JPH0989002A - Synchronizing device of transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To greatly improve synchronizing performance with a simple constitution. SOLUTION: A magnification mechanism for magnifying a pressing force following the movement of a sleeve 28 to speed changing gears 14 and 140 sides and transmitting this force to synchronizing rings 40 and 400 is provided between the hub 22 of a warner-type synchronizing device and the synchronizing ring 40. In addition to the magnification device in a forward speed changing gear side, a backward synchronizing mechanism for stopping the rotation of a drive shaft by inverting a pressing force and transmitting this force to the synchronizing rings 40 and 400 so as to exert synchronizing force when receiving a pressing force by the reverse shifting of the sleeve 28 is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a synchronizer used in a transmission for an automobile, and more particularly to a warner type synchronizer for improving synchronization performance.

[0002]

2. Description of the Related Art Conventionally, for example, a warner type synchronizer is known as a synchronizer used in a vehicle transmission. As is well known, the synchronizer of the warner pushes the chamfer surface provided on the outer circumference of the synchronizing ring with the chamfer surface formed on the spline of the sleeve, so that the inner peripheral conical surface of the synchronizing ring and the outer peripheral conical surface on the transmission gear side. Due to the friction between them, a synchronizing action is performed to eliminate the rotational difference between the sleeve and the transmission gear.

By this synchronizing action, the spline of the sleeve and the clutch gear on the transmission gear side can be smoothly meshed with the spline of the sleeve. That is, in the warner type synchronizer, when the movement of the shift fork starts the movement of the sleeve, the key moves together, and the key hits the groove of the synchronizing ring and pushes it. Then, the synchronizing ring is pressed against the outer peripheral conical surface of the transmission gear, the friction causes the transmission gear to start synchronizing, and the protrusion of the key disengages from the groove on the inner surface of the sleeve. However, it hits the tip of the spline of the synchronizing ring, where movement of the sleeve is blocked by the synchronizing ring.

For this reason, the sleeve strongly presses the synchronizing ring, and the synchronizing ring is pressed against the inner surface of the cone to generate a large frictional force, which promotes the synchronization between the sleeve and the transmission gear. When the synchronization is completed in this way and the relative speed difference between the sleeve and the transmission gear disappears, the friction torque disappears, the synchronization ring becomes rotatable, the sleeve passes through the synchronization ring, and the clutch gear on the transmission gear side is released. The gears mesh with each other to complete the shift.

[0005]

However, in such a conventional synchronizing device, the force for pressing the synchronizing ring against the outer peripheral conical surface of the transmission gear is the same as the pressing force acting on the sleeve from the shift fork of the operating mechanism. In the same way, there is a problem that it is difficult to increase the synchronization capability with a simple configuration, because the configuration becomes complicated by increasing the diameter of the conical surface or increasing the number of conical surfaces in order to enhance the synchronization capability. It was

Also, in a transmission having five forward gears and one reverse gear, in order to prevent the reverse gear from ringing when the shift operation to the reverse gear is performed, the sleeve for the fifth speed is set in the direction opposite to the fifth gear (the reverse gear). It is known that the reverse gear squeal can be prevented if the rotation of the drive shaft can be stopped by synchronizing with the fifth speed gear even when moving in the direction). However, in the conventional synchronizer,
There is a problem that it is difficult to move the sleeve in the opposite direction and synchronize.

The present invention has been made in view of the above-mentioned conventional problems, and an object of the present invention is to provide a synchronizing device for a transmission, which can greatly enhance the synchronizing ability with a simple structure.

[0008]

A transmission synchronizing device according to the present invention comprises an output shaft for outputting power rotation, a hub fixed to the output shaft and having a spline on the outer circumference, and a hub having a spline formed on the inner circumference. The sleeve is mounted so as to be slidable in the axial direction by fitting it into the outer peripheral spline of the sleeve, and is rotatably supported on the output shaft to form an outer peripheral conical surface on the bab side, and the inner peripheral surface of the sleeve continues to the outer peripheral conical surface. A transmission gear integrally provided with a clutch gear in which a spline meshes by axial movement, and a synchronizing ring having an inner peripheral conical surface facing the outer peripheral conical surface of the transmission gear and arranged between the sleeve and the outer peripheral conical surface. With. With regard to such a synchronizing device, the present invention provides a booster mechanism between the hub and the synchronizing ring which receives a pushing force associated with the movement of the sleeve toward the transmission gear and which boosts the pushing force and transmits the pushing force to the synchronizing ring. It is characterized by being provided in.

The booster mechanism has a pair of fulcrum protrusions acting as fulcrums at at least two symmetrical positions on the hub-side end surface of the synchronizing ring. On both sides of the pair of protrusions, a pair of levers divided into at least two in the circumferential direction are arranged in a ring shape with a certain clearance with respect to the fulcrum protrusion. The pair of levers are spread by the spring in the radial direction. A lever head is projected at the center of the outer periphery of the pair of levers. The lever head is formed with a taper edge that forms a force point that is decomposed into a radial component force toward the center and a component component in the axial direction when receiving a pressing force in the axial direction due to the movement of the sleeve.

Further, for each pair of link levers, an action point projection for forming an action point for multiplying the axial component force generated by pressing the force point of the lever head and transmitting it to a predetermined position on the end face of the synchronizing ring. Is provided. In this booster mechanism, the distance L1 from the fulcrum to the action point is different from the distance L1 from the fulcrum to the power point.
By setting so as to be short, the pressing force of the sleeve can be boosted by (L1 / L2) times to press the synchronizing ring.

Further, in the booster mechanism, when the inner peripheral conical surface of the synchronizing ring makes frictional contact with the outer peripheral conical surface of the transmission gear, the reaction force applied from the fulcrum protrusion to the end surface of each lever is provided on the pair of arms. The angle of the tapered edge is set so as to overcome the radial component force generated by the pressing of the tapered edge of the head. Therefore, even if the fulcrum position of the lever is pushed, it does not move in the radial direction, and the boosted pressing force can be reliably transmitted to the synchronizing ring. As a modification of the booster mechanism, a plurality of triangular fulcrum protrusions with the outer peripheral side as the apex are projected at a plurality of symmetrical positions on the hub-side end surface of the synchronizing ring, and triangular holes are formed in each of the fulcrum protrusions. A plurality of levers provided may be fitted and arranged in a ring shape.

The synchronizing ring may have a double synchro cone structure in which a cone is arranged between the synchronizing outer ring and the synchronizing inner ring. In this case, the boost mechanism
A plurality of fulcrum protrusions acting as fulcrums protruding at at least two symmetrical positions on the hub-side end faces of the synchronous outer ring and the synchronous inner ring are provided, and the pair of levers are pressed by the force point of the lever head. An action point protrusion is provided to form an action point that boosts the generated axial component force and transmits it to a predetermined position on the end surface of the synchronous outer ring.

