JP3138780B2 - Synchronous mechanism of gear transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a first rotating body with which a sleeve is axially movably engaged, and a torque transmitting dog tooth arranged coaxially with the first rotating body and capable of meshing the sleeve. A synchronization ring having a synchronization dog tooth capable of engaging the sleeve is disposed between the second rotation body and the second rotation body provided with the first rotation body so as to enable relative movement in a circumferential direction within a restricted range with respect to the first rotation body. A synchronous mechanism for a gear transmission in which a friction member is provided between the inner periphery of the first rotating body and the outer periphery of the synchronous ring to apply a frictional force to the first rotating body and the synchronous ring in accordance with the relative movement in the circumferential direction. About.

[0002]

2. Description of the Related Art Conventionally, such a mechanism is disclosed in, for example,
It is already known from Japanese Patent Application Laid-Open No. 2-196952.

[0003]

SUMMARY OF THE INVENTION In the above prior art,
A wave spring is used as a friction member interposed between the inner periphery of the hub as the first rotating body and the outer periphery of the synchronization ring. However, wave springs have a relatively small rigidity along the radial direction, so there is a problem with the assemblability to the synchronous ring.If the wall thickness of the wave spring is increased to increase the rigidity, it becomes difficult to deform. As the assemblability deteriorates, a predetermined frictional force cannot be obtained. Further, in the above-described conventional device, an annular concave portion for positioning and storing the wave spring is provided in the synchronous ring, and when assembling the wave spring to the synchronous ring, it is necessary to expand the diameter of the wave spring. This also deteriorates the assemblability. Moreover, since the outer surface and the inner surface of the wave spring are parallel to the inner periphery of the hub and the outer periphery of the synchronization ring, this is also the reason why the wave spring can be attached to the synchronization ring and the wave attached to the synchronization ring. This causes poor insertion and assembly of the spring into the hub inner periphery.

The present invention has been made in view of the above circumstances, and has as its object to provide a synchronous mechanism for a gear transmission in which the assemblability of a friction member is improved.

[0005]

In order to achieve the above object, according to the first aspect of the present invention, the friction member has a ring-like shape opposed to the end face of the synchronous ring along the axial direction on the first rotating body side. The connecting plate portion and the connecting plate portion
The first rotating body so as to impart circumferential frictional resistance to the rolling body.
The frictional force acting part which always elastically contacts the inner circumference of the
The friction member is integrated with the synchronization ring by being connected to the connecting plate.
And a locking claw that is locked to the outer surface of the ring so as to rotate the ring .

[0006]

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

1 to 6 show an embodiment of the present invention. FIG. 1 is a partial longitudinal sectional view of a gear transmission, FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG. 1, and FIG. FIG. 4 is a front view of the friction member, FIG. 5 is an enlarged sectional view taken along line 5-5 of FIG. 4, and FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. It is.

First, in FIG. 1, the first speed gear train G ₁ is
A drive gear 12 fixed to the main shaft 10 and a countershaft 11 meshed with the drive gear 12
A second speed gear train G ₂ is meshed with the drive gear 14 fixedly mounted on the main shaft 10 and a driven gear 13 which is rotatably supported via a bearing 16. And a driven gear 15 rotatably supported on the counter shaft 11 via a bearing 17. Also, the countershaft 11 is provided between the driven gears 13 and 15.
, A hub 19 is connected via a spline 18.

The driven gears 13 and 15 of the first and second speed gear trains G ₁ and G ₂ can be selectively engaged with the countershaft 11 and are provided with a hub 19 as a first rotating body and a first rotating body. synchronization mechanism 20 ₁ for the first speed between the driven gear 13 as a second rotating body is also a hub 19 of the first rotor second
Mechanism 20 ₂ for the second-speed synchronization is provided between the driven gear 15 as a rotary member.

[0010] The first speed synchronization mechanism 20 _1, sleeve 21
A hub 19 with which the sleeve 2 is axially movably engaged, and a sleeve 2
A synchronous ring 25 having synchronous dog teeth 25a capable of engaging the sleeve 21 is provided between the hub 19 and the driven gear 13 provided with the torque transmitting dog teeth 13a capable of engaging with the hub 19.
The friction member 26 is interposed between the inner periphery of the hub 19 and the outer periphery of the synchronous ring 25, and surrounds the synchronous ring 25, and is provided with a synchronizer spring. 27 are arranged.

[0011] The second-speed synchronization mechanism 20 ₂ includes a hub 19 which the sleeve 21 is engaged so as to be axially moved, the driven gear 15 for torque transmission Doc teeth 15a capable of meshing with the sleeve 21 is provided A synchronization ring 25 having synchronization dog teeth 25a capable of engaging the sleeve 21 is disposed between the hub 19 and the hub 19 so as to be able to move relative to the hub 19 in the circumferential direction.
A friction member 26 is interposed between the outer circumferences of the
And a synchronizer spring 27 is arranged.

