JP2004019809A - Synchronizer for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a synchronizer for a transmission including a booster mechanism, which prevents uneven abrasion of a synchronous ring by holding the roundness of the synchronous ring during rotation. <P>SOLUTION: In this synchronizer, a lever member is provided as the booster mechanism, and a plurality of projections for pressing the lever member outward in the radial direction are integrated with the synchronous ring. A balance weight 59 is provided in a position different from that of the projection 57 of the synchronous ring 56. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a transmission synchronizer, and more particularly, to a synchronous ring structure of a transmission synchronizer.
[0002]
[Related background art]
A key type synchronizer is known as a synchronizer for a transmission. However, since the key type synchronizer has a structure in which the input from the sleeve is transmitted to the synchronizer ring as it is, the operating force of the shift lever can be reduced without increasing the diameter of the synchronizer, or a material having a small friction coefficient can be used. In recent years, as disclosed in Japanese Patent Application Laid-Open No. 9-89002, a booster mechanism capable of expanding the pressing force of the sleeve and transmitting the force to the synchronous ring with a simple configuration has been proposed. A synchronizing device has been developed.
[0003]
The synchronizing device disclosed in this publication provides, for example, at least two plural lever members between a hub and a synchronizing ring which are spline-fitted to the sleeve while supporting the sleeve, and when the shift is performed, the sleeve is moved to the lever member. To the outer part in the radial direction, and rotate the lever member with the innermost part as a fulcrum to bring the abdomen (intermediate part) of the lever member into contact with the synchronization ring. Force) to transmit to the synchronous ring.
[0004]
Further, in the synchronization device, a plurality of block-shaped protrusions corresponding to the number of lever members are formed on the hub side of the synchronization ring, and the protrusions have a certain play in a gap between the plurality of lever member ends. Are fitted. This allows the plurality of lever members to be pressed outward in the radial direction by utilizing the frictional force generated between the annular tapered portion on the inner peripheral surface of the synchronization ring and the cone portion on the gear side during synchronization. The portion functions as a stopper to restrict movement of the sleeve toward the gear during synchronization.
[0005]
[Problems to be solved by the invention]
However, as disclosed in the above publication, when a block-shaped projection is provided on the synchronization ring, the mass of the portion provided with the projection is larger than the other portions, so that only the centrifugal force of this portion during rotation is obtained. In particular, the synchronous ring deforms into an elliptical shape.
[0006]
When the synchronous ring is deformed in an elliptical manner as described above, the tapered portion of the synchronous ring and the cone portion on the gear side are in partial contact, and uneven wear is generated in the tapered portion of the synchronous ring, which is not preferable.
The present invention has been made in order to solve such a problem, and an object of the present invention is to provide a transmission synchronizing device having a booster mechanism, in which a synchronizing ring is held in a perfect circle during rotation to synchronize. An object of the present invention is to provide a transmission synchronizing device capable of preventing uneven wear of a ring.
[0007]
[Means for Solving the Problems]
In order to achieve the above object, according to the invention of a transmission synchronizer according to claim 1, a hub fixed to a rotating shaft so as to be integrally rotatable, and a spline fitted to an outer periphery of the hub to be movable in an axial direction. And a cone portion having a clutch gear and a friction surface for synchronization, the sleeve being integrally rotatable with the rotary shaft, the clutch gear being rotatably supported around the rotary shaft in proximity to the hub, and being spline-fitted to the sleeve. A transmission gear provided integrally with the hub side, and an annular taper portion which is disposed so as to be able to rotate integrally with the hub and has a friction surface for synchronization which can be pressed against the cone portion of the transmission gear. The synchronous ring is provided between the hub and the synchronous ring in an arc shape along the synchronous ring, and a part of the outer periphery comes into contact with the sleeve during the synchronous operation, thereby reducing the pressing force of the sleeve. A plurality of lever members for transmitting to a ring, and provided integrally with the synchronization ring so as to protrude toward the hub side and to have a certain play in a circumferential direction in a gap between adjacent ones of the plurality of lever members. During the synchronization, the lever member is pressed radially outward by a frictional force between the cone portion and the tapered portion until the synchronization between the hub and the transmission gear reaches a predetermined synchronization state. A plurality of projections for restricting the lever member from moving inward in the radial direction, wherein the synchronization ring has a balance weight at a position different from the projections.
