JPH0612259Y2 - Manual transmission synchronizer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to a synchronizing device for a manual transmission, and more particularly to a synchronizing device in which two friction surfaces at the time of rotation synchronization are provided inside and outside. .

(Prior Art) Generally, gears are connected via a synchronizer at the time of shifting when shifting the manual transmission.

As the above-mentioned synchronizing device, for example, the one described in New Edition Automotive Engineering Handbook (June 1987; published by Japan Society of Automotive Engineers, Vol. 5, page 1-11) is generally known. In order to improve the synchronizing function, there is a so-called double cone type synchronizing device in which two friction surfaces are provided on the inner and outer sides as shown in FIG.

The double cone type synchronizer 1 is used for disconnecting and continuing the power transmission between the synchro hub 2 and the transmission gear 3, and is an annular inner balk ring 4 locked to the synchro hub 2 in the rotational direction. And the outer turbo ring 5, a synchro cone 7 that is locked in the rotational direction by a clutch gear 6 that rotates integrally with the transmission gear 3 is arranged.

When the coupling sleeve 8 is axially moved at the time of shift, the insert key 9 moved along with the coupling sleeve 8 presses the outer turbo ring 5, and thus the inner balk ring 4 and the outer turbo ring. 5 is pressed against the inside and the outside of the synchro cone 7, and the frictional force at this time synchronizes the rotation between the synchro hub 2 and the transmission gear 3.

(Problems to be solved by the invention) However, in such a conventional double-cone type synchronizer, the outer turbo ring 5 is pressed downward by its own weight at a normal time when the synchronizing action is not performed. The outer turbo ring 5 is brought into contact with the synchro cone 7, and the synchro cone 7 is also pressed downward to come into contact with the inner balk ring 4.

Therefore, the synchro-cone 7 is constantly rotated in a state where it is in contact with two locations inside and outside thereof, which causes a high frictional heat.

For this reason, if an attempt is made to increase the friction coefficient of the inner and outer cone surfaces of the synchro cone 7 in order to increase the synchro capacity, the friction heat of the contact portion further increases and the viscosity of the lubricating oil of the contact portion increases. There is a problem in that the fuel consumption is significantly deteriorated due to an increase in frictional resistance as well as a decrease in lubrication.

In view of the conventional problems, the present invention aims to increase the synchro capacity by reducing the area in which the synchro cone contacts the outer and inner balk rings during normal times when the synchronizing action is not performed. An object of the present invention is to provide a synchronizing device for a manual transmission that can be used.

(Means for Solving the Problems) In order to achieve the above object, the present invention provides an outer turbo ring that is axially movable while being locked in a coupling sleeve in a rotational direction. An inner balk ring which is arranged in the peripheral portion and which is locked to the coupling sleeve in the rotational direction, and a synchro cone which is arranged between the outer turbo ring and the inner balk ring and which is locked in the rotational direction with respect to the transmission gear. With the axial movement of the coupling sleeve, the outer turbo ring and the inner ring are pushed by axially pressing the outer turbo ring through an insert key engaged with the coupling sleeve. The synchro cone is pressed against the boring ring to synchronize the rotation of the manual transmission. In the device, a groove portion having a V-shaped cross section is formed along the circumferential direction on the inner circumference or the outer circumference of the synchro cone, and an annular spring, a part of which is cut off, is disposed in the groove portion, With a gap provided between the inner balk ring and the synchro cone, set the position so that the spring comes into contact with the end face on the transmission gear side, and apply the pressing force of the insert key by the spring. The feature is that a small axial locking force is generated.

(Operation) In the synchronizing device for a manual transmission according to the present invention having the above-described structure, when the synchronizing operation is performed, the outer turbo ring pressed by the insert key is pressed against the outer periphery of the synchro cone, and In this pressure contact state, the outer turbo ring further presses the synchro cone in the axial direction, and when the synchro cone is moved in the axial direction by the amount that eliminates the gap between the synchro cone and the inner vowel ring, the synchro cone and the inner vowel ring are pressed. It is pressed against the ring and rotation is synchronized.

On the other hand, when the synchronizing action is not performed, the spring engages with the groove, and the spring comes into contact with the end surface on the transmission gear side to position the synchro cone in the axial direction. A preset gap is maintained with the balk ring.

Therefore, even when the outer weight of the outer turbo ring acts on the synchro cone, the contact of the synchro cone with the inner balk ring is prevented, so that the frictional portion against the synchro cone is Since there is only one place, the frictional resistance can be greatly reduced.