By the way, the first and second speed synchronization mechanisms 2
0 _1, 20 _2, since those having basically the same configuration, hereinafter, be described in detail only for the second-speed synchronization mechanism 20 _2.

The hub 19 has a cylindrical portion 19a at its outer peripheral end which is coaxial with the countershaft 11 and extends in both axial directions. A sleeve 21 is slidably spline-connected to the cylindrical portion 19a. In addition, an annular engaging groove 28 for engaging a fork (not shown) is provided on the outer periphery of the sleeve 21 and a driven gear 29 is provided. Thus, the driven gear 29, the driving gear 30 provided on the main shaft 10, the driven gear 29 and the driving gear 3
0 meshes with a position and reverse gear gear train G _R de and movable idle gear (not shown) is formed between a position for releasing the engagement.

2 and 3, the synchronous ring 25 is basically formed in a cylindrical shape, and is extended radially outward from an end of the synchronous ring 25 on the driven gear 15 side. The synchronization dog teeth 25a are provided so as to protrude.
A tapered surface 25 is formed on the inner periphery of the synchronous ring 25 and the outer periphery of the driven gear 15 so that when the synchronous ring 25 is pressed toward the driven gear 15, they are pressed against each other to generate friction torque.
b and 15b are provided.

At the end of the cylindrical portion 19 a of the hub 19 on the side of the synchronous ring 25, regulating notches 32 are respectively provided at a plurality of, for example, three, intervals in the circumferential direction. Are provided with a plurality of locking projections 33 which are respectively disposed in the restriction notches 32. Thus, the relative movement of the synchronizing ring 25 with respect to the hub 19 in the circumferential direction is restricted by restricting the relative movement of the locking projection 33 in the circumferential direction at both ends of the restricting notch 32 in the circumferential direction. . Recesses 34, 34 are provided on the outer surface of the synchronization ring 25 on both sides of each locking projection 33, respectively.

Referring also to FIG. 4, the friction member 26
This is for applying a frictional force to the hub 19 and the synchronous ring 25 in accordance with the relative movement in the circumferential direction.
5, a connecting plate portion 35 formed in a ring shape facing the end surface on the hub 19 side along the axial direction, and the connecting plate portion elastically contacting the inner periphery of the hub 19 and the outer periphery of the synchronous ring 25. 3
5 and a plurality of frictional force acting claws 36 as frictional force acting portions, and a locking projection to be fitted into the recesses 34, 34 so as to sandwich the locking projection 33 of the synchronous ring 25 from both sides. And a plurality of sets of locking claws 37, 37... Which are connected to the connecting plate 35 in pairs at positions corresponding to 33.

A ring-shaped positioning projection 38 protruding toward the hub 19 is provided on the inner peripheral edge of the end surface of the synchronization ring 25 on the hub 19 side.
The friction member 26 is fitted to the inner periphery of the connection plate portion 35. That is, the friction member 26 is prevented from moving relative to the synchronization ring 25 in the radial direction by the positioning projection 38.

Referring also to FIG.
Are connected to the connecting plate portion 35 at positions spaced apart in the circumferential direction, and are formed in a triangular shape in which the synchronization dog teeth 25a side of the synchronization ring 25 is narrowed, and each frictional force action is performed. The tips of the claws 36 are formed in an arc shape. Moreover, when the friction member 26 is in a natural state in which no external force is applied, each of the frictional force acting claws 36 has an inclination angle α so as to incline radially outward toward the distal end side. It is connected to the unit 35. Therefore, each frictional force acting claw 3 facing the inner periphery of the cylindrical portion 19a of the hub 19
The outer surface 36a of each of the friction force acting claws 36, which faces the outer periphery of the synchronous ring 25, is formed as an inclined surface that is inclined inward in the radial direction of the hub 19 toward the hub 19. The synchronous ring 25 is formed on an inclined surface that is inclined outward in the radial direction of the synchronous ring 25 toward the synchronous ring 25 side.

Referring to FIG. 6 together, the locking claws 37.
It is formed in a substantially square shape and is provided continuously with the connecting plate portion 35. Moreover, when the friction member 26 is in a natural state in which no external force is applied, each of the locking claws 37 has an inclination angle β so as to incline radially outward toward the tip end. 35, the inclination angle β is set smaller than the inclination angle α of each of the frictional action claws 36.

