JP2010096331A - Synchronizing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a synchronizing device suppressing deterioration of synchronization performance due to abrasion of a member. <P>SOLUTION: The synchronizing device 1 includes a gear 2, a synchronizer ring 3, a synchronization hub 4, and a coupling sleeve 5. The gear 2 has a first cone face 23a slanted with respect to a rotation axis A of a shaft 9, and a second cone face 23b slanted with respect to the rotation axis A. The synchronizer ring has a third cone face 31a abutting on the first cone face 23a, and a fourth cone face 31b slidable with the second cone face 23b. The first cone face 23a ad the third cone face 31a are slanted with respect to the rotation axis A for just a first cone angle C1. The second cone face 23 includes a face slanted with respect to the rotation axis A for just a second cone angle C2 different from the first cone angle C1. The fourth cone face 31b includes a face slanted with respect to the rotation axis A for just the second cone angle C2. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a synchronization device used in a transmission.

  In the transmission, a synchronization device is used to realize a smooth shifting operation. This type of synchronizer includes, for example, a gear, a synchronizer ring, a sync hub, a coupling sleeve, and a sync key. The gear is a member supported by the shaft so as to be rotatable with respect to the shaft, and includes a transmission gear portion, a clutch gear portion, and a first sliding portion having a first cone surface. The synchronizer ring is an annular member supported by the first sliding portion and has a second cone surface that slides with the first cone surface. The sync hub is fixed to the shaft. The coupling sleeve is supported by the synchro hub so as to be movable in the axial direction and integrally rotatable with respect to the synchro hub. The synchronizer ring is supported by the synchro hub so as to be movable in the axial direction and rotatable integrally with the synchro hub. The synchro key is a member that moves in the axial direction together with the coupling sleeve, and is accommodated in the groove of the synchro hub.

The coupling sleeve moves in the axial direction in accordance with the movement of the shift lever. When the coupling sleeve moves in the axial direction, the synchronizer ring is pushed by the sync key. As a result, the first cone surface and the second cone surface slide, and a frictional force acts between the synchronizer ring and the gear. Due to this frictional force, the rotation speeds of the synchronizer ring and the gear are substantially the same, and the rotation of the gear can be synchronized with the rotation of the shaft. Thereby, a smooth speed change operation is possible (for example, refer to Patent Document 1).
JP-A-6-159389

In this type of synchronizer, since the synchronizer ring and the gear slide, for example, the synchronizer ring or the sliding portion of the gear wears. For example, if the synchronizer ring is worn, the relative position in the axial direction of the synchronizer ring with respect to the gear changes during synchronization, and the clutch gear portion and the synchronizer ring may interfere with each other. When the clutch gear portion and the synchronizer ring interfere with each other, the synchronizer ring does not move in the axial direction with respect to the gear, and the pressing force when the second cone surface is pressed against the first cone surface is reduced. As a result, the frictional force of the magnitude required for the synchronous operation is not generated between the first cone surface and the second cone surface. That is, there is a possibility that the synchronization performance is deteriorated due to wear of the members.
The subject of this invention is providing the synchronizer which can suppress that synchronous performance falls by abrasion of a member.

  The synchronization device according to the present invention includes a gear member, a synchronizer ring, a synchro hub, and a coupling sleeve. The gear member is a member that is supported by the shaft so as to be rotatable with respect to the shaft, and includes a transmission gear portion, a clutch gear portion that is provided to rotate integrally with the transmission gear portion, and a rotation shaft of the shaft. It has the 1st sliding surface which inclines with respect to it, and the 2nd sliding surface which inclines with respect to a rotating shaft. The sync hub is fixed to the shaft. The synchronizer ring includes a third sliding surface that is inclined with respect to the rotation axis and in contact with the first sliding surface, and a fourth sliding that is inclined with respect to the rotation axis and is slidable with the second sliding surface. And a surface. The coupling sleeve is supported by the synchro hub so as to be movable in an axial direction with respect to the synchro hub and to be integrally rotatable, and presses the synchronizer ring against the gear member. The first sliding surface is inclined with respect to the rotation axis by a first angle. The second sliding surface includes a surface that is inclined with respect to the rotation axis by a second angle different from the first angle. The third sliding surface is inclined with respect to the rotation axis by the first angle. The fourth sliding surface includes a surface that is inclined with respect to the rotation axis by the second angle.

