 P3 ... Intersection point between the ridge line B1 and the virtual cylinder C1 θ1 ... Angle formed by the line segment P1-P2 and the line segment P1-P3 B3 ... Bevel face bevel 2b and end face 2d of the tooth 2a Ridge line B4 ... Ridge line between tip chamfered portion 2c of tooth 2a and end surface 2d P4 ... Intersection point of ridge line B3 and ridge line B4 C2 ... Distance L2 (L2 = La-R1) obtained by subtracting tip radius R1 of drive gear 2 from center distance La. ) A virtual cylinder coaxial with the driven gear 2 having a radius of G2: a base circle of the driven gear 2 A2: an involute curve passing through the intersection P4 with an involute curve having the same shape as the tooth shape involute curve of the driven gear 2 P5: an involute curve A2 and a virtual Intersection point P6 with the cylinder C2 Intersection point between the ridge line B3 and the virtual cylinder C2 θ2 Angle formed between the line segment P4-P5 and the line segment P4-P6 θe Contact between the end faces of the teeth of the drive gear 1 and the driven gear 2 disappears Angle at which the drive gear 1 rotates from the position to a position where the drive gear 1 meshes with the driven gear 2 Le: the axial movement distance when the drive gear 1 meshes with the driven gear 2 5 ... reverse rotation direction dedendum side chamfer portion 1e and the end surface 1 of the tooth 1a
d ridge line B6 ... beveled edge 1f and end face 1 in anti-rotational direction of tooth 1a
The ridge line d7 The intersection point between the ridge line B5 and the ridge line B6 P8 The intersection point between the ridge line B5 and the virtual cylinder C1 The intersection point between the ridge line B6 and the tooth profile curve A3 The ridge line having the same shape as the tooth profile involute curve of the drive gear 1 Involute curve existing on the chamfered side of B5 and ridge line B6 A4... Involute curve existing on the end face side of ridge line B5 and ridge line B6 with the same shape as the tooth shape involute curve of drive gear 1 FIG. FIG. 3 is a side view illustrating a configuration of a starting mechanism including a pinion and a ring gear. Electric motor 7
Is provided with a drive gear 1 which is a pinion rotated by an electric motor 7, and the drive gear 1 moves in the axial direction, and is mounted on a shaft 5 connected to a crankshaft of an engine (not shown). , The crankshaft rotates, and the engine starts. FIG. 1 is a side view showing a configuration example of the gear device of the starting mechanism shown in FIG. The drive gear 1 rotates around the shaft 4 with the rotation of the shaft 4 and can move in the axial direction. The driven gear 2 rotates about the shaft 5 and the shaft 5 also rotates. The drive gear 1 and the driven gear 2 are opposed to each other with a center distance La therebetween. The drive gear 1 slides and rotates in the axial direction of the shaft 4 to engage with and be disengaged from the driven gear 2. As a result, the rotation of the shaft 4 is changed from the driving gear 1 to the driven gear 2.
And transmitted to the shaft 5.

When this involute gear device is used for a starter of an engine of an automobile or the like, the shaft 4 is connected to the motor of the starter, and the shaft 5 is connected to the crankshaft of the engine. To start the engine.

FIGS. 2 to 6 show a first embodiment of the present invention.

FIG. 2 is a perspective view showing a chamfered shape of the driving gear 1. As shown in FIG. The ridgeline B1 between the tooth 1a of the drive gear 1 in the anti-rotation direction tooth bevel 1b and the end face 1d is an involute curve having the same shape as the tooth profile involute curve of the drive gear 1 when viewed from the axial direction. .

FIG. 3 is a perspective view showing a chamfered shape of the driven gear 2. The ridgeline B2 between the rotation direction tooth flank 2b of the tooth 2a of the driven gear 2 and the end face 2d is an involute curve having the same shape as the tooth shape involute curve of the driven gear 2 when viewed from the axial direction.