[0008]
Therefore, since the synchronous ring has a large mass of the plurality of protrusions, when rotated, the centrifugal force of the portion of the protrusion is increased and tends to be elliptically deformed, but if a balance weight is provided at a position different from the protrusion. However, the same centrifugal force acts on the balance weight portion to cause the elliptical deformation, and as a result, the elliptical deformation due to the projection is canceled out, and the state close to a perfect circle is maintained even during rotation. Is done. As a result, uneven contact between the cone portion of the transmission gear and the tapered portion of the synchronous ring is eliminated, and uneven wear of the tapered portion is favorably prevented, and malfunction of the synchronous ring, and thus the synchronous device, is prevented. Thus, the life of the synchronization device is extended.
[0009]
Preferably, the mass of the projection of the synchronization ring is also reduced as much as possible, whereby the mass of the balance weight is reduced as well as the mass of the projection, and the synchronization ring is favorably maintained in a state close to a perfect circle.
Further, in the invention related to the transmission synchronizing device according to claim 2, the plurality of lever members include two lever members having the same shape, and the plurality of protrusions are provided diagonally on the synchronization ring. The synchronous ring has two balance weights diagonally at a position substantially 90 degrees from the protrusion.
[0010]
Therefore, when two lever members having the same shape are provided, and two projections are provided diagonally on the synchronous ring in accordance with the two lever members, the balance weight is diagonally moved to a position substantially 90 degrees with the projection. , The elliptical deformation due to the projections is favorably canceled, and the synchronization ring is favorably maintained in a state close to a perfect circle.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of a transmission synchronizer according to the present invention will be described with reference to the accompanying drawings.
Referring to FIG. 1, there is shown a longitudinal sectional view of a transmission synchronizing device according to the present invention. FIG. 2 shows a cross section of the synchronizer cut at 90 ° when viewed in the axial direction. That is, the upper side of the center line in FIG. 1 shows a vertical section of the synchronizer, and the lower side shows a horizontal section.
[0012]
As shown in FIG. 1, a second speed gear 10, for example, is rotatably connected to the output shaft 1 via a bearing 2, and a third speed gear 20, for example, via a bearing 3. A synchronizer main body 30 is disposed between the third gear 20 and the third speed gear 20.
An outer peripheral spline 4 is formed on the outer peripheral surface of the output shaft 1 between the second gear 10 and the third gear 20, and the hub 32 of the synchronizer body 30 is fitted to the outer spline 4. Specifically, an inner peripheral spline 34 is formed on the inner peripheral surface of the hub 32, and the inner peripheral spline 34 is press-fitted into the outer peripheral spline 4.
[0013]
Referring to FIG. 2, there is shown a view of the synchronizer main body 30 as viewed from the second speed gear 10 side, and will be described with reference to FIG.
A sleeve 40 is fitted on the outer periphery of the hub 32 so as to be slidable in the axial direction. Specifically, an outer peripheral spline 36 is formed on the outer peripheral surface of the hub 32, while an inner peripheral spline 42 is formed on the inner peripheral surface of the sleeve 40, and the inner peripheral spline 42 extends in the axial direction along the outer peripheral spline 36. It is slidably fitted.