Further, according to the present invention, in a transmission having five forward gears and one reverse gear, even if the sleeve is moved to the opposite side of the fifth speed gear again by shifting to the reverse gear, the synchronizing action with the five foot gears is performed. Therefore, there is provided a transmission synchronizing device capable of preventing the gear squeal during the operation to the reverse gear. Also in this case, the drive shaft to which the power rotation is input, the hub fixed to the drive shaft and having the spline on the outer circumference, and the spline formed on the inner circumference are fitted into the outer spline of the hub to be slidable in the axial direction. A clutch that is rotatably supported on the mounted sleeve and one drive shaft with respect to the hub, forms an outer peripheral conical surface on the hub side, and the inner peripheral spline of the sleeve meshes with the outer peripheral conical surface by axial movement. A synchronizing device comprising a forward transmission gear integrally provided with a gear, and a synchronizing ring having an inner peripheral conical surface facing the outer peripheral conical surface of the forward transmission gear and arranged between the sleeve and the outer peripheral conical surface. Therefore, it is intended that the sleeve of the fifth speed synchronizer moves to the opposite side of the fifth speed gear when shifting to the reverse gear.

With respect to such a synchronizer, the present invention provides a hub having a boosting mechanism for boosting the pushing force and transmitting it to the synchronizing ring when receiving the pushing force associated with the movement of the sleeve toward the forward transmission gear. And place it between the sync ring. In addition, when the sleeve receives a pressing force due to the movement to the reverse transmission gear side, it reverses the pressing force and transmits it to the synchronizing ring by the synchronous action that stops the rotation of the drive shaft by the synchronizing action. Also serves as a force mechanism.

The booster mechanism has a pair of first fulcrum protrusions that act as first fulcrums at at least two symmetrical positions on the hub-side end surface of the synchronizing ring. On both sides of each first fulcrum protrusion, a pair of levers, which are divided into at least two in the circumferential direction, are arranged in a ring shape with a certain clearance with respect to the fulcrum protrusion. The pair of levers are spread by the spring in the radial direction. A lever head is projected at the center of the outer periphery of the pair of levers.

A first force point is formed on the lever head, which is decomposed into a radial component force toward the center and an axial component force by receiving the axial pressing force associated with the movement of the sleeve toward the forward transmission gear. Forming a first taper edge. Further, for each pair of link levers, a first point of action is formed that boosts the axial component force generated by pressing the first force point of the lever head and transmits it to a predetermined position on the end surface of the synchronization ring. An action point protrusion is provided.

In this booster mechanism, the pressing force of the sleeve is set by setting the distance L2 from the first fulcrum to the first action point to be shorter than the distance L1 from the first fulcrum to the first force point. The synchronization ring can be pushed by boosting (L1 / L2) times. Further, the booster mechanism is configured such that when the inner peripheral conical surface of the synchronizing ring makes frictional contact with the outer peripheral conical surface of the transmission gear,
The reaction force applied from the fulcrum protrusion to the end surface of each lever overcomes the radial component force generated by the pressing of the first taper edge of the arm head provided on the pair of ring arms,
The angle of the first taper edge is set. For this reason, the first fulcrum position of the lever does not move even if it is pushed in the radial direction, and the pushing force boosted to the synchronizing ring can be reliably transmitted.

The reverse synchronization mechanism is formed at the edge of the lever head on the forward transmission gear side and forms a second force point that receives a pressing force due to the movement of the sleeve to the side opposite to the fifth speed gear.
Equipped with a tapered edge. A second fulcrum formed on the end face of the hub forming a second fulcrum for reversing the axial pressing force applied to the second force point of the second taper edge and transmitting it from the second action point at the end of each lever to the synchronizing ring. Equipped with protrusions. The reverse drive synchronization mechanism is set so that the distances L3 and L4 from the second fulcrum to the second force point and the second action point are substantially equal.

[0019]

1 is a sectional view of a synchronizing device of the present invention having a booster mechanism. In FIG. 1, a first speed gear 14 is attached to the output shaft 10 via bearings 120 and 12.
The 0 and 2 speed gears 14 are rotatably arranged, and the synchronizer 100 is arranged between them. The power rotation from the engine via the clutch is input to the first speed gear 140 and the second speed gear 14 via an idler gear (not shown).

A spline shaft 10-1 is provided between the second speed gear 14 and the first speed gear 140.
A hub 22 of the synchronizer is fitted and fixed by an inner peripheral spline 20. An outer peripheral spline 26 is formed on the outer peripheral portion of the hub 22. The inner peripheral spline 30 of the sleeve 28 is fitted into the outer peripheral spline 26 of the hub 22 so as to be movable in the axial direction.

The sleeve 28 has a fork groove 38 on the outer circumference. The clutch gear 16 is integrally formed on the sleeve 28 side of the second speed gear 14, and the inner peripheral spline 30 of the sleeve 28 can be engaged. Following the clutch gear 16, an outer peripheral conical surface 18 is provided. Outer conical surface 1
8 includes a synchronizing ring 40 having an inner peripheral conical surface 42.
Is arranged.

A clutch gear 160 is integrally formed on the sleeve 28 side of the first speed gear 140, and the inner peripheral spline 30 of the sleeve 28 can be engaged. Following the clutch gear 160, an outer peripheral conical surface 180 is provided. In the portion of the outer peripheral conical surface 180, the synchronization ring 400 having the inner peripheral conical surface 420 is arranged. Further, in the present invention, a boosting mechanism is provided between the synchronizing rings 40 and 400 and the hub 22.

FIG. 2 shows the synchronizing device on the 2-speed gear 14 side of FIG. 1 taken out. The following description is for the second speed gear 14
The side is taken as an example, but the same applies to the first speed gear 140 side. A pair of levers 50-1 and 50-2 forming a booster mechanism are provided between the synchronizing ring 40 and the hub 22. The assembled state of the levers 50-1 and 50-2 forming the booster mechanism to the hub 22 will be apparent from FIG. 3 which is a III-III cross section of FIG. 2. In FIG. 3, the sleeve 28 is omitted.