(Embodiment) Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

That is, FIGS. 1, 2, and 3 show a manual transmission synchronizing device 10 according to an embodiment of the present invention, and FIG. 1 shows the synchronizing device 1.
0 is a cross-sectional view of the upper half of the center line 0, and FIG.
FIG. 3 is an enlarged view of a main part surrounded by reference numeral II in FIG. 3, and FIG. 3 is a view as seen from the direction of arrow III in FIG. 1. In FIG. , The synchro hub 12 is spline-fitted to the power transmission shaft 16 and integrally rotated, and the transmission gear 14 is connected to the power transmission shaft 16
Is rotatably mounted on the bearing via a bearing 18.

Spline 2 formed on the outer periphery of the synchronizing hub 12
0 is fitted with a coupling sleeve 22 and
A part of the spline teeth of the synchro hub 12 and the coupling sleeve 22 is cut out so that the cutout portion 2
An insert spring 24 as an insert key is inserted into the synchro hub 12 side of No. 3 so as to be movable in the axial direction (horizontal direction in the drawing).

Between the synchro hub 12 and the transmission gear 14,
A balk ring 26, a synchro cone 28 and a clutch gear 30 are arranged.

The balk ring 26 is divided into an inner balk ring 26a and an outer turbo ring 26b, and the inner and outer turbo rings 26a and 26b are locked in a rotational direction by a spline 32, and the outer turbo ring 26b is fixed to the sync hub 12. The inner and outer turbo rings 26a and 26b are locked in the notched portion 23 of the synchro hub 12 in the rotational direction.
It is rotated together with.

The synchro cone 28 is disposed between the inner and outer turbo rings 26a and 26b, and the outer circumference of the inner balk ring 26a and the inner circumference of the outer turbo ring 26b are cones formed inside and outside the synchro cone 28, respectively. It is inclined along the surfaces 28a and 28b.

Gear teeth having the same pitch as the spline teeth formed on the coupling sleeve 22 are formed on the outer periphery of the outer turbo ring 26b.

The clutch gear 30 is spline-fitted to the boss portion of the transmission gear 14 and integrally rotated, and the opening 36 formed in the clutch gear 30 has a claw portion 38 protruding from the synchro cone 28. (Three locations are provided at equal intervals in the circumferential direction in this embodiment.), And the synchro cone 28 is rotated integrally with the clutch gear 30.

Further, on the outer circumference of the clutch gear 30, gear teeth 40 having the same pitch as the spline teeth of the coupling sleeve 22 are also provided.
Are formed.

In this embodiment, as shown in FIG. 2, a circumferential groove portion 42 is formed on the inner peripheral side of the claw portion 38 of the synchro cone 28, and the groove portion 42 is also formed in the groove portion 42 as shown in FIG. An annular spring 44 as a locking member that is urged in the radial direction is engaged with the spring 44. In this engaged state, the spring 44 contacts the right end surface of the clutch gear 30 in the figure.

A part of the spring 44 is separated, and the separated end is bent in the outer diameter direction to prevent the spring 44 from being separated from the groove 42.

By the way, the position where the spring 44 is engaged with the claw portion 38, that is, the position where the groove portion 42 is formed is at the synchro cone 2 position.
8 and the inner balk ring 26a with a slight gap δ between them, the spring 44 causes the clutch gear 3 to move.
It is set to abut 0.

The spring 44 is engaged with the inclined surface 42a on the right side of the groove portion 42 in the figure to prevent the synchrocone 28 from moving to the left side in the figure. The insert spring 24 is set to be smaller than the pressing force when pressing the outer turbo ring 26b, and when the pressing force of the insert spring 24 acts, the spring 44 is reduced in diameter along the inclined surface 42a. There is.

Further, when the pressing force of the insert spring 24 is released, the spring 44 moves the inclined surface 42a.
It will be returned to the original position again along
The inclined surface 42a also functions as a returning means.

With the above configuration, the synchronization device 10 of the present embodiment is
When the synchronizer 10 is not in operation, it is in the state shown in FIG. 1, and when this synchronizer is not in operation, the synchro-cone 28 moves from the position shown in FIG. Movement to is blocked.

Therefore, the outer turbo ring 26b is pushed downward by its own weight, and the load of the outer turbo ring 26b acts on the cone surface 28b on the outer periphery of the synchro cone 28 so that the component force on the left side in the figure is exerted on the synchro cone 28. Even if it occurs, the movement of the synchro cone 28 is prevented by the spring 44 abutting on the clutch gear 30.

By the way, in the state shown in FIG.
Since a preset gap δ is provided between the inner balk ring 26 and the inner balk ring 26a, the synchro cone 28 and the inner balk ring 26a are prevented from coming into contact with each other.

Therefore, when the synchronizer 10 is not in operation, the frictional portion generated on the synchro cone 28 is only the outer peripheral cone surface 28b of the synchro cone 28 that contacts the outer turbo ring 26b, and the frictional resistance is significantly reduced.

Next, when shifting the coupling sleeve 22 to the left in the figure when shifting from the non-operating state, the insert spring 24 also moves to the left along with the coupling sleeve 22, and the insert spring 24 moves to the outer side. The balk ring 26b is pressed to the left in the figure.