In this synchronization device, a frictional force is generated between the synchronizer ring and the gear member by sliding the first sliding surface and the third sliding surface. When at least one of the synchronizer ring and the gear member is worn, the axial position of the synchronizer ring with respect to the gear member at the time of synchronization approaches the clutch gear portion.
In this case, when the second sliding surface and the fourth sliding surface are slidable in addition to the first sliding surface and the third sliding surface, at least one of the synchronizer ring and the gear member is worn. Furthermore, the axial position of the synchronizer ring with respect to the gear member can be prevented from approaching the clutch gear portion by the second sliding surface and the fourth sliding surface. In particular, since the second sliding surface and the fourth sliding surface are inclined by the second angle with respect to the rotation axis, the frictional force necessary for synchronization is ensured and the gear member of the synchronizer ring is synchronized during synchronization. It can suppress that an axial direction position approaches a clutch gear part. That is, in this synchronization device, it is possible to suppress a decrease in synchronization performance due to member wear.

  Here, the “sliding surface” includes not only one continuously formed surface but also a surface that is divided into a plurality of regions as a result of forming a recessed portion such as a groove. .

  As described above, in the synchronization device according to the present invention, it is possible to suppress a decrease in synchronization performance due to wear of members.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
<Synchronizer configuration>
The synchronization device 1 will be described with reference to FIGS. 1 and 2. FIG. 1 is a schematic cross-sectional view of the synchronization device 1. FIG. 2 is a schematic sectional view (initial state) of the synchronizer ring 3 and the gear 2.
The synchronization device 1 is a mechanism for synchronizing the rotation of the shaft 9 and the gear 2 of the transmission, and is supported by the shaft 9. Specifically, as shown in FIG. 1, the synchronization device 1 includes a sync hub 4, a coupling sleeve 5, three sync keys 6, two sync springs 7, and a gear 2 (an example of a gear member). , And a synchronizer ring 3. When the synchronizer 1 is not operating, members other than the gear 2 are rotating together with the shaft 9.

The synchro hub 4 is fixed to the shaft 9 and has a plurality of external teeth 41 protruding outward in the radial direction. A synchronizer ring 3 is fitted in the synchronizer hub 4 so as to be movable in the axial direction and integrally rotatable.
The coupling sleeve 5 is an annular member for connecting the synchro hub 4 to a clutch gear portion 22 (described later) of the gear 2, and is supported by the synchro hub 4 so as to be movable in the axial direction. More specifically, the coupling sleeve 5 has a plurality of internal teeth 53 protruding radially inward. Since the inner teeth 53 mesh with the outer teeth 41 of the synchro hub 4, the coupling sleeve 5 can move in the axial direction and can rotate integrally with the synchro hub 4.
Since a shift fork (not shown) is fitted in the outer circumferential groove 51 of the coupling sleeve 5, the operating force of the shift lever is transmitted to the coupling sleeve 5 via the shift fork. Each inner tooth 53 has a recess 52 into which the protrusion 61 of the synchro key 6 is fitted.

The sync key 6 is a member for pressing the synchronizer ring 3 in the axial direction, and is accommodated in a groove (not shown) formed in the synchro hub 4 so as to be movable in the axial direction. The protrusion 61 of the synchro key 6 is fitted into a recess 52 formed in the internal tooth 53 of the coupling sleeve 5. The sync spring 7 is a generally ring-shaped spring, and presses the sync key 6 radially outward. The sync spring 7 is supported by the sync hub 4 and is fitted into an inner peripheral groove 62 formed on the inner peripheral side of the sync key 6.
The gear 2 is an annular member supported by the shaft 9 so as to be rotatable with respect to the shaft 9, and is made of, for example, iron. The gear 2 includes a transmission gear portion 21, a clutch gear portion 22, and a sliding portion 23.

The transmission gear portion 21 has a plurality of external teeth 21a extending radially outward, and meshes with other gears (not shown). The clutch gear portion 22 is a portion disposed on the side of the transmission gear portion 21 and has a plurality of external teeth 22a extending outward in the radial direction.
The sliding portion 23 is an annular portion disposed between the clutch gear portion 22 and the synchro hub 4 in the axial direction, and protrudes in the axial direction from the clutch gear portion 22 toward the synchro hub 4 side. The sliding part 23 has a first cone surface 23a (an example of a first sliding surface) and a second cone surface 23b (an example of a second sliding surface) on the outer peripheral side.
The first cone surface 23 a is a conical surface inclined with respect to the rotation axis A of the shaft 9. An inclination angle (so-called cone angle) of the first cone surface 23a with respect to the rotation axis A is defined as a first cone angle C1. The second cone surface 23b is a conical surface inclined with respect to the rotation axis A. When the inclination angle of the second cone surface 23b with respect to the rotation axis A is the second cone angle C2, the second cone angle C2 is set to be larger than the first cone angle C1. The second cone surface 23 b is formed continuously with the first cone surface 23 a, and further formed continuously with the annular side surface 22 b of the clutch gear portion 22.