In FIG. 3, the rib recessed portion between the boss side of the hub 22 and the outer peripheral spline 26 has two circumferential portions.
Divided horseshoe-shaped levers 50-1 and 50-2 are incorporated. The levers 50-1 and 50-2 are integrally formed with lever heads 52-1 and 52-2 at the center of the outer circumference.
Both ends of the levers 50-1 and 50-2 are arranged at regular intervals, and block-shaped fulcrum protrusions 44- projecting from the end surface of the synchronizing ring 40 arranged on the second speed gear 14 side in this portion. 1, 44-2 are arranged. Inside the lever heads 52-1 and 52-2, a notched ring-shaped spring 60 is incorporated, and the lever 50-
1, 50-2 are pushed out in the radial direction. In the assembled state of the spring 60, the lever 50-is attached to the protrusions 44-1 and 44-2 of the synchronization ring 40.
Clearance 4 between both ends of 1, 50-2
5-1 and 45-2 are formed.

Lever head 5 of levers 50-1 and 50-2
As is clear from the cross-sectional view of FIG. 2, the reference numerals 2-1 and 52-2 have L-shaped cross-sections whose tip ends extend to the second speed gear 14 side, and the taper edge 54 is formed on the edge portion on the sleeve 28 side.
-1, 54-2 are formed. This taber edge 54
The taper surface 36 formed on the left side of the inner peripheral spline 30 of the sleeve 28 is in contact with -1, 54-2. The relationship between the inner peripheral spline 30 of the sleeve 28, the clutch gear 16 of the coupling gear, and the synchronizing ring 40 with respect to the lever head 52-1 will be apparent from FIG. 4 in which the IV-IV cross section of FIG. 2 is developed.

In FIG. 4, the inner peripheral spline 30 of the sleeve 28 is cut out at the protruding position of the lever head 52-1 of the lever 50-1, and faces the taper position 54-1 of the lever head 52-1. It forms a tapered surface. Therefore, when the sleeve 28 is moved to the clutch gear 16 side by the operation of the shift fork, the tapered edge 54-1 of the lever head 52-1 is formed by the notched tapered surface 36 (see FIG. 2) in the inner peripheral spline 30. Will be pushed. Therefore, the lever head 52-1 forms a force point to which the pressing force is applied as the sleeve 28 moves.

FIG. 5 is a partial cross-sectional view of FIG. 2 showing the appearance of the synchronizing ring 40 on the second gear 14 side and the hub 22 and sleeve 28 sides. The synchronization ring 40 has a protrusion 44-1 extending from the end surface toward the hub 22. Protrusion 44-1
As shown in FIG. 3, on the side opposite to the protrusion 44-2,
Is located. The levers 50-1 and 50-2 are arranged above and below the protrusion 44-1 and are expanded in the radial direction by a spring 60 provided inside. Lever heads 52-1 and 52-2 protruding from the levers 50-1 and 50-2 are tapered edges 54-1 and 54.
-2, and the taper edges 54-1 and 54-2 have tapered surfaces 36 formed on the inner peripheral spline 30 of the sleeve 28.
Are facing each other. Further, fulcrum protrusions 58-1, 58 are provided on the end faces of the levers 50-1, 50-2 facing the synchronizing ring 40.
-2 is formed and abuts on the end surface of the synchronization ring 40 by the fulcrum protrusions 58-1 and 58-2.

The fulcrum protrusions 58-1 and 58-2 form points of action when the synchronizing ring 40 is pressed by the levers 50-1 and 50-2. Here levers 50-1, 50
-2 when the taper positions 54-1 and 54-2 are the power points and the action point protrusions 58-1 and 58-2 are the action points. The position is in the contact state of 50-1 and 50-2.

That is, when the sleeve 28 is moved, the outer periphery of the second speed gear 14 is started at the start of synchronization due to frictional contact when the synchronizing ring 40 is pressed through the levers 50-1 and 50-2 serving as a boosting mechanism. By frictional contact by pressing the inner peripheral conical surface 42 of the synchronizing ring 40 against the conical surface 18,
For example, the lever 50-1 on the upper side with respect to the protrusion 44-1 in FIG.
Of the lever 50-2 is in contact with the lower end of the left side of the projection 44-2, and at the same time, the end of the upper right side of the lever 50-2 is in contact with the lower side of the projection 44-2.
A fulcrum is formed by abutting the respective ends of 0-2.

Referring again to FIG. 5, taking the lever 50-1 as an example, the fulcrum position formed by the contact of the end of the synchronizing ring 40 with the protrusion 44-1 is set to O, and the lever 28 is moved by the movement of the sleeve 28. Letting P be the point of action on which the pressing force is applied to the tapered edge 54-1 of the head portion 52-1 and Q be the position of the action point protrusion 58-1 formed on the end face of the lever 50-1, the distance from the fulcrum O to the force point P is shown. Is L1 and fulcrum O
The distance L2 to the point of action Q is set to a shorter distance L2.

From the relationship between the fulcrum O, the force point P, and the action point Q of the lever 50-1, the axial pushing force applied to the force point P is Fin, and the axial pushing force applied from the action point Q to the synchronizing ring 40 is set. When the pressure is Fout, the following relational expression holds. Fin × L1 = Fout × L2 (1) Therefore, the force Fout applied to the action point Q is Fout = Fin × (L1 / L2) (2). Here, because of the relationship of L1> L2,
(L1 / L2) becomes a value exceeding 1, and the synchronizing ring 40 can be pressed by the force Fout that is (L1 / L2) times the pressing force Fin due to the movement of the sleeve 28.

On the other hand, when the sleeve 28 is moved and an axial pressing force Fin is applied to the force point P of the lever head 52-1, this force is simultaneously decomposed into an axial force and a radial force toward the center. It Therefore, the lever 50-1 pushes the protrusion 44-1 of the synchronizing ring 40 by its end portion. At this time, if the synchronizing ring 40 moves due to the pushing force of the lever 50-1, the tapered edge 54-1
The axial component force at is greatly reduced, and the function of the booster mechanism is lost. Therefore, the reaction force due to the frictional contact of the synchronizing ring 40 must overcome the force pressing the projection 44-1 of the lever 50-1 due to the movement of the sleeve 28. Therefore, in the present invention, the tapered edge is formed so that the reaction force applied to the protrusion 44-1 of the synchronizing ring 40 by the frictional contact due to the synchronizing action overcomes the component force for pushing the lever 50-1 in the radial direction by the movement of the sleeve 28. 52-
The angle of 1 is set.

Next, the operation of the embodiment shown in FIGS. 2 to 5 will be described. In FIG. 2, a shift fork (not shown) is fitted in a fork groove 38 formed on the outer circumference of the sleeve 28, and the second shift operation is performed by pushing the sleeve 28 to the left by the operation of the shift fork accompanying the shift operation. Done. By moving the sleeve 28 to the left, first, the tapered edges 54-1 of the levers 50-1 and 50-2,
The tapered surface 36 of the inner peripheral spline 30 of the sleeve 28 abuts on 54-2, and pushes the synchronization ring 40 by pushing the levers 50-1 and 50-2 to the left side, and the inner peripheral conical surface 42 of the synchronization ring 40 becomes the hub. 22 and the outer peripheral conical surface 18 of the second speed gear 14 having a rotational difference from 22 and contact with the second speed gear 14 side by friction with the synchronization ring 40 is started.