With the friction member 26 interposed between the inner periphery of the cylindrical portion 19a of the hub 19 and the outer periphery of the synchronization ring 25, each of the frictional force acting claws 36. Are bent so as to be close to the outer periphery of the cylindrical portion 19a.
Resiliently comes into contact with the inner circumference of
When the synchronous ring 25 moves relative to the hub 19 in the circumferential direction, the synchronous force is generated by the frictional force generated between the frictional force acting claws 36 moving together with the synchronous ring 25 and the inner periphery of the cylindrical portion 19a. A resistance is given to the circumferential movement of the ring 25 with respect to the hub 19.

[0021] Next, to explain the action of this embodiment, in order to establish the second-speed gear train G _2, the sleeve 21
1 is moved to the right side in FIG. 1, the movement of the sleeve 21 presses the synchronization ring 25 via the synchronizer spring 27, and the tapered surface 25 b of the synchronization ring 25 is pressed against the tapered surface 15 b of the driven gear 15.

When the sleeve 21 further moves beyond the synchronizer spring 27 and the sleeve 21 comes into contact with the synchronization dog teeth 25a, the synchronization ring 25 moves relative to the sleeve 21 in the circumferential direction within a restricted range. While being further pressed to the driven gear 15 side,
A strong frictional engagement force is generated between b and 15b, and the main shaft 10 is stopped even if rotated by inertia.

Thereafter, when the sleeve 21 further moves in a state in which the phase with the synchronizing dog tooth 25a is matched, the sleeve 21 is engaged with the torque transmitting dog tooth 15a of the driven gear 15 in a stationary state. At this time, no pressing force acts on the synchronous ring 25 to press the tapered surface 25b against the tapered surface 15b, and the synchronous ring 25 is rotatable. Thus the hub 19 and the driven gear 15 are connected to each other, the second-speed gear train G ₂ is established.

With this second speed gear train G ₂ established,
The synchronizing ring 25 is rotatable, and the locking projection 33 of the synchronizing ring 25 is moved to the hub 1 according to the rotation fluctuation of the engine.
There is a possibility that a striking sound may be generated by impacting both ends in the circumferential direction of the regulating notch 32 in 9. However, the friction member 26 is interposed between the hub 19 and the synchronization ring 25, and the relative movement of the synchronization ring 25 with respect to the hub 19 in the circumferential direction causes resistance due to the frictional force between the friction member 26 and the hub 19, It is possible to prevent the synchronous ring 25 from hitting both ends in the circumferential direction of the restricting notch 32, thereby preventing occurrence of a tapping sound.

Meanwhile, the friction member 26 is
5 is provided with a connecting plate portion 35 formed in a ring shape facing the end surface on the hub 19 side, so that the rigidity along the radial direction becomes relatively large, and therefore, the friction member 26 is mounted on the outer periphery of the synchronous ring 25. Occasionally, it is possible to assemble the entire friction member 26 while keeping it in a ring shape, which facilitates the mounting operation.

The friction member 26 is provided with a plurality of friction force action claws 36 which resiliently contact the inner periphery of the hub 19 and the outer periphery of the synchronization ring 25. The inner surface 36b of the frictional force acting claws 36 ...
When the friction member 26 is in the free state, the synchronous ring 2
The synchronous ring 25 is formed on an inclined surface that is inclined outward in the radial direction of the synchronous ring 25 toward the fifth side. Therefore, the friction member 26 is attached to the synchronous ring 2 so as to cover the synchronous ring 25.
5 can be easily mounted. The second speed gear train G ₂
When the sleeve 21 is returned to the hub 19 to cancel the establishment of the frictional force acting claws 36, the synchronous ring 25 also moves in the direction of releasing the engagement friction between the tapered surfaces 25b and 15b. 36b is formed on an inclined surface which is inclined outward in the radial direction of the synchronous ring 25 toward the synchronous ring 25 side, so that the tips of the frictional force acting claws 36 do not contact the synchronous ring 25, Therefore, the synchronizing ring 25 is not pushed inward in the radial direction by the frictional force acting claws 36, so that the tapered surfaces 25b,
15b is smoothly released from the frictional engagement state.
b, 15b can also be reduced.

Further, the outer surface 36 of the frictional force acting claws 36.
a is formed on the synchronization ring 25 in a natural state in which no external force is applied to the synchronization ring 25 because it is formed on an inclined surface inclined inward in the radial direction of the hub 19 toward the hub 19. The friction member 26 is connected to the hub 19.
It is easy to assemble it by inserting it into the cylindrical portion 19a. At this time, each of the frictional action claws 36 is formed in a triangular shape and has a relatively small sliding contact area with the inner surface of the cylindrical portion 19a. It can be pushed into the cylindrical portion 19a, which also facilitates assembly.