[0014]
The clutch gear 12 is provided integrally with the second speed gear 10 on the side of the sleeve 40 of the second speed gear 10, and the inner peripheral spline 42 of the sleeve 40 can mesh with the clutch gear 12. The clutch gear 22 is also provided integrally with the third speed gear 20 on the side of the sleeve 40 of the third speed gear 20, and the inner peripheral spline 42 of the sleeve 40 can be engaged with the clutch gear 22. That is, the synchronizer is configured such that the inner peripheral spline 42 slides in the axial direction on the outer peripheral surface of the hub 32, and the inner peripheral spline 42 selectively meshes with the clutch gear 12 or the clutch gear 22. The 10 and the hub 32 or the third speed gear 20 and the hub 32 are integrally rotatable via a sleeve 40. As a result, a driving force from an engine (not shown) is selectively transmitted to the output shaft 1 via the second speed gear 10 or the third speed gear 20.
[0015]
Further, on the hub 32 side of the second speed gear 10, a cone portion 14 having a friction surface for synchronization is formed integrally with the clutch gear 12, and similarly, on the hub 32 side of the third speed gear 20, A cone 24 having a friction surface for synchronization is formed integrally with the clutch gear 22.
A synchronous ring unit 50 is fitted around the cone portion 14 of the second speed gear 10 and the cone portion 24 of the third speed gear 20 with play in the axial direction. Specifically, the synchronizer has a triple-cone structure in which a center cone 52 having the same inclination angle is arranged together with the cone portions 14 and 24. The synchronization ring unit 50 is connected to the inner ring 54 so as to sandwich the center cone 52. It is composed of an outer ring 56. More specifically, the clutch gear 12 and the clutch gear 22 have a plurality of holes 13 and 23, respectively, while the center cone 52 has a plurality of claws 53 formed therein. 13 and the hole 23 are fitted together with play in the axial direction, thereby rotating integrally with the cone portion 14 of the second speed gear 10 and the cone portion 24 of the third speed gear 20. The inner ring 54 and the outer ring 56 rotate integrally with the hub 32 as described later.
[0016]
The inner ring 54, the outer ring 56, and the center cone 52 are in sliding contact with the annular tapered portion 54 a formed on the inner peripheral surface of the inner ring 54 such that the cone portions 14, 24 of the second speed gear 10 and the third speed gear 20 are formed. The cone portion 54b formed on the outer peripheral surface of the inner ring 54 comes into sliding contact with the annular taper portion 52a formed on the inner peripheral surface of the center cone 52, and the cone portion 52b formed on the outer peripheral surface of the center cone 52 The outer rings 56 are sequentially arranged in the radial direction so as to be in sliding contact with an annular tapered portion 56 a formed on the inner peripheral surface of the outer ring 56.
[0017]
Further, between the hub 32 and the synchronous ring unit 50, a pair of lever members 60 and 61 which function as a boosting mechanism with the output shaft 1 interposed therebetween are provided.
Referring to FIG. 3, there is shown a diagram in which the synchronous ring unit 50 and the center cone 52 are removed from FIG. 2, and the description will be made with reference to FIG.
As shown in FIG. 3, the lever members 60 and 61 each have a substantially horseshoe shape (arc shape) and are disposed along the synchronous ring unit 50. Lever heads (part of the outer periphery) 62 and 63 are integrally formed to protrude outward so as to fit. Further, the lever member 60 and the lever member 61 are disposed so that a fixed clearance is formed between the pair of both ends 64, 64 and the pair of both ends 65, 65. The cut-out ring-shaped spring 70 is held by pressing the lever members 60 and 61 radially outward. A thin plate 72 is inserted between the lever members 60 and 61 and the synchronous ring unit 50.
[0018]
As shown by the lever head 62 in FIG. 1, tapered surfaces 62a and 63a facing the hub 32 are formed at the distal ends of the lever heads 62 and 63 of the lever members 60 and 61. Of the inner peripheral spline 42 of 40, a portion corresponding to the notch 35 has a tapered surface 42a formed so as to face the tapered surfaces 62a and 63a.