At the start of synchronization on the side of the second speed gear 14 due to this frictional contact, the protrusion 44-is formed in the initial state as shown in FIG.
1, 44-2 is rotated relative to the levers 50-1, 50-2 located via clearances 45-1, 45-2, and the protrusions 44-1, 4-2 are rotated.
Contact 4-2. In this state, for example, the link relation of the fulcrum O, the force point P, and the action point Q of the lever 50-1 shown in FIG. 4 is established, and the pressing force boosted according to the above equation (2) is applied to the synchronization ring 40 and strongly pressed. .

At the same time, the reaction force (torque) due to the frictional contact of the synchronizing ring 40 is pushed by the sleeve 28 to cause the lever 50 to move.
Since the force pushing -1 inward in the radial direction is overcome and the protrusion 44-1 does not move, the pressing force by the sleeve 28 can be boosted as it is and transmitted to the synchronizing ring 40. When the rotation of the synchronizing ring 40 and the second speed gear 14 are completely matched by the pressing of the synchronizing ring 40 by this boosting action, the friction torque disappears.

Therefore, the protrusion 44- of the synchronization ring 40
There is no force to push back the levers 50-1 and 50-2 via the levers 1 and 44-2.
6 against the spring 60, levers 50-1, 50-
2 can be pushed inward and smoothly engaged with the clutch gear 16. Inner circumference spline 30 at this time
By pushing the levers 50-1 and 50-2 inward by the tapered surface 36, the synchronizing ring 40 is rotated so as to be returned by the clearances 45-1 and 45-2 in the initial state of FIG. Therefore, the synchronization ring 40 returns to the initial state again at the end of the shift.

FIG. 6 shows another embodiment of the present invention, in which a transmission mechanism having five forward gears and one reverse gear is provided with a booster mechanism for a synchronizer of the fifth speed gear, and the sleeve moves to the opposite side of the fifth speed gear. It is characterized in that a reverse synchronization mechanism is provided for synchronizing with the fifth speed gear when shifting to the reverse gear. In FIG. 6, a fifth speed gear 14-1 is rotatably mounted on the drive shaft 102 via a bearing 12. Following the fifth speed gear 14-1, the hub 22 of the synchronizer is fitted and fixed to the spline shaft 102-1 by the spline 20,
The snap ring 24 keeps it from coming off. Power from the engine is input to the drive shaft 102 via a clutch, and the fifth speed gear 14-1 meshes with a fifth speed driven gear connected to an output shaft (not shown).

Further, a reverse drive gear is connected to an output shaft (not shown), and a reverse driven gear is arranged via a reverse idler gear which can be attached to and detached from the reverse drive gear by reverse shift. By the shift, the reverse idler gear moves between the reverse drive gear and the reverse driven gear to mesh with each other, thereby transmitting the reverse rotation to the output shaft. As a transmission that reverse-shifts to the opposite side of such a 5-speed shift, for example, the F50A transmission manufactured by Nissan Motor Co., Ltd. is known.

The synchronizing mechanism of the fifth speed gear 14-1 is basically the same as that of the embodiment shown in FIG. That is, the outer peripheral spline 26 of the sleeve 22 is provided with the fork groove 38.
An inner peripheral spline 36 of 8 is fitted so as to be movable in the axial direction. A clutch gear 16 is integrally formed on the fifth speed gear 14-1 side, and an outer peripheral conical surface 18 is formed following the clutch gear 16.

To the outer peripheral conical surface 18, a synchronizing ring 40 having an inner peripheral conical surface 42 opposite thereto is arranged. A pair of horseshoe-shaped levers 50-1 and 50-2 is arranged between the synchronizing ring 40 and the hub 22, and is expanded in the radial direction by a spring 60 provided inside. The levers 50-1 and 50-2 have lever heads 54-12 and 54-22 projecting from the central outer peripheral portion. Lever head 54
Taking -12 as an example, the first taper edge 54-11 is formed on the side opposite to the fifth speed gear 14-1 and the fifth speed gear 14-1 is formed.
A second tapered edge 54-12 is formed on the side.

The inner peripheral spline 36 of the sleeve 28 has first and second tapered edges 54- of the lever head 52-1.
The tapered surface 36-11 is formed corresponding to the tapered edge 54-11, and the tapered surface 36-11 is formed corresponding to the tapered edge 54-12.
-12 is formed. The structure of the lever head portion 52-1 of the lever 50-1 is the lever 5 shown on the lower side.
The same applies to the lever head 52-2 of 0-2.

FIG. 7 shows the VII-VII surface of FIG. 6 without the sleeve 28. As is apparent from FIG. 7, in the ring-shaped recess between the shaft mounting portion side of the hub 22 and the outer peripheral spline 26, the half-moon shaped levers 50-1, 5 are formed.
0-2 is incorporated. Lever 50-1, 50-2
Protrusions 44-1 and 44-2 projecting from the end surface of the synchronizing ring are located between both ends of the lever, and the spring 60 pushes and spreads it in the radial direction to provide a constant clearance 45 with the end of the lever. -1, 45-2 are formed.

FIG. 8 is a development view of the section VIII-VIII in FIG. 6, and the relationship of the lever head 52-1 of the lever 50-1 with respect to the inner peripheral spline 30 of the sleeve 28 can be seen. That is,
Due to the notch of the outer peripheral spline 30 of the sleeve 28 corresponding to the lever head 52-1 protruding from the lever 50-1, the first tapered edge 54 on the right side of the lever head 52-1 is formed.
The first taper surface 36-11 for -11 and the second taper surface 36-12 for the left second taper edge 54-12.
Are formed correspondingly.

FIG. 9 is a partial cross-sectional view of the hub 22 and the sleeve 28 side with respect to the appearance of the synchronizing ring 40 of FIG. Taking the lever 50-1 as an example, the first surface with which the tapered surface 36-11 of the inner peripheral spline 36 of the sleeve 28 abuts
The tapered edge 54-11 forms the first power point in the boost mechanism of the fifth-speed gear synchronizer. Further, due to the frictional contact of the lever 50-1 at the start of synchronization, the contact position of the lever end portion with respect to the protrusion 44-1 forms the first fulcrum.