Then, the inner circumference of the outer turbo ring 26b is pressed against the cone surface 28b of the synchro cone 28 and further presses the synchro cone 28, and the pressing force at this time causes the spring 44 to follow the inclined surface 42a of the groove 42. The synchro cone 28 is moved while being reduced in diameter, and the cone surface 28a of the synchro cone 28 is pressed against the outer circumference of the inner balk ring 26a.

In this way, the synchro cone 28 generates a frictional force on both the inner side and the outer side, and the large frictional force at this time synchronizes the rotation of the synchro hub 12 and the transmission gear 14 in a short time, and the synchronization is completed. Coupling sleeve 2 in stages
2 moves leaving the insert spring 24, and the spline teeth of the coupling sleeve 22 are meshed with the gear teeth 34 and the gear teeth 40.

Then, the synchronizing hub 12 and the transmission gear 14 are connected to each other, torque can be transmitted between the transmission gear 14 and the power transmission shaft 16, and the shift operation is completed.

Next, in order to release the mesh with the transmission gear 14, the coupling sleeve 22 is returned to the state shown in FIG. 1, and the insert spring 2 for the outer turbo ring 26b is released.
The pressing force of 4 is released, and the outer turbo ring 26b is released.
Moves to the right in the figure and stops pressing the synchro cone 28.

Then, the spring 44 is moved in the direction toward the bottom of the groove 42 along the inclined surface 42a of the groove 42 by the urging force in the radial direction, so that the synchro cone 28 moves to the right in the drawing, and the synchro cone 28 moves. The gap δ is provided between the inner balk ring 28a and the inner balk ring 26a.

In the present embodiment, the groove portion 42 is provided with the synchro cone 28.
However, the present invention is not limited to this, and a groove is formed on the outer peripheral side of the protrusion 38, and a spring engaged with the groove is attached in the diameter reducing direction. It may be a vibrant one.

(Effect of the Invention) As described above, in the synchronizer for a manual transmission of the present invention, the synchro cone arranged between the inner balk ring and the outer turbo ring has a shaft smaller than the pressing force of the insert key. Since the positioning is performed by the engagement of the spring and the groove that generate the locking force in the direction, and the gap is provided between the synchro cone and the inner balk ring, the synchro cone and the inner balk ring are not operated when the synchronizer is not operating. Since friction with the ring can be prevented, the generated friction heat can be greatly reduced,
It is possible to improve the durability and fuel consumption significantly, and it is possible to increase the friction coefficient between the synchro cone and the inner balk ring and outer turbo ring, achieving a significant increase in the synchro capacity. Thus, the operability at the time of shifting can be significantly improved.

Also, when the shift operation is returned, the spring has a section V
Since it returns to the engaged state along the slope of the V-shaped groove, it has various excellent effects that the gap can be always provided between the synchro cone and the inner balk ring.

[Brief description of drawings]

FIG. 1 is a sectional view showing an essential part of an embodiment of the present invention, FIG. 2 is an enlarged view of a portion II in FIG. 1, and FIG. 3 is a structural view of an essential part seen from a direction III in FIG. FIG. 4 is a cross-sectional view of essential parts showing a conventional synchronizer. 10 ... Synchronizing device, 12 ... Synchro hub, 14 ... Transmission gear, 22 ... Coupling sleeve, 24 ... Insert spring (insert key), 26a ... Inner balk ring, 26b ... Outer turbo ring, 28 ... Synchro cone, 30 ... Clutch Gears, 42 ... Grooves (returning means), 44 ... Springs (locking members).

Claims (1)

[Scope of utility model registration request] 1. An outer turbo ring which is locked to a coupling sleeve in the rotational direction and is movable in the axial direction, and an outer turbo ring which is disposed on an inner peripheral portion of the outer turbo ring and is rotationally engaged with the coupling sleeve. An inner balk ring that is stopped, and a synchro cone that is arranged between the outer balk ring and the inner balk ring and that is locked in the rotational direction with respect to the transmission gear, are provided with the axial movement of the coupling sleeve. When the outer turbo ring is axially pressed through an insert key engaged with the coupling sleeve, the synchro cone is pressed between the outer turbo ring and the inner balk ring to achieve rotation synchronization. In the synchronizing device of the manual transmission, in which the inner or outer circumference of the synchro cone is A groove having a V-shaped cross section is formed along the circumferential direction, and an annular spring, a part of which is cut off, is disposed in the groove so that a gap is provided between the inner balk ring and the synchro cone. In this state, the position of the spring is set so that the spring comes into contact with the end surface on the transmission gear side, and the spring generates an axial locking force smaller than the pressing force of the insert key. Characteristic manual transmission synchronization device.