JPH0334497Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a synchronous meshing device mainly used in a gear transmission for a vehicle.

(Prior art) As an improved version of the generally known Borg-Werner type synchronizer, for example,
As shown in Japanese Patent Publication No. 24054 and Japanese Patent Publication No. 48-24096, there is a type of Borg-Warner type in which the shift key is omitted. In other words, in this type, a circular spring is installed between the internal spline teeth of the hub sleeve and the synchronizer ring, and this spring has the functions of a general Borg-Werner type shifting key and key spring. .

According to this configuration, when the hub sleeve is slid in the axial direction with a shift operation,
The synchronizer ring is also pushed axially through the circular spring mentioned above. As a result, the inner tapered cone surface of the synchronizer ring is pressed against the outer tapered cone surface on the transmission gear side, and friction torque is generated between these two tapered cone surfaces, thereby achieving the well-known rotational synchronization effect. ing.

(Problem to be solved by the invention) In the above-mentioned conventional synchromesh device, by omitting the shifting key used in the generally known Borg-Warner type, the space for incorporating the shifting key is reduced. The wall thickness of the synchronizer ring boss can be increased accordingly. The fact that the thickness of the boss portion of the synchronizer ring can be set large allows the axial dimension of the boss portion to be designed to be smaller accordingly.

However, as a matter of course, spline teeth are required on the outer periphery of the boss portion of the synchronizer ring, and a space for installing the circular spring must be secured between the spline teeth and the hub sleeve side. Therefore, the dimension of the boss portion of the synchronizer ring is larger than the basic axial length determined from the required area of the inner tapered cone surface, etc. Therefore, even though the above conventional configuration eliminates the shifting key, the actual situation is that the axial length of the synchronizer ring has not been sufficiently shortened.

In addition, with the conventional structure, there is a problem with the axial positioning of the circular spring, which causes problems such as deterioration of shift feeling or instability of the load due to axial deflection of the circular spring. left behind.

(Means for Solving the Problems) In order to solve the above problems, the synchronizer of the present invention is configured as follows.

That is, a synchronizer has a hub sleeve splined to the outer periphery of the clutch hub so that it can slide in the axial direction, and an inner tapered cone surface that is assembled to the outer periphery of the outer tapered cone surface on the transmission gear side and that can come into frictional contact with the outer tapered cone surface. The synchronizer ring is engaged with the clutch hub so that the synchronizer ring can rotate relative to the clutch hub within a predetermined range, wherein the internal spline teeth of the hub sleeve have chamfered portions on their end surfaces. and a synchronizing tooth having a chamfer on its end surface, and the end surface of the synchronizing tooth is set at a position recessed inward of the hub sleeve from the end surface of the meshing tooth, and the synchronizer The ring includes spline teeth located axially inward from the end surface of the hub sleeve and performs a synchronizing action by mutual contact of the chamfers with the synchronizing teeth in the hub sleeve, and the synchronizer ring also includes a flange formed on the axially outer side of the end surface of the hub sleeve; A spring is assembled therein, which receives a pressing action toward the center from the chamfered portion of the meshing teeth.

(Function) According to the above configuration, the spring is pressed toward the center by the chamfered portion of the meshing teeth of the hub sleeve as the clutch hub slides during the shift operation. As a result, the pressing load of the spring against the synchronizer ring increases, the inner tapered cone surface of the synchronizer ring is pressed against the outer tapered cone surface on the transmission gear side, and an initial friction torque is generated between them.

After this, the synchronizing teeth of the hub sleeve and the spline teeth of the synchronizer ring come into contact with each other, and the synchronizer ring is pushed in the axial direction. Then, the inner tapered cone surface of the synchronizer ring is pressed even more strongly against the outer tapered cone surface on the transmission gear side, increasing the frictional torque between both tapered cone surfaces. This provides the final synchronization effect associated with the shift operation.

Now, since the flange of the synchronizer ring receives only a slight axial force applied to the spring during the aforementioned shift operation, its wall thickness may be small. Further, the spline teeth of the synchronizer ring are located axially inward from the end surface of the hub sleeve. For these reasons, the axial length of the synchronizer ring falls within the range of basic dimensions determined from the required area of the inner taper cone surface.

(Effects of the invention) As described above, according to the invention, a space for assembling the spring and a space corresponding to the wall thickness of the flange for holding the spring can be secured between the end face of the hub sleeve and the transmission gear. Therefore, the axial length of this portion can be significantly shortened, and the synchronizer can be downsized. Furthermore, since the spring is held in the synchronizer ring itself, the positioning accuracy in the axial direction is high, and since the spring moves in the axial direction together with the synchronizer ring during a shift operation, the force exerted on the synchronizer ring by this spring is The load is stabilized and appropriate synchronization action is obtained.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings.