Further, each frictional force acting claw 3 is provided in the cylindrical portion 19a.
6 are pushed in, the friction members 26
, The relative movement with respect to the synchronous ring 25 in the radial direction is prevented, so that an external force in the direction of bending the tip of each of the claws 36... The frictional force acting claw 36 does not deform into a shape different from the other frictional force acting claws 36.

When an external force that bends inward in the radial direction acts on each of the frictional action claws 36 from the cylindrical portion 19a, as shown by a chain line in FIG.
7 and 37 are deformed in a direction in which the tips thereof are engaged with the locking projections 33, thereby increasing the engagement force of the friction member 26 with the synchronization ring 25.

When the friction member 26 is removed from the hub 19, the frictional force acting on the inner surface of the cylindrical portion 19a of the hub 19 is caused by the fact that the tips of the frictional force acting claws 36 are formed in an arc shape. The tip of the working claw 36 can be prevented from being caught as much as possible, thereby facilitating the removal operation and preventing the frictional working claw 36 from being deformed.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

[0032]

[0033]

According to the present invention as described above, according to the present invention, the friction member includes a ring-shaped connecting plate portion facing an end face of the first rotor side along the axial direction of the synchronizing ring, continuously provided at its connecting plate portion Is
Thus, the first rotating body is provided with frictional resistance in the circumferential direction.
A frictional force acting portion that resiliently and constantly comes into contact with the inner periphery of the first rotating body
Is also connected to the connecting plate to
Locked on the outer surface of the ring so as to rotate integrally with the ring.
And a locking ring through the locking claw.
The frictional member that has been prevented from rotating
Engine rotational torque fluctuation due to frictional force exerted on rolling elements
Circumferential phase of the synchronous ring with respect to the first rotating body due to factors such as
Give sufficient resistance to movement (circumferential dance)
Noise generated by the ring dance
It can be effectively prevented. Moreover, the friction member
Has a ring shape facing the end face on the first rotating body side of the synchronous ring.
To provide a connecting plate portion formed, rigidity along the radial direction is relatively greatly, thus during attachment to the synchronizing ring outer periphery of the friction member, keeping the whole of the friction member in a ring shape
It is possible to assemble as it is, making mounting work easier.
You.

[Brief description of the drawings]

FIG. 1 is a partial longitudinal sectional view of a gear transmission.

FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG.

FIG. 3 is an exploded view in which a synchronization mechanism is disassembled and developed in a circumferential direction.

FIG. 4 is a front view of the friction member.

FIG. 5 is an enlarged sectional view taken along line 5-5 of FIG. 4;

FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. 4;

[Description of Reference Numerals] 13, 15 driven gear 13a of the second rotor, the hub 20 _1, 20 ₂ synchronization mechanism 21 sleeve 25 synchronizing ring 25a synchronous dog teeth 26 as 15a for torque transmission dog teeth 19 first rotor Friction member 35 Connecting plate portion 36 Friction force acting claw as friction force acting portion

Continuation of the front page (72) Inventor Atsushi Ishihara 1-4-1 Chuo, Wako-shi, Saitama Pref. Honda Technical Research Institute Co., Ltd. (JP, U) Japanese Utility Model 62-196952 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16D 23/06 F16H 3/12

Claims (1)

(57) [Claims] A first rotating body (19) with which a sleeve (21) is axially movably engaged, and which is arranged coaxially with the first rotating body (19) and meshes the sleeve (21). The synchronous ring (25) having the synchronous dog teeth (25a) capable of engaging the sleeve (21) between the second rotary body (13, 15) provided with the obtained torque transmitting dog teeth (13a, 15a). ) Are arranged so as to be able to move relative to the first rotating body (19) in the circumferential direction within a restricted range, and the inner circumference of the first rotating body (19) and the synchronization ring (2) are arranged.
A synchronous mechanism of a gear transmission in which a friction member (26) for applying a frictional force to the first rotating body (19) and the synchronous ring (25) in accordance with the relative movement in the circumferential direction is interposed between the outer circumferences of (5). In the above, the friction member (26) includes a ring-shaped connecting plate portion (35) facing an end face of the synchronization ring (25) on the first rotating body (19) side along the axial direction, and the connecting plate portion (35). Connected to
To impart frictional resistance in the circumferential direction to the first rotating body (19).
As described above, always resiliently contacts the inner circumference of the first rotating body (19).
Frictional force acting portion (36) and connecting plate portion (35)
And the friction member (26) is connected to the synchronous ring (25).
To the outer surface of the ring (25) so as to rotate integrally with the ring (25).
Locking pawls (37) to be stopped ,
Synchronous mechanism of gear transmission.