The synchronizer ring 3 is an annular member supported in the radial direction by the gear 2 and is made of, for example, brass. Since the gear 2 is made of iron, when the synchronizer ring 3 and the gear 2 slide, the synchronizer ring 3 is mainly worn and the gear 2 is hardly worn. The synchronizer ring 3 is attached to the synchro hub 4 so as to be movable in the axial direction and rotatable integrally with the synchro hub 4. The synchronizer ring 3 has a third cone surface 31a (an example of a third sliding surface) and a fourth cone surface 31b (an example of a fourth sliding surface) on the inner peripheral side.
The third cone surface 31a is a conical surface inclined with respect to the rotation axis A, and is slidable with the first cone surface 23a. The inclination angle of the third cone surface 31a with respect to the rotation axis A is the same as the first cone angle C1. That is, the cone angle of the third cone surface 31a is the first cone angle C1.

The fourth cone surface 31b is a conical surface inclined with respect to the rotation axis A, and is slidable with the second cone surface 23b. The inclination angle of the fourth cone surface 31b with respect to the rotation axis A is the same as the second cone angle C2. That is, the cone angle of the fourth cone surface 31b is the second cone angle C2. The second cone angle C2 of the fourth cone surface 31b is set larger than the first cone angle C1 of the third cone surface 31a.
In an initial state in which the sliding portion 23 of the gear 2 and the synchronizer ring 3 are not worn, a gap is secured between the second cone surface 23b and the fourth cone surface 31b in the axial direction. A gap is also secured between the moving portion 32 and the side surface 22b of the clutch gear portion 22 in the axial direction. For this reason, the 2nd cone surface 23b does not slide with the 4th cone surface 31b in an initial stage. In the initial stage when the member is not worn, the dimension of the gap between the clutch gear portion 22 and the synchronizer ring 3 in the axial direction is defined as a dimension L.

For example, when the wear of the synchronizer ring 3 proceeds, the dimension L gradually decreases, and eventually the second cone surface 23b starts to slide with the fourth cone surface 31b. That is, it can be said that the second cone surface 23b and the fourth cone surface 31b are surfaces that slide after the sliding portion 23 (more specifically, the periphery of the first cone surface 23a of the sliding portion 23) is worn.
<Operation of synchronization device>
The operation of the synchronization device 1 will be described with reference to FIGS. When the synchronizer 1 is not operating, members other than the gear 2 are rotating together with the shaft 9. Here, it is assumed that the rotation speed of the gear 2 is smaller than the rotation speed of the shaft 9.
For example, when a shift fork (not shown) moves to the axial gear 2 side (right side in FIG. 1), the coupling sleeve 5 moves to the axial gear 2 side with respect to the sync hub 4. At this time, since the protrusion 61 is fitted in the recess 52 of the coupling sleeve 5, the synchro key 6 also moves to the gear 2 side in the axial direction together with the coupling sleeve 5.

  When the sync key 6 moves to the gear 2 side in the axial direction, the sync key 6 comes into contact with the synchronizer ring 3. In this state, when an axial operation force is transmitted from the shift fork to the coupling sleeve 5, the operation force is transmitted to the synchronizer ring 3 via the sync key 6. As a result, the third cone surface 31 a of the synchronizer ring 3 is pressed against the first cone surface 23 a of the gear 2, and a frictional force is generated between the synchronizer ring 3 and the gear 2. Due to this frictional force, the gear 2 tries to rotate together with the synchronizer ring 3, and the rotational speed of the gear 2 gradually increases. When the operating force transmitted from the shift fork exceeds a certain level, the protrusion 61 of the synchro key 6 is pushed inward in the radial direction by the inner teeth 53 of the coupling sleeve 5, and the synchro key 6 moves inward in the radial direction. To do. At this time, the sync spring 7 is elastically deformed so that the diameter becomes small while the sync key 6 is pressed radially outward. Since the synchronizer key 6 is in contact with the synchronizer ring 3 in the axial direction, only the coupling sleeve 5 moves toward the transmission gear portion 21 in the axial direction with respect to the synchronizer ring 3.