First, in FIG. 2, which is a cross-sectional view taken along the - line in FIG. Both transmission gears 2 and 3 with different numbers of teeth are mounted on roller bearings 4.
It is rotatably supported by. A clutch hub 6, which is a component of the synchronous meshing device, is assembled between the two transmission gears 2 and 3 by spline connection so as to rotate integrally with the shaft 1. As is generally well known, a hub sleeve 7 is fitted around the outer periphery of the clutch hub 6 with a spline so that it can slide in the direction along the axis (left and right in FIG. 1) when the transmission is shifted. ing.

A spline piece 15 having spline teeth 17 is fixed to the outer periphery of each of the boss portions of the above-mentioned transmission gears 2 and 3 so as to rotate together with each transmission gear 2 and 3. The synchronizer rings 10 are mounted on the outer tapered cone surfaces 16 formed on the outer peripheries of the boss portions of these spline pieces 15 so as to be able to rotate relative to each other. Note that the outer tapered cone surface 1 of the spline piece 15 is provided on the inner periphery of each boss portion 11 in each synchronizer ring 10.
6, an inner tapered cone surface 12 capable of frictional contact is formed.

Figure 3 is an enlarged view of a portion of Figure 2;
Figure 4 shows the cross section taken along the - line in the figure, and Figure 3 also shows the
As shown in FIG. 5, which shows a cross section taken along the line - in the figure, the boss portion 11 of the synchronizer ring 10 is
Spline teeth 13, which will be described in detail later, are formed on the outer periphery, and a flange 14 is integrally formed at a portion closer to the transmission gears 2 and 3 than the spline teeth 13 (see FIGS. 3 and 3). 5
(see figure). And this synchronizer ring 1
A C-shaped spring 8 having an opening at a portion of the circumference is assembled between the spline teeth 13 and the flange 14 on the outer periphery of the boss portion 11. This C-shaped spring 18 has a hook 19 formed by bending one end thereof inward, and this hook 19 is engaged with a hole 11a formed in the boss portion 11 of the synchronizer ring 10. There is.

Now, a part of the boss portion 11 of the synchronizer ring 10 is engaged with the index groove 6a of the clutch hub 6 so that it can rotate relative to it only within a predetermined range (mainly the third
(See Figure and Figure 4). As is clear from FIG. 6, the spline teeth 13 formed on the outer periphery of the boss portion 11 of the synchronizer ring 10 have chamfers 13a having a predetermined inclination angle on both side surfaces facing the hub sleeve 7. It is set to shape. Further, as is clear from FIG. 2, the spline teeth 13 are formed at three locations along the circumferential direction of the outer periphery of the boss portion 11 of the synchronizer ring 10. Furthermore, these spline teeth 13 are set to a size that eliminates the valleys of two internal spline teeth 8 of the hub sleeve 7, which will be described below, and combines them into a single tooth.

As for the internal spline teeth 8 and 9 of the hub sleeve 7, as is clear from FIG. The synchronizing internal spline teeth 9 are formed shorter than the other internal spline teeth 8. Furthermore, each of these synchronizing internal spline teeth 9 is formed with a chamfer 9a having an inclination angle corresponding to the chamfer 13a of the spline tooth 13 in the synchronizer ring 10. Regarding the chamfer 9a of these internal spline teeth 9 for synchronization,
Unlike the other chamfers of the internal spline teeth 8, it is set as a large inclined surface that slopes only on one side.

Note that the other internal spline teeth 8 in the hub sleeve 7 are each formed with a chamfered portion 8a, as is clear from FIG. When the hub sleeve 7 is slid, for example, to the right in FIG. , this spring 1
It functions to press toward the center of 8.

In the synchronous meshing device configured as above,
Assume that the hub sleeve 7 is slid, for example, in the right direction (direction toward the transmission gear 2) in FIGS. 1, 4, and 5 by a shift operation of the gear transmission. As the hub sleeve 7 slides at this time, the C-shaped springs 18 are each pushed toward the center by the chamfered portions 8a of the internal spline teeth 8. Thereby, the spring 18 against the synchronizer ring 10
As a result, the pressing load of the inner tapered cone surface 12 of the synchronizer ring 10 against the outer tapered cone surface 16 on the transmission gear 3 side also increases. As a result, an initial friction torque is generated between the tapered cone surfaces 12 and 16 due to the shift operation.

Based on the above initial friction torque, the synchronizer ring 10 is dragged by the rotation of the outer tapered cone surface 16 on the transmission gear 2 side and rotates until a part of its boss portion 11 comes into contact with the side surface of the index groove 6a of the clutch hub 6. do. In this state, the spline teeth 13 of the synchronizer ring 10
As shown by the imaginary line in FIG. 6, the chamfer 13a is positioned so as to face the chamfer 9a of the synchronizing internal spline teeth 9 of the hub sleeve 7, and is in a state of waiting for synchronization.