[0019]
That is, when the sleeve 40 slides in the axial direction, the taper surface 42a of the inner peripheral spline 42 comes into contact with the taper surfaces 62a, 63a of the lever heads 62, 63, and the lever head is moved by a horizontal component force. The parts 62, 63 are displaced in the axial direction, and at the same time, the lever heads 62, 63, that is, the lever members 60, 61, are depressed radially inward against the spring force of the spring 70 by the vertical component force. ing.
[0020]
The outer ring 56 is fitted with a fixed clearance between the pair of both ends 64, 64 of the lever members 60, 61 and the pair of both ends 65, 65 with a certain play in the circumferential direction. A pair of block-shaped projections 57, 57 are integrally formed at diagonal positions.
The projection 57 of the outer ring 56 is provided with a claw 58 extending inward in the radial direction, while the inner ring 54 is provided with a member 55 extending toward the hub 32 so as to correspond to the claw 58 so as to engage with the engagement groove. 55a are formed, and the pawl 58 and the engagement groove 55a are fitted.
[0021]
That is, the inner ring 54 is connected to the outer ring 56 via the engaging groove 55 a and the claw 58, and the outer ring 56 is a block-shaped projection 57 and a fixed portion between the pair of both ends 64, 64 and the pair of both ends 65, 65. The lever members 60 and 61 are connected to the hub 32 via the lever heads 62 and 63 and the notch 35 via a clearance. Accordingly, the inner ring 54, the outer ring 56, and the lever members 60 and 61 rotate integrally with the hub 32.
[0022]
Hereinafter, the operation of the thus configured synchronizer will be briefly described. Here, a case where the sleeve 40 is operated toward the second speed gear 10 will be described, but the same applies to a case where the sleeve 40 is operated toward the third speed gear 20.
When the sleeve 40 is operated, for example, toward the second speed gear 10, the tapered surface 42a of the inner peripheral spline 42 first comes into contact with the tapered surfaces 62a, 63a of the lever heads 62, 63, as described above. As a result, the lever heads 62 and 63 are displaced in the axial direction by the horizontal component force. At this time, the lever members 60 and 61 use the pair of both ends 64 and 64 and the pair of both ends 65 and 65 as fulcrums. , And the abdominal portions 60a and 61a of the lever members 60 and 61 press the outer ring 56 via the thin plate 72. That is, assuming that the lever heads 62 and 63 are the power points and the pair of both ends 64 and 64 and the pair of both ends 65 and 65 are the fulcrum, the abdominal parts 60a and 61a of the lever members 60 and 61 become the action points and the force for moving the sleeve 40 Is enlarged (power boosted) by the action of the lever, and the outer ring 56 is pressed toward the second speed gear 10 by the lever members 60 and 61 with a relatively large force.
[0023]
As a result, friction is easily and reliably generated between the outer ring 56 and the center cone 52, between the center cone 52 and the inner ring 54, and between the inner ring 54 and the cone portion 14 of the second speed gear 10. Synchronization with the speed gear 10 is quickly achieved.
Further, when the tapered surface 42a of the inner peripheral spline 42 comes into contact with the tapered surfaces 62a, 63a of the lever heads 62, 63, as described above, the lever heads 62, 63, that is, the lever member 60 are caused by the vertical component force. , 61 are depressed radially inward against the spring force of the spring 70, while the frictional force is generated between the synchronous ring unit 50, the center cone 52, and the cone portion 14 of the second speed gear 10. That is, during synchronization, the pair of block-shaped projections 57, 57 of the outer ring 56 also try to move in the rotational direction by the frictional force, and one of the pair of both ends 64, 64 of the lever members 60, 61 and the pair of both ends 65, Since one of the pressure members 65 is pressed, the movement of the lever members 60 and 61 inward in the radial direction is temporarily restricted by the pressing force.
[0024]
As a result, until the hub 32 and the second gear 10 are brought into a predetermined synchronization state, the movement of the sleeve 40 toward the second gear 10 is prevented by the lever heads 62 and 63, and the hub 32 and the second gear are stopped. The sleeve 40 is reliably prevented from accidentally coming into contact with the clutch gear 12 while the gear 10 is not yet synchronized.
