JPH0849732A - Synchronizer for transmission - Google Patents

Abstract

PURPOSE:To dissolve drag at taper cone parts effectively by centrifugal force acting upon an inertial mass body and prevent fretting wear caused by the contact of the inertial mass body. CONSTITUTION:Spline pieces 23, 24 disposed adjacently to a clutch hub 20 have inclined holes 40, 41 opened to the side face on the synchronizer ring 30 side of the spline pieces 23, 24 and separated from the rotational center toward the opening part side. Balls 42, 43 coming in contact with the side face of the synchronizer ring 30 are movably accommodated in these inclined holes 40, 41. Since the balls 42, 43 and the synchronizer ring 30 are relatively rotated, fretting wear is prevented, and since the balls 42. 43 can be enlarged in diameter, axial force based on centrifugal force is increased so as to positively prevent drag at taper cone parts 38, 39.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle transmission, and more particularly to a synchronizing device used in a manual transmission.

[0002]

2. Description of the Related Art The basic structure of a synchronizing device used in a manual transmission for a vehicle will be described with reference to FIG.
This is a single-cone type synchronizer disclosed in Japanese Patent No. 15221, in which a clutch hub 2 is spline-fitted to a rotating shaft 1, and synchronized gears 3 and 4 are rotatable on both left and right sides sandwiching the clutch hub 2. It is arranged. The parts on the clutch hub 2 side of these synchronized gears 3 and 4 are
The spline pieces 5 and 6 are spline-fitted.
Further, among these spline pieces 5 and 6, taper cone portions 7 and 8 are formed on the outer peripheral portion of the boss portion that extends toward the clutch hub 2 side, and synchronizer rings 9 and 10 are formed on these taper cone portions 7 and 8. It is fitted so as to be movable in the axial direction by a predetermined size. A hub sleeve 11 is engaged with the outer peripheral portion of the clutch hub 2 so as to be movable only in the axial direction, chamfers are formed at both end portions on the inner peripheral side of the hub sleeve 11, and the synchronizer rings 9 are provided. , 10 have chamfers formed on their outer circumferences, and splines that engage with the hub sleeve 11 are formed on the outer circumferences of the spline pieces 5, 6.

In the above synchronizing device, when the hub sleeve 11 is moved to one of the synchronized gears 3 and 4, the synchronizer rings 9 and 10 are pushed by a key (not shown), and the spline pieces 5 and 6 are pushed. Move to the side. As a result, the synchronizer rings 9 and 10 are engaged with the spline pieces 5 and 6 by the tapered cone portions 7 and 8, and start to rotate synchronously. After the chamfers of the hub sleeve 11 and the chamfers of the synchronizer rings 9 and 10 come into contact with each other, when the hub sleeve 11 is further moved, the hub sleeve 11 pushes the chamfers of the synchronizer rings 9 and 10 apart to move forward, and the spline pieces 5 and 6 are moved forward. Engages with the spline.

The synchronizer rings 9 and 10 in the synchronizer act when the hub sleeve 11 is engaged with the spline pieces 5 and 6 on the synchronized gears 3 and 4, and are in the neutral state shown in FIG. The synchronizer rings 9 and 10 are stopped together with the clutch hub 2 in a state in which a predetermined gear is set by a gear that does not exist. However, when the forcing force for moving the synchronizer rings 9 and 10 to the clutch hub 2 side is not acting, they may be engaged with the spline pieces 5 and 6 via the taper cone portions 7 and 8. In the state,
Since the synchronizer rings 9 and 10 are stopped together with the clutch hub 2, the spline pieces 5 and 6 are rotating, so that the taper cone portions 7 and 8 slip, causing sliding friction. Such friction causes drag torque, which causes power loss and temperature rise of lubricating oil.
This may cause the life of the synchronizer ring to be shortened, and the sticking of the sticker at the time of contact may cause the synchronizer ring to move and generate abnormal noise.

Therefore, in the conventional synchronizer shown in FIG. 4, the radius is gradually increased from both ends in the axial direction toward the center of the inner surface of the clutch hub 2 where the hub sleeve 11 is engaged. Taper surfaces 12 and 13 increasing
On the other hand, the synchronizer rings 9 and 10 are formed with holes 14 and 15 extending in the radial direction.
Balls 16 and 17 that are inertial mass bodies are movably accommodated in 15, and the balls 16 and 17 are configured to project to the outer peripheral side by a centrifugal force.