When the hub sleeve 7 slides further from the synchronization waiting state, the channel 9a of the synchronizing internal spline teeth 9 of the hub sleeve 7 contacts the channel 13a of the spline teeth 13 of the synchronizer ring 10, and the synchronizer ring 10 Press in the axial direction. As a result, the pressing load of the inner tapered cone surface 12 of the synchronizer ring 10 against the outer tapered cone surface 16 on the transmission gear 2 side further increases, and both tapered cone surfaces 1
The frictional torque between 2 and 16 is also increased to achieve the final synchronization effect.

Due to this final synchronization, the transmission gear 2
The rotations of the clutch hub 6 and hub sleeve 7 sides (that is, the shaft 1 side) are synchronized.
After this, the synchronizing internal spline teeth 9 of the hub sleeve 7 pass on both sides of the spline teeth 13 on the synchronizer ring 10, and the other internal spline teeth 8 pass through the spline teeth 17 on the transmission gear 2 side.
The shift is completed when the lever engages.

Now, the boss part 11 of the synchronizer ring 10
The flange 14 formed in the above-mentioned shape only needs to have enough rigidity to absorb the slight force in the axial direction that acts on the spring 18 during the above-mentioned shift operation, and the flange 14 is designed to have a thin wall thickness. It is possible to do so. and,
Since the boss portion 11 of the synchronizer ring 10 has the above-mentioned flange 14 that positions the spring 18 in the axial direction separately from the spline teeth 13 thereof, the spline teeth 13 of the synchronizer ring 10 are closer to the clutch hub 6 than the above spring 18. This means that they can be formed closer together. From this, the spline tooth 1 of the synchronizer ring 10
3 can be formed within the range of the basic axial length of the boss portion 11 determined from the required area of the inner tapered cone surface 12, etc., and thus the axial length of the synchronizer ring 10 can be significantly shortened. can do.

Further, both the chamfer 9a of the internal spline tooth 9 for synchronization in the hub sleeve 7 and the chamfer 13a of the spline tooth 13 in the synchronizer ring 10 have a large contact surface. For this purpose, for example, mutual spline teeth 9,
Dimensional tolerances etc. in 13 are absorbed, and stable synchronization action is obtained.

In addition, in the above synchronized meshing device, the normal Borg・
Since the structure eliminates the plurality of shifting keys and key springs in the Warner type, it has the following advantages.

Since the boss portion 11 of the synchronizer ring 10 does not require a groove for engaging with the shifting key, this synchronizer ring 1
The wall thickness of the boss portion 11 of 0 can be made uniform over the entire circumference, and local wear of the inner tapered cone surface 12 can be prevented.

The thickness of the boss portion 11 of the synchronizer ring 10 can be made thicker by the space for incorporating the shifting key. This allows the axial length of the synchronizer ring 10 to be designed to be smaller.

The number of parts is reduced and the ease of assembly is improved.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of a synchronous meshing device of a gear transmission, Fig. 2 is a sectional view taken along the line - - in Fig. 1, Fig. 3 is an enlarged sectional view of a part of Fig. 2, and Fig. 4 is a sectional view taken along the line - The figure is a cross-sectional view taken along the - line in Figure 3, and Figure 5 is a cross-sectional view of Figure 3.
6 is an enlarged plan view of a portion of the synchronizer ring, and FIG. 7 is a plan view showing a portion of the internal spline teeth of the hub sleeve. 2, 3...Transmission gear, 6...Clutch hub, 7
...Hub sleeve, 8... Internal spline teeth of hub sleeve, 8a... Chamfered portion of internal spline teeth,
10...Synchronizer ring, 11...Boss part of the synchronizer ring, 12...Inner taper cone surface of the synchronizer ring, 13...Spline teeth of the synchronizer ring, 14...Flange of the synchronizer ring, 16...Transmission gear side Outer tapered cone surface, 18...spring.

Claims (1)

[Claim for Utility Model Registration] A hub sleeve that is spline-slidingly fitted to the outer periphery of the clutch hub so that it can slide in the axial direction, and is assembled to the outer periphery of the outer tapered cone surface on the transmission gear side, and can make frictional contact with the outer tapered cone surface. and a synchronizer ring having an inner tapered cone surface,
In the synchronizing meshing device in which the synchronizer ring is engaged with the clutch hub so as to be relatively rotatable within a predetermined range, the internal spline teeth of the hub sleeve are meshing teeth having chamfered portions on their end surfaces; and synchronizing teeth having chamfers on their end surfaces, and the end surfaces of the synchronizing teeth are set at a position recessed inward of the hub sleeve from the end surfaces of the meshing teeth, and the synchronizer ring Spline teeth are located axially inward from the end surface of the sleeve and perform a synchronizing action by contacting mutual chamfers with the synchronizing teeth in this hub sleeve, and the synchronizer ring also has spline teeth that are located axially inward from the end surface of the hub sleeve. a flange formed on the axially outer side of the synchronizer ring, and the hub sleeve is slid in the axial direction with respect to the outer periphery between the spline teeth and the flange in the synchronizer ring. A synchronized meshing device characterized in that a spring is assembled which receives a pressing action toward the center from the chamfered portions of the teeth.