Further, the action point projection 58-1 provided on the end face of the lever 50-1 on the side of the synchronizing ring 40 forms the action point.
Also for the lower lever 50-2, the lever head 52-2
The right side of the first tapered edge 54-21 is the first force point by the pressing of the tapered surface 36-11 of the sleeve 28, and the protrusion 44-.
1. The contact position of the lever end portion with respect to the protrusion 44-2 (see FIG. 6) located on the opposite side of 1 is the first fulcrum, and the action point protrusion 5
The contact position of the end surface of the synchronizing ring 40 by 8-2 is the first point of action.

Here, the first fulcrum position of the lever 50-1 is set to O.
Assuming 1, the force point position is P1 and the action point position is Q1, a boosting action of Fout 1 = Fin1 × (L1 / L2) (3) can be obtained in the same manner as the equation (2). Next, with reference to FIG. 6, a reverse synchronization mechanism for shifting to the opposite side of the fifth speed gear 14-1 will be described. This reverse drive synchronization mechanism is provided integrally with the boost mechanism of the synchronizer for the fifth speed gear 14-1. First, taking the lever 50-1 as an example, 5 of the lever head 52-1 is used.
The second taper edge 54-12 provided on the high speed gear 14-1 side
And the taper surface 36-12 of the sleeve 28 facing this
Is provided for reverse synchronization for stopping the rotation of the drive shaft 10 by synchronizing the drive shaft 10 with the fifth speed gear 14-1 when shifting to the side opposite to the fifth speed gear 14-1.

Therefore, the sleeve 28 is connected to the fifth speed gear 14-
1 is moved to the opposite side, the pressing force by the taper surface 36-12 causes the second taper edge 54- of the lever head 52-1 to move.
12, the pressing force to the side opposite to the fifth speed gear 14-1 is inverted to the pressing force on the fifth speed gear 14-1 side by the lever 50-1 and is applied to the synchronizing ring 40. As a mechanism for reversing this pressing force, as shown in FIG. 7, from the end surface of the hub 26 on the shaft side, the protruding portion 64-
1, 64-2 are provided, and the lever 50-2 is provided with overhanging portions 64-3, 64-4. As is apparent from the cross section of the hub 22 in FIG. 9, the overhanging portions 64-1 to 64-4 contact substantially the centers of the levers 50-1 and 50-2, and the edge portions thereof contact the levers 50-1 and 50-2. The position 50-2 is the second fulcrum position Q2.

Further, the second taper edge 54-12 of the lever head 52-1 with respect to the second fulcrum position Q2 is set as the second force point position P2. Further, the end side surface of the lever 50-1 below the fulcrum position Q2 is the position of the second action point Q2 with respect to the synchronizing ring 40. The second point of action Q2 is realized by forming trapezoidal protrusions 46-1 and 46-2 on both sides of the protrusion 44-1 projecting from the end surface of the synchronization ring 40 and bringing them into contact with each other.

Here, when the sleeve 28 is moved to the side opposite to the fifth speed gear 14-1, the pressing force applied to the second tapered edge 54-12 of the lever 50-1 is set to Fin2 and the synchronizing ring 4.
The inverted pressing force applied to the action point Q2 of the trapezoidal overhanging portion 46-1 of 0 is Fout 2, the distance to the second force point P2 with respect to the fulcrum position O2 is L4, and the distance to the second action point Q2 is L3. Then, the following relational expression holds.

Fin2 × L4 = Fout2 × L3 (4) Therefore, the inverted pressing force FOUT2 applied to the synchronizing ring 40 is Fout2 = Fin2 × (L4 / L3) (5). By setting L3 and L4 to be almost the same,
An inverted pressing force Fout 2 equal to the pressing force Fin2 with the movement of the sleeve 28 can be applied to the synchronizing ring 40. By pressing the synchronizing ring 40 with the pressing force reversed in this way, the inner peripheral conical surface 42 of the synchronizing ring 40 is pressed against the outer peripheral conical surface 18 of the fifth speed gear 14-1 to make frictional contact, and the clutch of the clutch is engaged during reverse shift. The fifth speed gear 1 is in a stopped state even if the drive shaft 10 is inertially rotated by being separated.
The rotation of the drive shaft 10 is stopped by the frictional contact of the synchronizing ring 40 with 4-1 so that a reverse idler gear (not shown) can be engaged between the reverse drive gear and the reverse driven gear without causing a gear squeal.

Next, the operation of the embodiment shown in FIGS. 6 to 9 will be described. First, the shift operation for the forward fifth gear 14-1 in FIG. 6 is the same as that in the embodiment of FIG. That is, when the shift lever is shifted to the fifth speed, the sleeve 28 is moved to the left by the shift fork (not shown). Therefore, the first tapered edges 54-11 and 54-21 provided on the right side of the lever heads 52-1 and 52-2 of the levers 50-1 and 50-2 are the tapered portions 36 of the inner peripheral spline 36 of the sleeve 28. -11, the inner peripheral conical surface 42 of the synchronizing ring 40 is pushed in the axial direction by the fifth speed gear 14-
The friction is brought into contact with the outer peripheral conical surface 18 on the first side to perform synchronization, and upon completion of synchronization, the spline 3 of the sleeve 28
6 is engaged with the clutch gear 16 to complete the shift.

Next, 5 speed gear 1 for reverse shift
The shift operation to the side opposite to 4-1 will be described. Generally, in a transmission having five forward gears and one reverse gear, the operation pattern of the shift lever operated by the driver is as shown in FIG. The shift position 90 for the fifth speed is normally in the same row as the reverse shift position 92, and is located on the opposite side with respect to the neutral position 94.

In general, when the clutch is released and the shift operation is performed while the vehicle is stopped and the engine is rotating, the output shaft on the axle side of the transmission is stopped, but the drive shaft on the engine side is stopped. It rotates by inertia together with the clutch disc, and unless the rotation of the input side drive shaft is stopped during the shift operation, a phenomenon called gear noise occurs when shifting each transmission gear, and an unpleasant meshing sound is generated.

Normally, the forward transmission gear is provided with a synchronizing device, but the reverse transmission gear is generally not provided with a synchronizing device. For this reason, when a shift operation to the reverse gear is performed in order to move the vehicle backward, there is a high possibility that the gear will ring. In response to such a gear squeal at the time of reverse shift, if the shift operation is once performed to the fifth forward speed immediately before the clutch is disengaged and the reverse shift is performed and then the reverse shift is performed with the clutch released, the action of the fifth forward speed synchronizing device is performed. It is known that the drive shaft on the input side stops rotating and reverse shift can be performed without causing gear noise.