When the coupling sleeve 5 moves in the axial direction, the outer teeth 33 of the synchronizer ring 3 are pushed in the axial direction by the inner teeth 53 of the coupling sleeve 5. As a result, the frictional force generated between the synchronizer ring 3 and the gear 2 is increased, and the rotational speed of the gear 2 is increased just before the inner teeth 53 of the coupling sleeve 5 are engaged with the outer teeth 22a of the clutch gear portion 22. The rotational speed of the synchronizer ring 3 and the coupling sleeve 5 is substantially the same. When the coupling sleeve 5 further moves in the axial direction in this state, the inner teeth 53 of the coupling sleeve 5 are guided to the outer teeth 33 of the synchronizer ring 3 and finally the outer teeth 22a of the clutch gear portion 22 and Engage. As a result, the gear 2 is coupled to the sync hub 4 by the coupling sleeve 5, and the gear 2 rotates together with the shaft 9.
<Influence of member wear>
Here, the influence of wear of the synchronizer ring 3 will be described with reference to FIGS. 3 and 4 are schematic sectional views (wear state) of the synchronizer ring and the gear. FIG. 3 shows a state where the second cone surface 23b is in contact with the fourth cone surface 31b, and FIG. 4 shows a state where the synchronizer ring 3 is further worn from the state of FIG.

As described above, since the synchronizer ring 3 slides with the sliding portion 23 of the gear 2 during the shifting operation, the synchronizer ring 3 formed of a metal softer than the gear 2 is gradually worn. As the wear of the synchronizer ring 3 proceeds, the fourth cone surface 31b eventually comes into contact with the second cone surface 23b (see, for example, FIG. 3).
When the fourth cone surface 31b comes into contact with the second cone surface 23b, in addition to the space between the first cone surface 23a and the third cone surface 31a, the second cone surface 23b and the fourth cone surface 31b A frictional force is generated even between the two. Here, since the first cone angle C1 is smaller than the second cone angle C2, the frictional force generated between the first cone surface 23a and the third cone surface 31a is the second cone surface 23b and the fourth cone surface 31b. It is larger than the frictional force generated between the two. For this reason, the periphery of the fourth cone surface 31b of the synchronizer ring 3 is less likely to wear than the periphery of the third cone surface 31a.

Further, since the second cone angle C2 is larger than the first cone angle C1, the synchronizer ring 3 can be used even if the peripheral portion of the fourth cone surface 31b is worn compared to the case where the peripheral portion of the third cone surface 31a is worn. The axial position with respect to the gear 2 does not change so much (for example, see FIG. 4).
For these reasons, the axial position of the synchronizer ring 3 with respect to the gear 2 is more in the state where the fourth cone surface 31b slides with the second cone surface 23b than in the initial state. It is possible to suppress changes due to wear.
However, in the initial state, since the first cone surface 23a and the third cone surface 31a having a small cone angle slide with each other, a large force is generated by the synchronizer ring 3 to tighten the sliding portion 23, and a large frictional force is generated. Can be generated.
<Features of synchronization device>
The characteristics of the synchronization device 1 described above are summarized below.

(1)
In the synchronization device 1, a frictional force is generated between the synchronizer ring 3 and the gear 2 by sliding the first cone surface 23 a and the third cone surface 31 a. For example, when the synchronizer ring 3 is worn, the axial position of the synchronizer ring 3 with respect to the gear 2 during the synchronous operation approaches the clutch gear portion 22.
In this case, since the second cone surface 23b and the fourth cone surface 31b can slide in addition to the first cone surface 23a and the third cone surface 31a, the synchronizer ring 3 is worn when the synchronizer ring 3 is worn. The second cone surface 23b and the fourth cone surface 31b can suppress the axial position of the second gear from approaching the clutch gear portion 22. In particular, since the second cone surface 23b and the fourth cone surface 31b are inclined by the second cone angle C2 with respect to the rotation axis A, the friction force necessary for the synchronization operation is secured to some extent, and the synchronization is performed during the synchronization operation. It is possible to suppress the axial position of the kniter ring 3 relative to the gear 2 from approaching the clutch gear portion 22. That is, it can suppress that a synchronous performance falls by abrasion of a member.

For example, as shown in FIG. 5, the amount of decrease in the dimension L between the clutch gear portion 22 and the synchronizer ring 3 in the axial direction is smaller than that of a conventional synchronizer without the second cone surface 23b and the fourth cone surface 31b. Can be suppressed.
(2)
When the second cone surface 23b and the fourth cone surface 31b slide in addition to the first cone surface 23a and the third cone surface 31a, the pressing force transmitted to the synchronizer ring 3 is dispersed to these cone surfaces. . In addition, since the second cone angle C2 is larger than the first cone angle C1, the force with which the synchronizer ring 3 tightens the sliding portion 23 is also reduced around the fourth cone surface 31b.
For these reasons, when the sliding of the second cone surface 23b and the fourth cone surface 31b starts, the resistance force in the rotational direction acting between the synchronizer ring 3 and the sliding portion 23 is expected to be slightly reduced. Is done. When the resistance force between the synchronizer ring 3 and the sliding portion 23 is reduced, the time required for synchronization is slightly increased.