Next, the operation of the thus configured apparatus will be described. 4A and 4B show a meshing state of the driving gear 1 and the driven gear 2 during operation, wherein FIG. 4A is a front view, and FIG. 4B is a sectional view taken along line V-V of FIG. FIG. 5 also shows the meshing state of the driving gear 1 and the driven gear 2 during operation, and FIG.
Is a front view, and (b) is a WW sectional view of (a). FIG.
Represents the meshing state of the driving gear 1 and the driven gear 2 during operation, (a) is a front view, and (b) is XX of (a).
It is sectional drawing. 7A and 7B show a meshing state of the driving gear 1 and the driven gear 2 in operation in the related art, in which FIG. 7A is a front view, and FIG. 7B is a sectional view taken along the line Y-Y of FIG.

When the drive gear 1 is transferred to the driven gear 2, the end face 1d of the tooth 1a of the drive gear 1 and the tooth 2 of the driven gear 2
When the end face 2d does not collide, the drive gear 1 meshes with the driven gear 2 as it is. As shown in FIG. 4, when the end face 1 d of the tooth 1 a of the drive gear 1 collides with the end face 2 d of the tooth 2 a of the driven gear 2, the drive gear 1 is pressed against the driven gear 2. 1 rotates, and the interference between the end face 1d of the tooth 1a of the drive gear 1 and the end face 2d of the tooth 2a of the driven gear 2 disappears at the position shown in FIG. When the drive gear 1 further rotates, as shown in FIG. 6, the drive gear 1 moves in the axial direction while rotating and meshes with the driven gear 2.

As shown in FIG. 7, the anti-rotational tooth chamfered portion 1b of the tooth 1a of the conventional driving gear 1 and the rotationally toothed chamfered portion 2b of the tooth 2a of the driven gear 2 are respectively formed. If the chamfers are parallel to the center line of the teeth, the contact areas S3, S4 of the contact portions 3c, 3d of the tooth end faces when the respective tooth end faces of the driving gear 1 and the driven gear 2 collide.
(S3 + S4) is small, and the contact surface pressure of the contact portions 3c and 3d increases.

On the other hand, in the case of the present invention, the contact areas S1, S2 of the contact portions 3a, 3b on the end surfaces of the teeth in FIG.
Is (S1 + S2), and the contact area of these contact portions is in the relationship of (S1 + S2> S3 + S4), and the contact area of the contact portion on the end face of the tooth is larger than that of the related art, and the contact area of the contact portion is larger. By reducing the surface pressure, it is possible to prevent wear on the end surfaces of the teeth. In addition, the angle θe at which the drive gear 1 rotates from the position shown in FIG. 5 where the end faces of the teeth of the drive gear 1 and the driven gear 2 are no longer in contact to the position shown in FIG. Can secure an angle equivalent to that of the prior art.
Is also equivalent to the conventional moving distance Le in the case of meshing with the driven gear 2, and the meshing of the driving gear 1 does not deteriorate.

As described above, according to the first embodiment of the present invention, the end face of the tooth is prevented from being worn and the durability of the gear device is greatly improved without deteriorating the meshing property of the gear. be able to.

FIGS. 8 to 9 show a second embodiment of the present invention. FIG. 8 is a front view showing a chamfered shape of the driving gear 1 and FIG. 9 is a front view showing a chamfered shape of the driven gear 2. . FIG.
Shows the shape when the teeth 1a of the drive gear 1 are viewed from the axial direction.

In FIG. 8, the ridge line between the chamfered portion 1b in the anti-rotation direction of the tooth 1a and the end surface 1d is B1, the ridge line between the tip chamfered portion 1c of the tooth 1a and the end surface 1d is B2, and the ridge line B1
And the intersection of the ridge line B2 is P1. A virtual cylinder coaxial with the drive gear 1 having a radius equal to a distance L1 (L1 = La-R2) obtained by subtracting a tip radius R2 of the driven gear 2 from a center distance La between the drive gear 1 and the driven gear 2 is defined as C1. The center of the base circle is on the central axis of the drive gear 1, and among the involute curves having the same shape as the tooth profile involute curve of the drive gear 1, the involute curve passing through the intersection P1 is defined as A1.
The intersection of the involute curve A1 and the virtual cylinder C1 is P2
When the intersection of the ridge line B1 and the virtual cylinder C1 is P3, the anti-rotation direction of the teeth 1a of the drive gear 1 is set so that the angle θ1 formed by the line segment P1-P2 and the line segment P1-P3 is 2 degrees or less. A tooth flank chamfer 1b is provided.