That is, if the synchronizing device for the forward transmission gear is actuated to stop the rotation of the drive shaft on the input side at the time of reverse shift by some method, the reverse shift can be performed without causing the gear noise. In the embodiments of FIGS. 6 to 9, in order to prevent gear squeal during reverse shift, the synchronizer provided in the fifth speed gear 14-1 can be operated in conjunction with the reverse shift.

In FIG. 6, when the shift lever is shifted from the neutral position 94 to the reverse position 92 as shown in FIG. 10, the sleeve 28 is moved to the side opposite to the fifth speed gear 14-1 by the shift fork provided in the shift mechanism. . The movement of the sleeve 28 causes the inner peripheral spline 30 to move.
The tapered surfaces 36-12, 36-22 of the shaft axially press the second tapered edges 54-12, 54-22 of the levers 50-1, 50-2 arranged on the hub 22 side. That is,
Taking the lever 50-1 side of FIG. 9 as an example, the movement of the sleeve 28 to the side opposite to the fifth speed gear 14-1 causes the second tapered edge 36-12 on the left side of the lever head 52-1 to become the second tapered edge 36-12. An axial pressing force Fin2 is applied to the action point P2. Therefore, the lever 52-1 is provided with the overhanging portion 64-1 on the end surface of the hub 22.
Is rotated clockwise with the edge portion of the second fulcrum position O2, and the action point Q2 at the lower end of the lever causes the synchronization ring 40 to rotate.
The trapezoidal overhang portion 40-1 is pressed leftward with a pressing force of Fout 2.

Similarly, for the lever 50-2 located on the lower side, the synchronizing ring 40 is pressed to the left. Therefore, in FIG. 5, the synchronizing ring 42 is replaced with the fifth speed gear 14-1.
The inner peripheral conical surface 42 is pressed against the outer peripheral conical surface 18 on the gear side, and frictional contact occurs. At this time, if the drive shaft 10 inertially rotates together with the clutch disc due to clutch disengagement, the drive shaft 10 has stopped.
Synchronous ring 4 with respect to outer peripheral conical surface 18 of high speed gear 14-1
The frictional contact of 0 stops the rotation of the drive shaft 10.

When the sleeve 28 is further pushed to the side opposite to the fifth speed gear 14-1, the levers 50-1 and 50-2 are pushed inward toward the central axis against the spring 60, and the fifth speed gear 14- The reverse idler gear (not shown) can be smoothly meshed between the reverse drive gear and the reverse driven gear by the synchronizing action on the first side. FIG.
2 is another embodiment of the boosting mechanism of the present invention used in the transmission of FIG. FIG. 11 shows a portion used in place of the levers 50-1 and 50-2 provided with the synchronizing device of FIG. 2 as a boosting mechanism together with the synchronizing ring 40.
First, on the end surface of the synchronization ring 40, triangular fulcrum protrusions 48-1, whose vertices are located in the outer circumferential direction at three points in the circumferential direction,
48-2 and 48-3 are provided.

For each of the fulcrum protrusions 48-1 to 48-3, the lever 50-11 divided into three in the circumferential direction.
50-12 and 50-13 are arranged. Lever 50-1
Each of 1 to 50-13 has a triangular hole 66 arranged with a certain clearance on the two sides of the apex side with respect to the triangular fulcrum protrusions 48-1 to 48-3 of the synchronizing ring 40.
-1, 66-2, 66-3 are formed and these holes 66-1 to 66-1
66-3 to the fulcrum protrusions 48-1 to 48- of the synchronization ring 40
It is fitted in each of the three.

Further, the levers 50-11 to 50-13 are expanded in the radial direction by a partially cut-out ring-shaped spring arranged on the inner side, and in this initial state, they are fulcrum protrusions 48-1 to 48-3. A fixed clearance is formed between the two sides of the holes 66-1 to 66-3 on the apex side as shown in the figure. Further, each of the levers 50-11 to 50-13 has a lever head 52-11, 52-1 at the center of the outer periphery.
2.52-13 is protruding.

The lever heads 52-11 to 52-13 are the same as the lever heads 52-1 and 52-2 of the levers 50-1 and 50-2 shown in FIG. Taper edge 54 that is pressed by taper surface 36
-11, 54-12, 54-13. The synchronization ring 40 and the levers 50-11 to 50 shown in FIG.
-13 to the synchronizing ring 40 and levers 50-1, 5 of FIG.
By incorporating in place of 0-2, the synchronizing ring 40 is tapered edge 52-11 when the sleeve 28 is moved to the second gear 14 side at the time of shifting, similarly to the embodiment of FIG.
It is possible to apply a pressing force to ~ 52-13 by boosting.

Further, the levers 50-11 to 50-1 in FIG.
For each of the lever heads 52-11 to 52-13 of No. 3 as in the lever heads 52-1 and 52-2 of the levers 50-1 and 50-2 of the embodiment of FIG. By providing the same, the boosting action when shifting to the fifth speed gear 14-1 and the reverse synchronization action when shifting to the reverse gear 70 can be similarly realized.

FIG. 12 shows another embodiment of the synchronizing apparatus of the present invention. In FIG. 12, levers 50-11 and 50-21 are arranged on the left side of the recessed portion of the rib between the boss for mounting on the output shaft of the hub 22 and the outer peripheral spline 26, and the lever 50-11 is disposed on the recessed portion on the right side. -12 and 50-22 are arranged. Lever 50-11, 50-12 and lever 50
21 and 50-22 are levers 50-1 and 50- of FIG.
It has a horseshoe shape that is self-divided in the same circumferential direction as 2, but does not have tapered edges 54-1 and 54-2.

Instead of the tapered edges 54-1 and 54-2, blocks 80-1 and 80-2 are provided in FIG. Taking the block 80-1 as an example, the blocks 80-1 and 80-2 have taper edges 82-11 and 82-12 corresponding to the taper edges 36-11 and 36-12 formed on the inner peripheral spline 36 of the sleeve 28. . Similarly,
The block 80-2 provided for the lower levers 50-21 and 50-22 also includes the inner peripheral spline 36 of the sleeve 28.
The tapered edges 82-21 and 82-22 corresponding to the tapered surfaces 36-21 and 36-22 formed in the above are formed.

Lever 50-11, 50-12, 50-2
The arrangement of 1, 50-22 with respect to the synchronization ring 40 is shown in FIG.
In the same manner as in the above embodiment, the springs 60 are provided on both sides of the protrusions 44-1 and 44-2 with clearances 45-1 and 45-2.
It is assembled by being pressed by the radial direction. Furthermore, levers 50-11, 50-12, 50-2
The end faces of the transmission gears 1, 50-22 on the transmission gear side, that is, the end faces of the transmission gears facing the synchronizing ring correspond to the action point projections 58-1 acting as the action points Q as in the embodiment of FIG. The protrusion is provided at a position not shown. In the synchronizer having the sixth structure shown in FIG. 12, the shift lever is moved regardless of whether the sleeve 28 is shifted to the left transmission gear or the right transmission gear. It is possible to enhance the synchronization performance by applying a force that boosts the pressing force by the force to the synchronization ring of the synchronizer.