In the synchronization device 1, since the second cone surface 23b slides on the fourth cone surface 31b after the third cone surface 31a of the synchronizer ring 3 is worn, the second cone surface 23b and the fourth cone are started from the initial state. Compared with the case where the surface 31b is in contact, the period until the second cone surface 23b and the fourth cone surface 31b are used can be lengthened. Therefore, it is possible to maintain a state where the synchronization operation is completed in a short time as long as possible. Thereby, compared with the case where the 2nd cone surface 23b and the 4th cone surface 31b are used from the beginning, it can suppress reliably that a synchronous performance falls by abrasion of a member.
(3)
In the synchronization device 1, since the second cone angle C2 is set larger than the first cone angle C1, the frictional force generated between the first cone surface 23a and the third cone surface 31a is generated by the second cone surface 23b. And the frictional force generated between the fourth cone surface 31b is larger.

Conversely, since the second cone angle C2 is set to be larger than the first cone angle C1, even if the peripheral portion of the fourth cone surface 31b of the synchronizer ring 3 is worn, the synchronizer ring 3 is not synchronized. The axial position with respect to the gear 2 is unlikely to change. Thereby, it can prevent that the synchronizer ring 3 interferes with the clutch gear part 22, and can suppress reliably that a synchronous performance falls by abrasion of a member.
<Other embodiments>
The specific configuration of the present invention is not limited to the above-described embodiment, and various changes and modifications can be made without departing from the scope of the invention.
In addition, about the structure which has the function substantially the same as the above-mentioned embodiment, the same code | symbol is used and detailed description is abbreviate | omitted.

(A)
In the above-described embodiment, the second cone surface 23b and the fourth cone surface 31b are conical surfaces, but the second cone surface 23b and the fourth cone surface 31b may be curved with respect to the rotation axis A. . Here, the state of “curving with respect to the rotation axis A” means a state in which the cone angle of the cone surface is gradually changed with the axial direction as a reference.
For example, the synchronization device 101 illustrated in FIGS. 6 to 8 includes a gear 102 and a synchronizer ring 103. The gear 102 has a first cone surface 123a and a second cone surface 123b. The synchronizer ring 103 has a sliding portion 123 formed with a third cone surface 131a and a fourth cone surface 131b. The first cone surface 123a and the third cone surface 131a are conical surfaces that are inclined with respect to the rotation axis A, similarly to the first cone surface 23a and the third cone surface 31a described above, and the cone angle is the first cone angle. The cone angle C11.

On the other hand, unlike the second cone surface 23b and the fourth cone surface 31b, the second cone surface 123b and the fourth cone surface 131b are curved with respect to the rotation axis A. More specifically, the second cone surface 123b is formed such that the second cone angle C12 gradually increases from the first cone surface 123a to the side surface 22b, and has a first radius of curvature R1. The fourth cone surface 131b is formed so that the cone angle gradually increases from the third cone surface 131a to the side surface 132b, and has a second radius of curvature R2. The second curvature radius R2 is set smaller than the first curvature radius R1.
In this case, as shown in FIG. 9, the reduction amount of the dimension L is gradually reduced from the middle as compared with the conventional synchronization device. For this reason, it can suppress that synchronous performance falls by abrasion of a member like the above-mentioned embodiment.

Further, in the synchronization device 1, the fourth cone surface 31b includes a curved surface that is curved with respect to the rotation axis A by the second curvature radius R2 that is smaller than the first curvature radius R1, and therefore, from the second cone surface 123b. The fourth cone surface 131b can be prevented from coming into contact with the side surface 22b first, and the fourth cone surface 131b can be efficiently brought into contact with the second cone surface 123b.
(B)
In the above-described embodiment, the single cone type synchronization device 1 has been described. However, a multi cone type synchronization device may be used. For example, the synchronization device 201 shown in FIG. 10 includes a gear 202 (an example of a gear member, an example of a gear member body), a first synchronizer ring 203 (an example of a synchronizer ring, an example of a first ring member), and an intermediate ring. 208 and a second synchronizer ring 207 (an example of a synchronizer ring, an example of a second ring member).