The ridge line between the tooth surface chamfered portion 1b in the anti-rotation direction of the tooth of the drive gear 1 and the end surface 1d is at least a straight line, a circular arc convex on the tooth flank side of the tooth, and a radius of curvature on the tooth bottom side. It may be one of the smaller clothoid curves convex to the tooth side.

FIG. 9 shows the shape when the teeth 2a of the driven gear 2 are viewed from the axial direction. In FIG. 9, the ridge line between the tooth surface chamfered portion 2b and the end surface 2d of the tooth 2a is B3, and the ridge line between the tip chamfered portion 2c and the end surface 2d of the tooth 2a is B4.
And the intersection of the ridge line B3 and the ridge line B4 is P4. A virtual cylinder coaxial with the driven gear 2 having a radius equal to a distance L2 (L2 = La-R1) obtained by subtracting a tip radius R1 of the driving gear 1 from a center distance La between the driving gear 1 and the driven gear 2 is denoted by C2.
The center of the base circle is on the central axis of the driven gear 2, and among the involute curves having the same shape as the tooth profile involute curve of the driven gear 2, the involute curve passing through the intersection P4 is defined as A2. When the intersection of the involute curve A2 and the virtual cylinder C2 is P5 and the intersection of the ridgeline B2 and the virtual cylinder C2 is P6, the angle θ2 formed by the line segment P4-P5 and the line segment P4-P6 is 2 degrees or less. 2a of the driven gear 2
Are provided in the rotational direction.

The ridge line between the chamfered portion 2b in the rotational direction of the tooth of the driven gear 2 and the end surface 2d is at least a straight line,
It is preferable to use either a convex arc on the tooth surface side of the tooth or a clothoid curve convex on the tooth surface side with a smaller radius of curvature on the tooth bottom side.

Even when the driving gear 1 and the driven gear 2 are meshed with each other, the end faces of the teeth are prevented from being worn and the durability of the gear device is greatly improved without deteriorating the meshing properties of the gears. Can be.

FIG. 10 shows a third embodiment of the present invention.
FIG. 10 is a front view showing a chamfered shape of the drive gear 1.
FIG. 10 shows the shape when the teeth 1a of the drive gear 1 are viewed from the axial direction.

In FIG. 10, the ridge line between the root 1a of the tooth 1a in the anti-rotation direction and the end face 1d is B5, and the ridge line 1f of the tip 1a in the anti-rotation direction and the ridge line of the end face 1d are B6.
And the intersection of the ridge line B5 and the ridge line B6 is P7. A virtual cylinder coaxial with the drive gear 1 having a radius L1 (L1 = La−R2) obtained by subtracting a tip radius R2 of the driven gear 2 from a center distance La between the drive gear 1 and the driven gear 2 is denoted by C1, and a ridgeline is provided. The point at which B5 and virtual cylinder C1 intersect is P8. The intersection of the ridge line B6 and the tooth profile curve is P9. Also,
When the drive gear 1 is viewed from the axial direction, the ridge line B5 and the ridge line B
6, an involute curve A3 having the same shape as the tooth profile involute curve of the drive gear 1 existing on the chamfer side;
5 and an involute curve A4 having the same shape as the tooth profile involute curve of the driving gear 1 existing on the end face side of the ridge line B6 are located at positions shifted from each other by two degrees in the rotation direction of the driving gear 1, and the intersection points P7 and P8 And the intersection P9 exists between the involute curve A3 and the involute curve A4.

Even with such a drive gear 1, wear of the end faces of the teeth can be prevented and the durability of the gear device can be greatly improved without deteriorating the meshing properties of the gears.

As described above, according to the configuration described in the embodiment, the tooth end faces of the drive gear and the driven gear collide with each other at the time of gear engagement without deteriorating the meshing properties of the gears. By securing the contact area of the contact portion and reducing the contact surface pressure of the contact portion, wear of the end faces of the teeth of the drive gear and the driven gear can be prevented, and the durability of the gear device can be greatly improved. .

[0034]

As described above, according to the present invention, it is possible to prevent the wear of the end faces of the teeth and to greatly improve the durability of the gear device without deteriorating the meshing property of the gears. .