FIG. 13 shows another embodiment of the present invention, which is characterized in that a double cone structure is used for the synchronizing device.
In FIG. 12, the synchronizing outer ring 4 is provided in a portion of the synchronizing ring provided subsequent to the clutch 16 of the second speed gear 14.
The double cone structure is realized by providing the cone 84 between the 0-1 and the synchronous inner ring 40-2. The cone 84 has claws 85 projecting from a plurality of positions on the left side in the circumferential direction, and the claws 85 are holes 8 formed in the end surface of the clutch gear 16.
It is fitted in 8-1, 88-2. Therefore, the cone 84 is movable in the axial direction and is restricted in the rotation direction with respect to the transmission gear 15.

FIG. 14 is a cross section taken along line XIV-XIV of FIG.
The sleeve 28 is omitted. Protrusions 44-11, 44-12 are provided on the two end faces of the synchronous inner ring 40-2 arranged inside the cone 84 indicated by the broken line in the radial direction.
Are formed. Similarly, the projections 44-21 and 44-22 are formed on the synchronous outer ring 40-2.

Such protrusions 44-11, 44-12,
44-21, 44-22, the lever end surface is separated by a certain clearance, and half-moon shaped levers 50-1, 50-2 are provided.
Is assembled and is assembled in a state of being expanded in the radial direction by the spring 60 arranged inside. Like the embodiment of FIG. 3, the levers 50-1 and 50-2 have lever heads 52-1 and 52-2, and the sleeve 2
8 has a taper edge 54-1 on the contact portion of the inner peripheral spline,
54-2 is formed.

The operation of the embodiment shown in FIG. 13 will be described. When the sleeve 28 moves to the second gear 14 side in accordance with the shift operation, the tapered surface 36 of the inner peripheral spline 30 causes the tapered edges of the levers 50-1 and 50-2. 54-1, 54-
2 is pressed in the axial direction. This force is the lever 50-1,50
-2 is boosted by the enlarging action, and the synchronous outer ring 4
Press 0-2 to the left.

Therefore, the inner peripheral conical surface of the synchronous outer ring 40-1 presses the outer peripheral conical surface of the cone 84 to generate a frictional force, and the inner peripheral conical surface of the cone 84 further forms the synchronous inner ring 40-2. It is pressed against the outer peripheral conical surface to generate torque due to frictional contact. As a result, the second speed gear 14 side follows and rotates in synchronization with the rotation of the hub 22 rotating on the output shaft 10, and when the two rotations coincide, the sleeve 28 moves to the lever 5.
The 0-1 and 50-2 are pushed down and fitted into the clutch gear 16 smoothly.

In the embodiment described above, the taper surface of the inner peripheral spline of the sleeve 28 and the taper edge of the lever head portion of the lever, which realize the booster mechanism of the synchronizer, are direct taper surfaces. However, each tapered surface may be a curved surface having a certain radius of curvature. Further, in the above-mentioned embodiment, the number of levers used in the booster mechanism and the reverse synchronization mechanism is two and three, but these numbers may be appropriately determined as necessary. it can.

Furthermore, in order to increase the friction torque in the synchronizer, each conical surface is cut with a screw or an oil groove is provided, and the spring is not limited to the ring-shaped spring 60, and various modifications such as the spring shape and arrangement are made. With regard to improvements and the like, it is possible to carry out appropriate modifications within a range that does not impair the functions of the booster mechanism and the reverse synchronization mechanism of the present invention.

[0073]

As described above, according to the present invention, since the pressing force of the sleeve is boosted to act on the synchronizing ring, the synchronizing ability can be greatly improved. In addition, advance 5 steps 1
It is possible to reliably prevent gear noise when shifting to the reverse gear stage in the disconnected transmission.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a synchronizer including a booster mechanism of the present invention, taking a first gear and a second gear as examples;

2 is a sectional view of the synchronizing device of the present invention, which is taken out from the second gear side of FIG. 1;

FIG. 3 is a sectional view taken along the line III-III of FIG. 2 excluding the sleeve;

FIG. 4 is a developed cross-sectional view taken along the line IV-IV of FIG. 1 as seen from the outside except the hub;

FIG. 5 is an explanatory diagram of the relationship between the synchronization ring and the lever;

FIG. 6 is a sectional view of a synchronizing device of the present invention including a booster mechanism and a reverse synchronizing mechanism;

7 is a sectional view taken along line VII-VII of FIG. 6 without the sleeve;

FIG. 8 is a developed cross-sectional view taken along the line VIII-VIII of FIG. 6 as seen from the outside except the hub;

9 is an explanatory view of the relationship between the synchronizing ring and the lever of FIG. 6;

FIG. 10 is an explanatory diagram of a shift pattern of a shift lever of a 5-speed transmission;

FIG. 11 is an explanatory view of a main part of another embodiment of the synchronizing device of the present invention having a boosting mechanism;

FIG. 12 is a cross-sectional view of another embodiment of the present invention with a booster mechanism;

FIG. 13 is a cross-sectional view of an embodiment of the present invention using a double synch cone;

14 is a cross-sectional view taken along the line XIV-XIV of FIG. 13 except for the sleeve;

[Explanation of symbols]

 10: Output shaft 12, 120: Bearing 140: 1st speed gear 14: 2nd speed gear 100: Synchronous device 16,160: Clutch gear 18: Outer peripheral conical surface 22: Hub 26: Outer peripheral spline 28: Sleeve 30: Inner peripheral spline 36 : Tapered surface 38: Fork groove 40, 400: Synchronous ring 42, 420: Inner peripheral conical surface 44-1, 44-2: Protrusion 45-1, 4-2: Clearance 50-1 to 50-2: Lever 52- 1, 52-2: Lever head 54-1, 54-2: Tapered edge 58-1, 58-2: Support point protrusion 60: Spring

Claims (11)