The gear 202 has a transmission gear portion 21, a clutch gear portion 222, and a sliding portion 223. The sliding part 223 has a first cone surface 223a (an example of a fifth sliding surface) and a second cone surface 223b (an example of a sixth sliding surface) on the outer peripheral side. The cone angle of the first cone surface 223a is a first cone angle C21 (an example of a fifth angle). The cone angle of the second cone surface 223b is the second cone angle C22 (an example of a sixth angle).
The intermediate ring 208 is an annular member provided to rotate integrally with the gear 202, and includes a first intermediate cone surface 281a (an example of a first sliding surface) and a second intermediate cone surface 281b (a second sliding surface). An example of a surface), and a plurality of protrusions 289 inserted into the plurality of recesses 222b of the clutch gear portion 222. The cone angle of the first intermediate cone surface 281a is the same as the first cone angle C21 (an example of the first angle). The cone angle of the second intermediate cone surface 281b is the same as the second cone angle C22 (an example of the second angle).

The first synchronizer ring 203 is an annular member disposed on the radially outer side of the intermediate ring 208 and corresponds to the above-described synchronizer ring 3. The first synchronizer ring 203 has a third intermediate cone surface 231a (an example of a third sliding surface) and a fourth intermediate cone surface 231b (an example of a fourth sliding surface) on the inner peripheral side. Yes. The cone angle of the third intermediate cone surface 231a is the same as the first cone angle C21. The cone angle of the fourth intermediate cone surface 231b is the same as the second cone angle C22. In the initial state, a gap is secured between the second intermediate cone surface 281b and the fourth intermediate cone surface 231b.
The second synchronizer ring 207 is an annular member sandwiched between the intermediate ring 208 and the sliding portion 223 in the radial direction, and the third cone surface 271a and the fourth cone surface 271b are arranged on the inner peripheral side. Have. The second synchronizer ring 207 has a sixth cone surface 273 on the outer peripheral side. The cone angle of the third cone surface 271a is the same as the first cone angle C21. The cone angle of the fourth cone surface 271b is the same as the second cone angle C22. In the initial state, a gap is secured between the second cone surface 223b and the fourth cone surface 271b. Since the second synchronizer ring 207 is provided so as to rotate integrally with the first synchronizer ring 203, the fifth cone surface 283 of the intermediate ring 208 slides with the sixth cone surface 273 of the second synchronizer ring 207. Move.

In the synchronization device 201, when the first synchronizer ring 203 is pushed in the axial direction by the coupling sleeve 5 via the synchronizer key 6, the intermediate ring 208 and the sliding portion 223 are interposed between the intermediate ring 208 and the sliding portion 223. A second synchronizer ring 207 is sandwiched. As a result, a frictional force is generated between the first intermediate cone surface 281a and the third intermediate cone surface 231a, a frictional force is generated between the fifth cone surface 283 and the sixth cone surface 273, and the first cone surface 223a. A frictional force is generated between the third cone surface 271a.
For example, when the first synchronizer ring 203 and the sliding portion 223 are worn, the state shown in FIG. In this state, the fourth cone surface 271b is in contact with the second cone surface 223b, and the fourth intermediate cone surface 231b is in contact with the second intermediate cone surface 281b.

Even in this case, the axial position of the first synchronizer ring 203 with respect to the gear 202 during the synchronous operation can be prevented from approaching the clutch gear portion 222 as in the above-described embodiment.
(C)
Furthermore, a synchronization device 301 shown in FIG. 12 is also conceivable as a multi-cone type synchronization device. This synchronizer 301 has friction surfaces increased on the intermediate ring 208 and the second synchronizer ring 207 of the synchronizer 201 described above. Specifically, the synchronizer 301 includes a first synchronizer ring 203 (an example of a synchronizer ring, an example of a first ring member), an intermediate ring 308, and a second synchronizer ring 307 (an example of a synchronizer ring, An example of a second ring member) and a gear 202 (an example of a gear member, an example of a gear member main body).

The intermediate ring 308 includes a first intermediate cone surface 281a (an example of a first sliding surface), a second intermediate cone surface 281b (an example of a second sliding surface), and a fifth cone surface 383 (a first intermediate sliding surface). And a sixth cone surface 384 (an example of a second intermediate sliding surface). The cone angle of the fifth cone surface 383 is the first cone angle C21 (an example of a third angle). The cone angle of the sixth cone surface 384 is the second cone angle C22 (an example of the fourth angle). The first intermediate cone surface 281 a and the second intermediate cone surface 281 b are formed on the outer peripheral side of the intermediate ring 308. The fifth cone surface 383 and the sixth cone surface 384 are formed on the inner peripheral side of the intermediate ring 308.
The second synchronizer ring 307 includes a third cone surface 271a (an example of a seventh sliding surface), a fourth cone surface 271b (an example of an eighth sliding surface), and a seventh cone surface 373 (a third intermediate slide). An example of a moving surface) and an eighth cone surface 374 (an example of a fourth intermediate sliding surface). The cone angle of the seventh cone surface 373 is the first cone angle C21. The cone angle of the eighth cone surface 374 is the second cone angle C22. The third cone surface 271 a and the fourth cone surface 271 b are formed on the inner peripheral side of the second synchronizer ring 307. The seventh cone surface 373 and the eighth cone surface 374 are formed on the outer peripheral side of the intermediate ring 308. The seventh cone surface 373 is in contact with the fifth cone surface 383. In the initial state, a gap is secured between the sixth cone surface 384 and the eighth cone surface 374.