[Brief description of the drawings]

FIG. 1 is a side view showing a configuration example of a gear device.

FIG. 2 is a perspective view showing the first embodiment of the present invention and showing a chamfered shape of teeth of a driving gear.

FIG. 3 is a perspective view showing the first embodiment of the present invention and showing a chamfered shape of teeth of a driven gear.

FIG. 4 is a front view and a cross-sectional view showing the first embodiment of the present invention, showing a meshing state of the driving gear and the driven gear during operation.

FIG. 5 is a front view and a cross-sectional view showing the first embodiment of the present invention, showing a meshing state of the driving gear and the driven gear during operation.

FIG. 6 shows the first embodiment of the present invention, and is a front view and a sectional view showing a meshing state of the driving gear and the driven gear during operation.

7A and 7B are a front view and a cross-sectional view illustrating a meshing state of a driving gear and a driven gear according to the related art during operation.

FIG. 8 is a front view showing a second embodiment of the present invention and showing a chamfered shape of teeth of a drive gear.

FIG. 9 is a front view showing a second embodiment of the present invention and showing a chamfered shape of a tooth of a driven gear.

FIG. 10 is a front view showing a third embodiment of the present invention and showing a chamfered shape of teeth of a drive gear.

FIG. 11 is a side view showing a configuration of a starting mechanism including a pinion of a starter and a ring gear.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Driving gear, 1a, 2a ... Teeth, 1b ... Bevel part of anti-rotation direction tooth surface, 1c, 2c ... Tip bevel part, 1d, 2d ...
End face, 2 ... driven gear, 2b ... bevel on the tooth surface in the rotation direction.

Claims (13)