Therefore, in the synchronizer rings 9 and 10 on the side of the spline pieces 5 and 6 with which the hub sleeve 11 is not engaged, the balls 16 and 17 are pushed toward the outer peripheral side by the centrifugal force, so that the balls 16 and 17 are clutched. Since the hub 2 tends to move toward the center side in the axial direction along the tapered surfaces 12 and 13, the hub 2 is biased in the direction away from the spline pieces 5 and 6, and the slippage at the tapered cone portions 7 and 8 is eliminated. .

[0007]

SUMMARY OF THE INVENTION In the above-mentioned conventional synchronizing device, the centrifugal force acting on the balls 16 and 17 is applied to the tapered surface 1.
Although it is configured to convert the axial force by 2 and 13 and to cause the synchronizer rings 9 and 10 to return by the axial force, the clutch hub 2 and the synchronizer rings 9 and 10 do not rotate relative to each other. ,
Each ball 16 and 17 has an extremely small area and has a tapered surface 12,
Since it comes into contact with 13, there is a possibility that fretting wear may occur at this contact portion.

Further, since the synchronizer rings 9 and 10 holding the balls 16 and 17 are small parts which move in the axial direction, the balls 16 and 17 which can be held on the synchronizer rings 9 and 10 should be small and have a small mass. It is unavoidable that the taper angles of the tapered surfaces 12 and 13 that can be formed on the clutch hub 2 are difficult to be large in order to secure the strength of the clutch hub 2.
Therefore, in the above-described conventional synchronizer, it is difficult to generate an axial force sufficient to return the synchronizer rings 9 and 10, and there is still much room for improvement in practical use.

The present invention has been made in view of the above circumstances, and it is easy to sufficiently increase the returning movement force for canceling the drag torque between the synchronizer ring and the synchronized rotating body. An object of the present invention is to provide a synchronizer for a transmission that is free from fretting wear.

[0010]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention holds an inertial mass body projecting toward a synchronizer ring side by a centrifugal force in a synchronized rotating body with which a hub sleeve is engaged. It is characterized in that the synchronizer ring is configured to return and move by a centrifugal force acting on the inertial mass body. More specifically, according to the present invention, a hub sleeve is engaged with an outer peripheral portion of a clutch hub attached to a rotating member so as to be movable only in an axial direction, and the hub sleeve is attached to the hub sleeve by moving the hub sleeve in the axial direction. The synchronized rotating body to be engaged is arranged adjacent to the clutch hub and rotatably with respect to the rotating member, and when the synchronized rotating body or the member rotating integrally with the synchronized rotating body is approached. In a synchronizing device for a transmission, in which a synchronizer ring for transmitting torque between the synchronized rotating body or a member that rotates integrally with the synchronized rotating body is arranged, a centrifugal force held by the synchronized rotating body and a centrifugal force An inertial mass body that moves to the synchronizer ring side to press the synchronizer ring in a direction away from the synchronized rotating body by acting is provided. The one in which the features.

[0011]

In the present invention, when the synchronized rotating body rotates, a centrifugal force acts on the inertial mass held by the synchronized rotating body, and the inertial mass receiving the centrifugal force moves toward the synchronizer ring side. As a result, the inertial mass body pushes the side surface of the synchronizer ring in a direction away from the synchronized rotating body. Therefore, the synchronizer ring is disengaged from the synchronized rotating body, and the friction, that is, the drag torque, is eliminated at the portion where torque is transmitted between the two.

Since the synchronizer ring and the synchronized rotating body rotate relative to each other, fretting wear due to the inertial mass contacting the side surface of the synchronizer ring is prevented. Also, since the synchronized rotating body is a large component compared to the synchronizer ring, the inertial mass body that can be held by this can be made large, and as a result, the direction of the axis line for returning and moving the synchronizer ring can be increased. The force can be made sufficiently large and necessary.

[0013]

EXAMPLES The present invention will now be described in detail based on examples. 1 and 2, the clutch hub 20 and the high speed gear 21 and the low speed gear 22 located on the left and right of the clutch hub 20 are fitted to a rotating shaft (not shown), and the clutch hub 20 is spline fitted to the rotating shaft. The gears 21 and 22 are rotatably attached to the rotary shaft. The clutch hub 2 is attached to each gear 21, 22.
A boss portion that protrudes toward the 0 side is formed, and spline pieces 23 and 24 are spline-fitted therein. The spline pieces 23, 24 are the synchronized rotating bodies in the present invention, and these are the gears 21, 22.
It may be integrally formed with or may be press-fitted.