Even in this case, similarly to the above-described embodiment, it is possible to suppress a decrease in synchronization performance due to wear of members.
(D)
Although the synchronization devices 201 and 301 shown in FIGS. 10 to 12 are described as examples of the multi-cone type synchronization device, the sliding surface that generates the greatest resistance in the rotational direction during synchronization is located on the outermost side. Since the sliding surfaces are arranged, it can be said that the sliding surface on which wear is likely to proceed is the sliding surface arranged on the outermost periphery side. Therefore, for example, in the synchronization device 201 shown in FIG. 10, the wear of the first intermediate cone surface 281a and the third intermediate cone surface 231a tends to proceed. In other words, even if the second intermediate cone surface 281b and the fourth intermediate cone surface 231b are provided only on the clutch gear portion 222 side of the first intermediate cone surface 281a and the third intermediate cone surface 231a, a decrease in synchronization performance can be suppressed.

Specifically, in the synchronization device 401 shown in FIG. 13, the second cone surface 223b and the fourth cone surface 271b of the synchronization device 201 shown in FIG. 10 do not exist, and the first cone surface 223a and the third cone surface 271a are the clutches. It is formed up to the vicinity of the gear portion 222. Even in this case, the second intermediate cone surface 281b and the fourth intermediate cone surface 231b are provided on the clutch gear portion 222 side of the first intermediate cone surface 281a and the third intermediate cone surface 231a arranged on the outermost periphery side. Therefore, similarly to the above-mentioned embodiment, it can suppress that a synchronous performance falls by abrasion of a member.
(E)
In the above-described embodiment, the cone surface (an example of the sliding surface) is divided into a plurality of regions as a result of forming a concave portion such as a groove in addition to one continuously formed surface. It also includes the surface.

For example, a plurality of annular grooves 335 may be formed in the third cone surface 331a and the fourth cone surface 331b as in the synchronizer ring 303 shown in FIG. In this case, the third cone surface 331a is divided into a plurality of regions, but the third cone surface 331a and the fourth cone surface 331b in this case are also included in the concept of the cone surface.
(F)
In the above-described embodiment, it is described that the second cone surface 23b slides with the fourth cone surface 31b after at least one of the first cone surface 23a and the third cone surface 31a is worn. The second cone surface 23b may slide with the fourth cone surface 31b.
(G)
In the above-described embodiment, it is described that the synchronizer ring 3 is mainly worn. However, the present invention is not limited to such a case. For example, the material may be adjusted so that not the synchronizer ring 3 but the gear 2 is mainly worn. It is also conceivable that both the synchronizer ring 3 and the gear 2 are worn.

  Furthermore, although the wear of the member is cited as a factor that decreases the synchronization performance, deformation of the wear material (for example, a carbon material) attached to the member is also considered as a factor that decreases the synchronization performance. When the wear material is compressed by the pressing force, the thickness of the wear material becomes thin. As a result, the synchronizer ring approaches the clutch gear portion and the clutch gear portion and the synchronizer ring interfere with each other as in the case where the member is worn. That is, the synchronization performance also deteriorates due to the deformation of the friction material attached to the member.

  Since the synchronization device according to the present invention can suppress a decrease in synchronization performance due to wear of members, the present invention is useful in the field of transmissions.

Schematic cross section of the synchronization device Schematic cross section of synchronizer ring and gear (initial state) Schematic sectional view of the synchronizer ring and gear (wear state) Schematic sectional view of the synchronizer ring and gear (wear state) Graph for comparison with conventional technology Schematic cross section of synchronizer ring and gear (initial state) Schematic sectional view of the synchronizer ring and gear (wear state) Schematic sectional view of the synchronizer ring and gear (wear state) Graph for comparison with conventional technology Schematic cross section of synchronizer ring and gear (initial state) Schematic sectional view of the synchronizer ring and gear (wear state) Schematic cross section of synchronizer ring and gear (initial state) Schematic cross section of synchronizer ring and gear (initial state) Schematic cross section of synchronizer ring and gear (example of cone surface)