[Claims]
1. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. In an involute gear device in which one or both of the anti-rotation direction of the ridge portion of the tooth surface and the end surface of the driving gear and the rotation direction of the ridge portion of the tooth surface and the end surface of the driven gear are chamfered, An anti-rotational tooth chamfer of the drive gear teeth and a rotational tooth chamfer of the driven gear teeth are provided along each tooth surface, and the tooth surface chamfers and end surfaces of each tooth are provided. An involute gear device characterized in that when viewed from the axial direction, the ridge line of the involute gear is constituted by an involute curve having the same shape as each tooth profile involute curve.
2. The ridge line between the chamfer of the tooth of the drive gear in the anti-rotation direction and the end face of the tooth of the drive gear is at least a straight line, a convex arc on the tooth flank side of the tooth, and a tooth with a smaller radius of curvature on the tooth bottom side. The involute gear device according to claim 1, wherein the involute gear device is any one of a clothoid curve that is convex on the surface side.
3. The ridge line between the chamfered portion in the rotational direction of the tooth of the driven gear and the end face is at least a straight line, a circular arc convex on the tooth flank side of the tooth, and the tooth surface with a smaller radius of curvature on the tooth bottom side. The involute gear device according to claim 1, wherein the involute gear device is any one of a clothoid curve that is convex on the side.
4. A drive gear having an involute tooth profile chamfered in the anti-rotation direction of the ridge portion between the tooth surface and the end surface, the drive gear being slidable in the axial direction of the rotation shaft, and rotating the drive gear. A starter comprising a motor to be driven, wherein the ridge line between the tooth surface chamfered portion in the anti-rotation direction of the tooth of the drive gear and the end face is formed of an involute curve having the same shape as the tooth profile involute curve when viewed from the axial direction. A starter characterized by:
5. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. An involute gear device in which one or both of the tooth surface of the driving gear and the rotation direction of the ridge portion of the driven gear are chamfered, and An electric motor for rotating a driving gear, the starting mechanism of the engine, wherein the anti-rotational tooth chamfer of the teeth of the drive gear of the involute gear device and the rotational chamfer of the teeth of the driven gear are chamfered. An involute that is applied along each tooth surface and has the same shape as each tooth profile involute curve when the ridge line between the tooth surface chamfer and the end surface of each tooth is viewed from the axial direction. An engine starting mechanism characterized by being constituted by a curve.
6. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. In an involute gear device in which one or both of the anti-rotation direction of the ridge portion of the tooth surface and the end surface of the driving gear and the rotation direction of the ridge portion of the tooth surface and the end surface of the driven gear are chamfered, A point at which a first ridge line between the chamfered portion and the end face in the anti-rotational direction of the tooth of the drive gear intersects with a second ridge line between the chamfered portion and the end face of the tooth is defined as a first intersection, An involute curve having the same shape as the tooth shape involute curve of the drive gear passing through the first intersection, and a radius obtained by subtracting a tip circle radius of the driven gear from a center distance between the drive gear and the driven gear. Drive teeth The point where the car and the virtual cylinder on the same axis intersect is the second intersection, the point where the first ridgeline intersects with the virtual cylinder is the third intersection, and the first intersection and the second intersection The teeth of the drive gear are formed such that the angle formed by a virtual line segment formed between the intersection and the virtual line formed between the first intersection and the third intersection is 2 degrees or less. An involute gear device, wherein the anti-rotational tooth flanks are provided.
7. A drive gear, wherein a tooth profile chamfered in the anti-rotation direction of the ridge portion between the tooth surface and the end surface is formed as an involute tooth profile, and is slidable in the axial direction of the rotation shaft. And at least a rotating electric motor,
In a starter for driving a driven gear attached to an engine to start an engine, a first ridge line between a chamfered portion and an end surface in a non-rotational direction of teeth of the drive gear, and a chamfered portion and an end surface of the tooth. The first intersection is defined as the point where the second ridge line intersects with the first ridge line, and the involute curve having the same shape as the tooth profile involute curve of the drive gear passing through the first intersection and the center of the drive gear and the driven gear A point where the drive gear and the virtual cylinder on the same axis having a radius equal to a distance obtained by subtracting the tip circle radius of the driven gear from the distance intersects a second intersection point, the first ridge line and the virtual cylinder are The intersection point is a third intersection point, and a virtual line segment formed between the first intersection point and the second intersection point and a virtual line segment formed between the first intersection point and the third intersection point So that the angle between the line and the line is less than 2 degrees A starter, wherein the anti-rotational tooth flanks of the teeth of the drive gear are provided.
8. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. In an involute gear device in which one or both of the anti-rotation direction of the ridge portion of the tooth surface and the end surface of the driving gear and the rotation direction of the ridge portion of the tooth surface and the end surface of the driven gear are chamfered, A point at which a first ridge line between the chamfered portion in the rotational direction of the tooth of the driven gear and the end face and a second ridge line between the chamfered portion and the end face of the tooth are defined as a first intersection, An involute curve passing through one intersection and having the same shape as the tooth profile involute curve of the driven gear; and the driven having a radius obtained by subtracting the tip radius of the driving gear from the center distance between the driving gear and the driven gear. tooth The point where the car and the virtual cylinder on the same axis intersect is the second intersection, the point where the first ridgeline intersects with the virtual cylinder is the third intersection, and the first intersection and the second intersection Teeth of the driven gear so that an angle formed by a virtual line segment formed between the intersection and the virtual line formed between the first intersection and the third intersection is 2 degrees or less. An involute gear device characterized in that the rotation direction tooth flanks are provided.
9. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. An involute gear device in which one or both of the tooth surface of the driving gear and the rotation direction of the ridge portion of the driven gear are chamfered, and An electric motor for rotating the drive gear, the engine starting mechanism comprising: a first ridge line between the anti-rotation direction tooth face chamfered portion and the end face of the tooth of the drive gear; and a tip chamfered portion and an end face of the tooth. A point at which the second ridge line intersects is defined as a first intersection, and an involute curve having the same shape as the tooth shape involute curve of the drive gear passing through the first intersection and a center distance between the drive gear and the driven gear. A point at which the drive gear having the radius obtained by subtracting the tip circle radius of the driven gear and the virtual cylinder on the same axis intersects as a second intersection, and the first ridge line intersects with the virtual cylinder. Let a point be a third intersection, a virtual line segment formed between the first intersection and the second intersection, and a virtual line segment formed between the first intersection and the third intersection And the anti-rotational tooth bevel chamfers of the teeth of the drive gear are provided so that the angle between them is 2 degrees or less. The point at which the third ridge line intersects with the fourth ridge line between the chamfered portion and the end face of the tooth is defined as a fourth intersection, and the involute having the same shape as the tooth profile involute curve of the driven gear passing through the fourth intersection From the curve and the center distance between the drive gear and the driven gear, A point at which the driven gear having a radius equal to a distance obtained by subtracting the tip circle radius and the virtual cylinder on the same axis intersects as a fifth intersection, and a point at which the fourth ridge line intersects with the virtual cylinder is sixth. And an angle between an imaginary line segment formed between the fourth intersection point and the fifth intersection point and an imaginary line segment formed between the fourth intersection point and the sixth intersection point. An engine starting mechanism provided with the chamfered portions in the rotational direction of the teeth of the driven gear so that the rotation angle is less than or equal to 2 degrees.
10. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. In an involute gear device in which one or both of the anti-rotation direction of the ridge portion of the tooth surface and the end surface of the driving gear and the rotation direction of the ridge portion of the tooth surface and the end surface of the driven gear are chamfered, A first intersection point is defined as a point at which a first ridge line between the anti-rotational direction root chamfered portion and the end face of the tooth of the drive gear and a second ridge line between the anti-rotational direction tip side chamfered portion and the end surface of the tooth intersect. A point at which the first ridge line intersects with a virtual cylinder having a radius equal to a distance obtained by subtracting a tip radius of the driven gear from a center distance between the driving gear and the driven gear is defined as a second intersection. ,
The intersection between the second ridge line and the tooth profile curve is defined as a third intersection. Further, when the drive gear is viewed from the axial direction, a first involute curve having the same shape as a tooth profile involute curve of the drive gear present on the chamfer side of the first ridge and the second ridge, A first ridgeline and a second involute curve having the same shape as the tooth profile involute curve of the drive gear existing on the end face side of the second ridgeline exist at positions shifted by two degrees in the rotation direction of the drive gear. The first intersection, the second intersection, and the third intersection are
An involute gear device that exists between the first involute curve and the second involute curve.
11. A drive gear having an involute tooth profile which is chamfered in the anti-rotation direction of a ridge portion between a tooth surface and an end surface and slidable in the axial direction of a rotation shaft; A starter configured to drive a driven gear attached to the engine to start the engine, wherein the first ridgeline of the tooth of the drive gear is formed in a counter-rotating direction bevel and an end face. The point at which the second ridgeline of the tooth in the anti-rotational direction bevel and the end face intersects is defined as a first intersection, and the first ridgeline and the center distance between the driving gear and the driven gear are determined from the center distance. A point at which the virtual cylinder having a radius equal to the distance obtained by subtracting the tip circle radius of the driven gear intersects with the second intersection,
The intersection between the second ridge line and the tooth profile curve is defined as a third intersection. Further, when the drive gear is viewed from the axial direction, a first involute curve having the same shape as a tooth profile involute curve of the drive gear present on the chamfer side of the first ridge and the second ridge, A first ridgeline and a second involute curve having the same shape as the tooth profile involute curve of the drive gear existing on the end face side of the second ridgeline exist at positions shifted by two degrees in the rotation direction of the drive gear. The first intersection, the second intersection, and the third intersection are
A starter which is located between the first involute curve and the second involute curve.
12. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. In an involute gear device in which one or both of the anti-rotation direction of the ridge portion of the tooth surface and the end surface of the driving gear and the rotation direction of the ridge portion of the tooth surface and the end surface of the driven gear are chamfered, A first intersection point is defined as a point at which a first ridge line between the rotation direction dedendum chamfer and the end face of the tooth of the driven gear and a second ridge line of the rotation direction tip chamfer and the end face of the tooth intersect, The second intersection is defined as a point at which the first ridge line intersects a virtual cylinder having a radius equal to a distance obtained by subtracting a tip radius of the driving gear from a center distance between the driving gear and the driven gear, Intersection between the second ridge line and the tooth profile curve Is the third intersection. Also, when the driven gear is viewed from the axial direction, a first involute curve having the same shape as a tooth profile involute curve of the driven gear present on the chamfered side of the first ridge and the second ridge, A first ridgeline and a second involute curve having the same shape as the tooth profile involute curve of the driven gear present on the end face side of the second ridgeline are present at positions shifted by two degrees in the rotation direction of the driven gear. Wherein the first intersection, the second intersection, and the third intersection are present between the first involute curve and the second involute curve. .
13. A driving gear and a driven gear each having an involute tooth profile, wherein at least one of the driving gear and the driven gear slides in the axial direction to engage and disengage. An involute gear device in which one or both of the tooth surface of the driving gear and the rotation direction of the ridge portion of the driven gear are chamfered, and An electric motor for rotating the drive gear; a starting mechanism for the engine, comprising: a first ridgeline of the anti-rotational direction root chamfer of the teeth of the drive gear and an end face; The point at which the second ridge line intersects with the end face is defined as a first intersection, and the first ridge line and a distance obtained by subtracting the radius of the addendum circle of the driven gear from the center distance between the driving gear and the driven gear. Virtual circle with radius The point where the tube intersects is the second intersection,
The intersection between the second ridge line and the tooth profile curve is defined as a third intersection. Further, when the drive gear is viewed from the axial direction, a first involute curve having the same shape as a tooth shape involute curve of the drive gear present on the chamfer side of the first ridge and the second ridge, A first ridgeline and a second involute curve having the same shape as the tooth profile involute curve of the drive gear existing on the end face side of the second ridgeline exist at positions shifted by two degrees in the rotation direction of the drive gear. The first intersection, the second intersection, and the third intersection are
The anti-rotation direction tooth chamfered portions of the teeth of the drive gear are provided so as to be present between the first involute curve and the second involute curve, and the rotation of the teeth of the driven gear is provided. A point at which a first ridgeline of the direction tooth root chamfer and the end face intersects with a second ridgeline of the tooth rotation chamfer and the end face as the first intersection, and the first ridgeline A point at which a virtual cylinder having a radius equal to a distance obtained by subtracting the tip radius of the drive gear from the center distance between the drive gear and the driven gear is defined as a second intersection, the second ridge line and the tooth profile The intersection with the curve is the third intersection. Further, when the driven gear is viewed from the axial direction, a first involute curve having the same shape as a tooth profile involute curve of the driven gear present on the chamfered side of the first ridge line and the second ridge line, A first ridgeline and a second involute curve having the same shape as the tooth profile involute curve of the driven gear present on the end face side of the second ridgeline are present at positions shifted by two degrees in the rotation direction of the driven gear. The first intersection, the second intersection, and the third intersection are located between the first involute curve and the second involute curve, and the teeth of the driven gear The engine starting mechanism according to claim 1, wherein the rotation direction tooth flanks are provided.
JP11278162A 1998-09-30 1999-09-30 Involute gear device, starter and starting mechanism of engine Pending JP2000170882A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP27694498 1998-09-30
JP10-276944 1998-09-30
JP11278162A JP2000170882A (en) 1998-09-30 1999-09-30 Involute gear device, starter and starting mechanism of engine