Keys 25 are mounted at a plurality of positions on the outer peripheral portion of the clutch hub 20 so as to move back and forth in the axial direction, and on the outer peripheral side thereof, hub sleeves 26 having chamfers formed at both ends in the axial direction. But clutch hub 20
It is mounted so as to rotate integrally with and to move back and forth in the axial direction. The key 25 is provided with a pair of key springs 27 provided on the outer peripheral side of the key 25.
It is held so as not to drop from 0.

The synchronizer shown in FIGS. 1 and 2 is of a so-called triple cone type, and is a synchronizer inner ring (hereinafter simply referred to as an inner ring).
28, 29, synchronizer middle ring (hereinafter simply referred to as middle ring) 30, 31 and synchronizer outer ring (hereinafter simply referred to as outer ring) 3
Three synchronizer rings 2, 3 are arranged between the clutch hub 20 and each spline piece 23, 24. That is, each spline piece 23, 24 is formed with a boss portion projecting to the clutch hub 20 side, and inner rings 28, 29 are respectively fitted therein so as to be movable in the axial direction.

The boss portion and the inner ring 28,
Tapered cone portions 34, 35 are formed between the inner ring 28, 29 and 29 when the inner rings 28, 29 are moved toward the spline pieces 23, 24. The middle rings 30 and 31 are annular members having tapered surfaces on both inner and outer circumferences, and are fitted to the outer circumferences of the inner rings 28 and 29 so as to be movable in the axial direction. 31 is a spline piece 23, 24
Is engaged with the spline pieces 23, 24 so as to rotate integrally therewith. And, between the outer peripheral surfaces of the inner rings 28 and 29 and the inner peripheral surfaces of the middle rings 30 and 31, the tapered cone portions 3 are engaged with each other by the movement in the axial direction.
6, 37 are formed. Outer ring 3
2, 33 are fitted on the outer peripheral sides of the middle rings 30, 31 so as to be able to move back and forth in the axial direction, and on the outer peripheral sides of the outer rings 32, 33, the hub sleeve 26
The chamfers facing each other are formed at regular intervals.

The outer rings 32 and 33 are engaged with the clutch hub 20 so as to rotate integrally with the clutch hub 20, and the outer rings 32 and 33 and the inner rings 28 and 29 are the outer rings 32 and 33. By engaging a protrusion formed on the inner rings 28 and 29 with a portion of the inner ring extending to the inner peripheral side, both are integrally rotated. And between the outer rings 32 and 33 and the middle rings 30 and 31,
Tapered cone portions 38 and 39 are formed which are engaged with each other by movement in the axial direction.

In the spline pieces 23, 24 facing the outer rings 32, 33, inclined holes 40, 41 opened toward the outer rings 32, 33 are formed.
Are formed at regular intervals in the circumferential direction, and balls 42, which are inertial mass bodies, are formed in these inclined holes 40, 41.
43 are housed movably. Here, the tilted holes 40 and 41 connect the balls 42 and 43 to the spline pieces 23 and 2 when centrifugal force acts on the balls 42 and 43.
The hole for guiding to the 4 side is formed so as to be inclined with respect to the axial direction so that the dimension from the rotation center becomes large on the opening side, that is, far from the rotation center. Since such a guiding action occurs on the inner surface of the inclined holes 40, 41 which is located on the outer side in the radial direction of the spline pieces 23, 24, if this portion is inclined as shown in the figure. The entire inclined holes 40 and 41 do not need to be particularly inclined. Furthermore, the openings of the inclined holes 40 and 41 are opposed to the side surfaces of the outer rings 32 and 33, so that the balls 42 and 43 are located in the outer rings 3 and 33.
It is configured to come into contact with the side surfaces of 2, 33.

The diameters of the balls 42 and 43 are determined by the spline pieces 23 and 24 and the outer rings 32 and 33.
The maximum distance between the outer rings 32, 33
Is preferably equal to or larger than the size of the gap between the spline pieces 23 and 24 when they are farthest from each other. In this case, the balls 42 and 43 are prevented from falling out of the inclined holes 40 and 41. Further, since the outer rings 32 and 33 move in the axial direction, the lengths of the inclined holes 40 and 41 must be such that the balls 42 and 43 are retracted so as to allow the movement. , 4
3 pushes the outer rings 32 and 33 to move the balls 42, from the position farthest from the spline pieces 23 and 24.
43 is set to a length that allows retreat.