[Claims] 1. An output shaft for outputting power rotation, a hub fixed to the output shaft and having a spline on the outer circumference, and a spline formed on the inner circumference, fitted in an outer spline of the hub to slide in the axial direction. A movably mounted sleeve, rotatably supported on the output shaft, forming an outer peripheral conical surface on the bab side, and an inner peripheral spline of the sleeve following the outer peripheral conical surface by axial movement. A transmission gear integrally provided with a meshing clutch gear; a synchronizing ring having an inner peripheral conical surface opposed to an outer peripheral conical surface of the transmission gear and arranged between the sleeve and the outer peripheral conical surface; And a booster mechanism that is disposed between the synchronizing ring and receives a pressing force associated with the movement of the sleeve toward the transmission gear, and boosts the pressing force and transmits the boosting force to the synchronizing ring.
A synchronizing device for a transmission, characterized by being provided with. 2. A transmission synchronizer according to claim 1, wherein the booster mechanism is a pair of fulcrums that act as fulcrums protruding at least at two symmetrical positions on the hub-side end surface of the synchronizing ring. A fulcrum protrusion, a pair of levers that are divided into at least two in the circumferential direction, and are arranged in a ring shape on both sides of the pair of fulcrum protrusions with a certain clearance, and protrude into the center of the outer peripheral portion of the pair of levers; A lever head having a tapered edge that forms a force point that is decomposed into a radial component force toward the center and an axial component force by receiving an axial pressing force due to the movement of the sleeve, and a force point of the lever head And an action point projection formed for each of the pair of levers, which forms an action point for multiplying the axial component force generated by the pressing of the lever and transmitting it to a predetermined position on the end face of the synchronizing ring. Features Synchronization device of the transmission. . 3. The transmission synchronizing device according to claim 1, wherein the distance L2 from the fulcrum to the action point is set shorter than the distance L1 from the fulcrum to the power point. Features and gearbox synchronization device. 4. The transmission synchronizing device according to claim 2, wherein when the inner peripheral conical surface of the synchronizing ring comes into frictional contact with the outer peripheral conical surface of the transmission gear, the fulcrum protrusion extends from the end surface of each lever. The angle of the taper edge is set so that the reaction force applied to it overcomes the radial component force generated by the pressing of the taper edges of the lever heads provided on the pair of levers, and the transmission is synchronized. apparatus. 5. The transmission synchronizing device according to claim 2, wherein a plurality of triangular shapes are provided as fulcrum protrusions of the booster mechanism, with the outer peripheral side as an apex in the circumferential direction of the Bab side end surface of the synchronizing ring. A synchronism device for a transmission, characterized in that fulcrum protrusions are evenly arranged, and a plurality of levers each having a triangular corresponding hole arranged with a certain clearance are arranged for each of the plurality of fulcrum protrusions. 6. The transmission synchronizing device according to claim 1, wherein the synchronizing ring has a double cone structure in which a cone is arranged between a synchronizing outer ring and a synchronizing inner ring. Synchronizer. 7. The transmission synchronizing device according to claim 6, wherein the booster mechanism is projected at at least two positions which are symmetrical positions on the hub-side end faces of the synchronous outer ring and the synchronous inner ring. A plurality of fulcrum protrusions acting as fulcrums, a pair of levers divided into at least two in the circumferential direction, and arranged in a ring shape on both sides of the plurality of fulcrum protrusions with a certain clearance, and a pair of levers. A lever head having a taper edge that is projected in the center of the outer peripheral portion and that forms a force point that is decomposed into a radial component force and an axial component force toward the center under the axial pressing force associated with the movement of the sleeve. And a pair of link levers that form an action point that boosts the axial component force generated by pressing the force point of the lever head and transmits it to a predetermined position on the end surface of the synchronous outer ring. Synchronizer features and the transmission further comprising a, and the action point projection formed. . 8. A drive shaft to which power rotation is input, a hub fixed to the drive shaft and having a spline on the outer circumference, and a spline formed on the inner circumference to be slid in the axial direction by being fitted into an outer spline of the hub. A movably mounted sleeve, and a rotatably mounted bearing on one of the drive shafts for the hub, forming an outer peripheral conical surface on the bab side, and an inner peripheral spline of the sleeve following the outer peripheral conical surface. A forward transmission gear integrally provided with a clutch gear that meshes by axial movement, and an inner peripheral conical surface that faces an outer peripheral conical surface of the forward transmission gear, and is arranged between the sleeve and the outer peripheral conical surface. A synchronizing ring, and is arranged between the hub and the synchronizing ring, and doubles the pressing force when receiving the pressing force due to the movement of the sleeve toward the forward transmission gear side. And a booster mechanism that is transmitted to the synchronizing ring, and that is integrally provided with the booster mechanism. When the pusher force is applied as the sleeve moves toward the opposite side of the forward transmission gear, the push force is increased. And a reverse synchronization mechanism for stopping the rotation of the drive shaft by a synchronizing action by reversing and transmitting to the synchronizing ring. 9. The synchronizer for a transmission according to claim 8, wherein the booster mechanism is projected at at least two positions which are symmetrical positions of the end face on the Bab side of the synchronizing ring, and acts as a first fulcrum. A pair of first fulcrum protrusions, a pair of levers that are divided into at least two in the circumferential direction, and are arranged in a ring shape on both sides of the first fulcrum protrusions with a certain clearance, and the center of the outer peripheral portion of the pair of levers. The first taper edge, which is projected to each of the first and second ends, forms a first force point that is decomposed into a radial component force toward the center and an axial component force by receiving the axial pressing force associated with the movement of the sleeve. A lever head provided on the side edge, and a first point of action for boosting the axial component force generated by pressing the first force point of the lever head and transmitting the boosted force to a predetermined position on the end face of the synchronizing ring. The pair of levers to be formed A reverse action mechanism formed at an edge of the lever head on the side of the forward transmission gear, and the sleeve moves to the opposite side of the forward transmission gear. And a second taper edge forming a second force point that receives a pressing force associated with the above, and an axial pressing force applied to the second force point of the second taper edge is reversed to a second action point at the end of each lever. And a second fulcrum protrusion formed on the end surface of the hub that forms a second fulcrum to be transmitted to the synchronizing ring. . 10. The transmission synchronizing device according to claim 9, wherein the booster mechanism includes the fulcrum projection when the inner peripheral conical surface of the synchronizing ring makes frictional contact with the outer peripheral conical surface of the transmission gear. The angle of the first tapered edges is set so that the reaction force exerted on The feature is that it is set and the gear synchronizer. 11. The transmission synchronizing device according to claim 9, wherein the first fulcrum protrusion of the booster mechanism is a triangular shape having an apex on the outer peripheral side in the circumferential direction of the Bab side end face of the synchronizing ring. A plurality of first fulcrum protrusions are evenly arranged, and a plurality of levers having triangular corresponding holes arranged with a certain clearance are arranged for each of the plurality of first fulcrum protrusions. And gearbox synchronizer.