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JP11278162A JP2000170882A (en) 1998-09-30 1999-09-30 Involute gear device, starter and starting mechanism of engine

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006109838A1 (en) * 2005-04-08 2006-10-19 Tsutomu Miyaoku Gear with cornu's spiral tooth profile
DE102010038443A1 (en) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Asymmetrical toothing
JP2014170172A (en) * 2013-03-05 2014-09-18 Brother Ind Ltd Image forming apparatus
US9683636B2 (en) 2015-03-30 2017-06-20 Toyota Jidosha Kabushiki Kaisha Ravigneaux planetary gear device

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006109838A1 (en) * 2005-04-08 2006-10-19 Tsutomu Miyaoku Gear with cornu's spiral tooth profile
US8100028B2 (en) 2005-04-08 2012-01-24 Tsutomu Miyaoku Cornu's spiral tooth gear
DE102010038443A1 (en) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Asymmetrical toothing
US9222567B2 (en) 2010-07-27 2015-12-29 Robert Bosch Gmbh Asymmetric toothing
JP2014170172A (en) * 2013-03-05 2014-09-18 Brother Ind Ltd Image forming apparatus
US9683636B2 (en) 2015-03-30 2017-06-20 Toyota Jidosha Kabushiki Kaisha Ravigneaux planetary gear device

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