Next, the operation of the above-mentioned synchronizer will be explained. FIG. 1 shows a neutral state or a state in which the gear stage is set by another gear, and the hub sleeve 26 is formed by the spline pieces 23, 24.
And not engaged. Therefore, the clutch hub 20 and the rotating shaft in which the clutch hub 20 is spline-fitted are stopped, while the low speed gear 21 and the high speed gear 22 are rotating. Since the gears 21 and 22 and the spline pieces 23 and 24 are integrated, the spline pieces 23 and 24 are also rotating, and as a result, they are housed in the inclined holes 40 and 41 of the spline pieces 23 and 24. Centrifugal force acts on the balls 42 and 43. Therefore, the balls 42, 43 move radially outward along the inner surface of the inclined holes 40, 41, and as a result, the inclined holes 40, 41.
The outer ring 32, 33 is in contact with the side surface of the outer ring 32, 33 facing the opening of the outer ring. That is, the outer rings 32, 33
The balls 42, 43 are pressing in the direction away from the spline pieces 23, 24, and therefore the engagement between the outer rings 32, 33 and the middle rings 30, 31 at the tapered cone portions 38, 39 is released, No slippage occurs in this part.

The centrifugal force and each load acting in the axial direction will be described with reference to FIG.
Centrifugal forces acting on the 2, 43 FB is represented by ^{FB = (4πr 3/3)} × ρ × R × ω 2. In this equation, r is the radius of the ball, ρ is the specific gravity per ball, R is the radius of revolution of each ball (the distance from the center of the rotation axis to the center of the ball), and ω is the rotational angular velocity of the spline piece. If the axial force generated based on this centrifugal force FB is greater than the force FS that pushes the outer ring toward the spline piece due to vehicle vibration, etc., the movement (or dance) of the outer rings 32, 33 to the spline piece side is prevented. Which is FS <FB sin θ · cos θ × N. In addition, θ is the inclination angle of the inclined hole, and N is the number of balls for each spline piece. Therefore, by increasing the angle of the inclined hole to some extent, the outer ring 3
It is possible to prevent the movement of the members 2 and 33 to the side of the spline pieces 23 and 24, and to prevent so-called dance of the outer rings 32 and 33, and abnormal noise and wear caused thereby. Since the axial force based on the centrifugal force of the balls 42 and 43 acts in the direction in which the movement of the hub sleeve 26 is blocked, even if the angle of the tilted holes 40 and 41 is increased, the axial force that accompanies it is increased. However, it is preferable to set it so as to be smaller than the upper limit of the shift operation force or the upper limit of the gear pull-out load at the time of one side synchronization.

FIG. 2 shows a state in which the shift to the low speed stage has been completed. In the state shown in FIG.
6 to the right in the figure, the key 25
Together with this, the key 25 pushes the outer ring 33 toward the spline piece 24 in the axial direction. Since the axial force based on the centrifugal force acting on the ball 43 is smaller than the shift operation force, the outer ring 33 moves in the axial direction while pushing the ball 43 toward the spline piece 24, and as a result, each tapered cone portion 35. , 37, 39, torque transmission occurs, and the synchronizer ring and the clutch hub 20 gradually start to rotate. In this state, the chamfer of the hub sleeve 26 and the chamfer of the outer ring 33 face each other. If the hub sleeve 26 is further pushed in the axial direction from this state, the chamfers come into contact with each other,
Synchronization is complete. When the hub sleeve 26 moves further, the chamfers of the outer ring 33 are pushed apart to move the hub sleeve 26 to the spline piece 24 side, and finally engage with the spline to complete the shift.

Therefore, in the above synchronizing device, the outer rings 32 and 33 are engaged with the tapered cone portions 38 and 39 by the centrifugal force of the balls 42 and 43 held by the spline pieces 23 and 24 which are the synchronized rotating bodies. Since it is configured to press in the direction out of alignment, it is possible to prevent power loss and increase in oil temperature due to drag torque at the tapered cone portions 38, 39. Further, since so-called dance of the outer ring rig 30 can be prevented, it is possible to prevent wear and breakage due to the outer rings 32 and 33 colliding with the key 25. In particular, in the above-described synchronizer, since the axial force due to the centrifugal force of the ball is applied to the outermost ring on the outermost side, the centrifugal force increases in proportion to the radius of gyration, so that in practice, Since the balls 42 and 43 can be held by the spline pieces 23 and 24 which can generate a sufficiently large axial force and have dimensional allowance, the balls 42 and 43 which are inertial mass bodies are relatively large. It is possible to use the same one, and also in this respect, it becomes possible to sufficiently press the synchronizer ring in the direction to disengage the tapered cone portion. And, in the triple cone type or double cone type synchronizer, the power loss due to the drag torque in the taper cone portion on the outer peripheral side is the largest, but in the above device, the drag torque in the outermost taper cone portion can be eliminated. Therefore, it has an excellent effect of reducing power loss.