When the hub 32 and the second speed gear 10 are synchronized, the frictional force is reduced, so that the lever members 60 and 61 move radially inward by the predetermined play against the spring force of the spring 70, and the sleeve 40 is moved. The sleeve 40 can move toward the second speed gear 10, and the sleeve 40 meshes with the clutch gear 12. This completes the shift.
[0025]
By the way, referring to FIG. 4, there is shown a view of the outer ring 56 as viewed from the hub 32 side. Hereinafter, based on the same figure and FIGS. 1 and 2, the characteristic structure of the outer ring 56 according to the present invention will be described. The operation will be described.
As described above, the outer ring 56 is integrally formed with a pair of block-shaped protrusions 57 and 57 at diagonal positions. However, the outer ring 56 according to the present invention further includes a A pair of (two) balance weights 59 having the same mass are integrally formed diagonally at a position forming 90 ° so that the center of rotation, that is, the axis and the center of gravity of the outer ring 56 coincide with each other. . In this case, it is desirable that the balance weight 59 has substantially the same width dimension as the block-shaped protrusion 57 in the circumferential direction, and has substantially the same mass as the protrusion 57.
[0026]
The block-shaped projection 57 is provided with a notch 57a, so that the mass of the block-shaped projection 57 is reduced as much as possible.
As described above, when the outer ring 56 is provided with the pair of balance weights 59, 59 together with the pair of block-shaped protrusions 57, 57, generally, the rotation of the outer ring 56 generates a centrifugal force, and the centrifugal force becomes F = It is mrω ² (m: mass, r: radius of rotation, ω: angular velocity), and the larger the mass, the larger the centrifugal force acts and the outer ring 56 is deformed elliptically. The elliptical deformation caused by the applied centrifugal force is offset by the centrifugal force acting on the pair of balance weights 59 having substantially the same mass, and the outer ring 56 is maintained in a state close to a perfect circle even during rotation. Is done.
[0027]
Accordingly, if the outer ring 56 is elliptically deformed during rotation, the tapered portion 56a of the outer ring 56 and the cone portion 52b of the center cone 52 are in uneven contact with each other, and the tapered portion 56a may be unevenly worn. By disposing such an uneven contact, such uneven wear of the tapered portion 56a is favorably prevented, malfunction of the outer ring 56, the center cone 52, and furthermore, the synchronizer is prevented, and the life of the synchronizer is extended. It is planned.
[0028]
The notch 57a is provided on the block-shaped projection 57 to reduce the mass as much as possible, so that the balance weight 59 can be made relatively light together with the projection 57 to prevent deviation of the mass balance. It is possible to favorably maintain a state close to a perfect circle.
The description of the embodiment of the transmission synchronizing device according to the present invention is finished above, but the embodiment is not limited to the above embodiment.
[0029]
For example, in the above-described embodiment, the pair of balance weights 59, 59 is provided on the outer ring 56 so as to form substantially 90 ° with the pair of protrusions 57, 57, but the outer ring 56 is maintained in a state close to a perfect circle. If possible, balance weights may be provided at a plurality of locations on the outer ring 56.
Further, in the above embodiment, the notch 57a is provided in the block-shaped protrusion 57 of the outer ring 56 to reduce the mass. However, if the extra thickness of the protrusion 57 is cut in addition to the notch 57a, the balance weight 59 Can be further reduced, and the outer ring 56 can be more favorably maintained in a state close to a perfect circle.
[0030]
In the above embodiment, the case where the balance weight 59 is provided on the outer ring 56 has been described. However, the present invention may be applied to the inner ring 54 and the center cone 52. For example, although the elliptical deformation is caused by the centrifugal force of the member 55 in which the engagement groove 55a is formed, a balance weight may be provided on the inner ring 54 so as to cancel the elliptical deformation.