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Synchronizer 2 Gear (an example of a gear member)
DESCRIPTION OF SYMBOLS 3 Synchronizer ring 4 Synchro hub 5 Coupling sleeve 6 Synchro key 7 Syncro spring 9 Shaft 21 Transmission gear part 22 Clutch gear part 23 Sliding part 23a 1st cone surface (an example of 1st sliding surface)
23b Second cone surface (an example of a second sliding surface)
31a Third cone surface (an example of a third sliding surface)
31b 4th cone surface (an example of the 4th sliding surface)
223a First cone surface (an example of a fifth sliding surface)
223b Second cone surface (an example of a sixth sliding surface)
231a Third intermediate cone surface (an example of a third sliding surface)
231b Fourth intermediate cone surface (an example of a fourth sliding surface)
281a First intermediate cone surface (an example of a first sliding surface)
281b Second intermediate cone surface (an example of a second sliding surface)
373 7th cone surface (example of third intermediate sliding surface)
374 Eighth cone surface (example of fourth intermediate sliding surface)
383 Fifth cone surface (an example of a first intermediate sliding surface)
384 6th cone surface (example of second intermediate sliding surface)

Claims (8)

A member that is supported by the shaft so as to be rotatable with respect to the shaft, the transmission gear portion, a clutch gear portion that is provided to rotate integrally with the transmission gear portion, and a rotation axis of the shaft; A gear member having a first sliding surface inclined and a second sliding surface inclined with respect to the rotation axis;
A synchro hub fixed to the shaft;
A third sliding surface that is inclined with respect to the rotating shaft and is in contact with the first sliding surface; and a fourth sliding surface that is inclined with respect to the rotating shaft and is slidable with the second sliding surface. And a synchronizer ring having
A coupling sleeve supported by the synchro hub so as to be axially movable and integrally rotatable with respect to the synchro hub, and for pressing the synchronizer ring against the gear member;
The first sliding surface is inclined with respect to the rotation axis by a first angle;
The second sliding surface includes a surface inclined with respect to the rotation axis by a second angle different from the first angle;
The third sliding surface is inclined with respect to the rotation axis by the first angle;
The fourth sliding surface includes a surface that is inclined with respect to the rotation axis by the second angle.
Synchronizer. The second sliding surface slides with the fourth sliding surface after at least one of the first sliding surface and the third sliding surface is worn.
The synchronization device according to claim 1. The second sliding surface is disposed between the first sliding surface and the clutch gear portion in the axial direction,
The second angle is greater than the first angle;
The synchronization device according to claim 1 or 2. The second sliding surface and the fourth sliding surface are formed such that the second angle gradually increases as going to the clutch gear portion side in the axial direction.
The synchronization device according to any one of claims 1 to 3. The second sliding surface includes a curved surface that is curved by a first radius of curvature with respect to the rotation axis,
The fourth sliding surface includes a curved surface that is curved with respect to the rotation axis by a second radius of curvature that is smaller than the first radius of curvature.
The synchronization device according to any one of claims 1 to 4. The gear member includes a gear member main body having the transmission gear portion and the clutch gear portion, and is disposed so as to be integrally rotatable with respect to the clutch gear portion, and the first sliding surface and the second sliding surface are disposed on an outer peripheral side. An intermediate ring having
The synchronizer ring is provided so as to be integrally rotatable with respect to the synchro hub and is disposed on the radially outer side of the intermediate ring, and is provided so as to be integrally rotatable with respect to the synchro hub. A second ring member disposed radially inward of
The first ring member has the third sliding surface and the fourth sliding surface on the inner peripheral side,
The synchronization device according to any one of claims 1 to 5. The intermediate ring has a first intermediate sliding surface inclined with respect to the rotation axis by a third angle and a second intermediate sliding surface inclined with respect to the rotation axis by a fourth angle on the inner peripheral side. Have
The second ring member is inclined with respect to the rotation axis by the third angle and is slidable with the first intermediate sliding surface, and the fourth angle with respect to the rotation axis by the fourth angle. A fourth intermediate sliding surface that is inclined and slidable on the outer peripheral side.
The synchronization device according to claim 6. The gear member main body has a fifth sliding surface inclined with respect to the rotation axis by a fifth angle and a sixth sliding surface inclined with respect to the rotation axis by a sixth angle on the outer peripheral side. And
The second ring member is inclined with respect to the rotation axis by the fifth angle, and is inclined with respect to the rotation axis by the seventh sliding surface that can slide with the fifth sliding surface. And the sixth sliding surface and the slidable eighth sliding surface on the inner peripheral side,
The synchronization device according to claim 6 or 7.

Images