Further, since the outer rings 32, 33 and the spline pieces 23, 24 rotate relative to each other when not in shift, it is possible to prevent fretting wear on the side surfaces of the outer rings 32, 33 due to contact of the balls 42, 43. it can. The outer rings 32, 33
It is conceivable that the balls 42, 43 rotate at a high speed due to the relative rotation between the ball and the spline pieces 23, 24. However, since lubricating oil is sufficiently supplied to this part, it is possible to effectively prevent wear and heat generation. it can.

The inner diameter of the inclined holes 40 and 41 is equal to that of the ball 4
Since the sizes of 2, 43 are set so that they can move freely, the balls 42, 43 may fall off the inclined holes 40, 41 during assembly. In order to prevent such inconvenience, it is preferable to apply sufficient grease to the inclined hole or the ball and prevent the ball from falling off due to its viscosity. In that case, the grease flows by the temperature rise during use and is used for lubrication of other parts. Further, in order to surely prevent the balls 42 and 43 from falling off, the open ends of the inclined holes 40 and 41 may be slightly caulked.

The present invention is not limited to the above-described embodiment, and may be applied to a double-cone type synchronizer or a single-cone type synchronizer other than the triple-cone type synchronizer shown in the above-mentioned embodiment. Can also be applied. Further, the inertial mass body is not limited to the above-mentioned ball, and one having an appropriate shape can be used, and various materials such as metal, synthetic resin, or ceramic can be adopted as the material. Further, the inclined hole may penetrate the spline piece. The tilted hole may be any one as long as it has a sloped surface that guides to the synchronizer ring side when a centrifugal force acts on the inertial mass body, and its shape is not particularly limited, and it may be a portion other than the hole. Good.

[0027]

As described above, according to the synchronizing device of the present invention, the inertial mass body is held by the synchronized rotating body that rotates relative to the synchronizer ring, and the inertial mass body is generated by the centrifugal force acting on the inertial mass body. Since it was configured to press against the side of the synchronizer ring, the synchronizer ring engages at the tapered cone when not shifting,
Accordingly, it is possible to effectively prevent generation of dragging torque, and it is possible to effectively prevent fretting wear at the contact portion due to the relative rotation of the inertial mass body and the synchronizer ring.

Further, since the inertial mass body is held by the synchronized rotating body having a dimensional allowance, the size of the inertial mass body can be increased as compared with the conventional one, and as a result, the synchronizer ring is axially moved. The force for pressing in the direction can be made sufficiently large. Furthermore, since the inclination angle that causes the axial force due to the centrifugal force of the inertial mass body is not particularly limited, the axial force can be increased in this respect as well.

In general, according to the present invention, the movement of the synchronizer ring to the synchronized rotation side and so-called dance are effectively prevented, and the power loss, wear or oil temperature rise due to the drag torque is effectively prevented. Will be possible.

[Brief description of drawings]

FIG. 1 is a partial cross-sectional view showing an embodiment of the present invention, showing a neutral state or a traveling state at another gear.

FIG. 2 is a cross-sectional view showing a state of shifting to a low speed stage.

FIG. 3 is an explanatory diagram of a working state of each load caused by a centrifugal force acting on the ball.

FIG. 4 is a sectional view showing an example of a conventional synchronizing device.

[Explanation of symbols]

 20 Clutch hub 23,24 Spline piece 26 Hub sleeve 28,29 Synchronizer inner ring 30,31 Synchronizer middle ring 32,33 Synchronizer outer ring 42,43 Ball

Claims (1)

[Claims] 1. A synchronized sleeve in which a hub sleeve is engaged with an outer peripheral portion of a clutch hub attached to a rotating member so as to be movable only in an axial direction, and the hub sleeve is engaged with the hub sleeve by the axial movement of the hub sleeve. The rotating body is disposed adjacent to the clutch hub and rotatably with respect to the rotating member, and the synchronized rotating body is moved as the rotating body approaches the synchronized rotating body or a member that rotates integrally with the synchronized rotating body. Alternatively, in a synchronizing device of a transmission, in which a synchronizer ring that transmits torque between the synchronized rotating body and a member that rotates integrally with the synchronized rotating body is arranged, the synchronizing device is held by the synchronized rotating body, and centrifugal force acts on the synchronized rotating body. And an inertial mass body that moves toward the synchronizer ring and presses the synchronizer ring in a direction away from the synchronized rotating body. Speed machine of the synchronization device.