[0031]
In the above embodiment, the synchronizing device having the triple-cone structure has been described. However, the present invention is naturally applicable to a synchronizing device having a single-cone structure or a double-cone structure.
Further, in the above embodiment, the synchronizing device in which the lever member is composed of the two lever members 60 and 61 has been described. However, the synchronizing device in which three or more lever members are provided and the outer ring has three or more block-shaped protrusions. Even so, the present invention can be applied favorably.
[0032]
【The invention's effect】
As described in detail above, according to the transmission synchronizing device of the first aspect of the present invention, the synchronizing ring includes a lever member as a boosting mechanism, and a plurality of protrusions that press the lever member outward in the radial direction. In the synchronizing device integrated with the above, the balance weight is provided at a position different from the projection of the synchronization ring, so that the elliptical deformation due to the projection of the synchronization ring is canceled out, and the synchronization ring is close to a perfect circle even during rotation. In this state, uneven contact between the cone portion of the transmission gear and the tapered portion of the synchronous ring can be eliminated, and uneven wear of the tapered portion can be favorably prevented. Thereby, the malfunction of the synchronization ring and thus the synchronization device can be prevented, and the life of the synchronization device can be extended.
[0033]
According to the transmission synchronizing device of the second aspect, in the case where two lever members having the same shape are provided, and two projections are provided diagonally on the synchronizing ring in accordance therewith, the balance weight is provided. Are provided diagonally at a position substantially 90 degrees from the protrusion, so that the elliptical deformation due to the protrusion can be favorably canceled, and the synchronization ring can be favorably maintained in a state close to a perfect circle.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a transmission synchronizing device according to the present invention.
FIG. 2 is a view of a synchronization device main body as viewed from a second speed gear side.
FIG. 3 is a diagram in which a synchronous ring unit and a center cone are removed from FIG. 2;
FIG. 4 is a view of the outer ring viewed from a hub side.
[Explanation of symbols]
1 Output shaft 10 2nd gear 20 3rd gear 30 Synchronizer main body 32 Hub 40 Sleeve 50 Synchronous ring unit 52 Center cone 54 Inner ring 56 Outer ring 57 Projection 57a Notch 59 Balance weight 60, 61 Lever member

Claims (2)

A hub fixed to the rotating shaft so as to be integrally rotatable,
A sleeve that is spline-fitted to the outer periphery of the hub, is supported so as to be movable in the axial direction, and rotates integrally with the rotation shaft,
A transmission gear that is rotatably supported around the rotation axis in proximity to the hub, and a clutch part that is spline-fitted with the sleeve and a cone part that has a friction surface for synchronization is integrally provided on the hub side;
A synchronous ring that is disposed so as to be able to rotate integrally with the hub, and is provided with an annular tapered portion having a friction surface for synchronization that can be pressed against the cone portion of the transmission gear;
A plurality of arc-shaped members are provided between the hub and the synchronization ring along the synchronization ring, and a part of the outer periphery comes into contact with the sleeve during the synchronization operation to transmit the pressing force of the sleeve to the synchronization ring. A lever member,
The synchronous ring is provided integrally with the hub side so as to protrude toward the hub, and is fitted with a certain play in the circumferential direction in a gap between adjacent lever members of the plurality of lever members, and during synchronization, The lever member is pressed radially outward by the frictional force between the cone portion and the tapered portion, and the lever member moves radially inward until the synchronization between the hub and the transmission gear reaches a predetermined synchronization state. And a plurality of protrusions that regulate
The synchronization device for a transmission, wherein the synchronization ring has a balance weight at a position different from the protrusion. The plurality of lever members include two lever members having the same shape, and the plurality of protrusions are provided diagonally on the synchronization ring.
2. The transmission synchronizing device according to claim 1, wherein the synchronizing ring has two diagonal pieces of the balance weight at positions substantially 90 degrees from the protrusion. 3.

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