JP2007327548A - Synchronizing device and transmission equipped therewith - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a synchronizing device having great thrusting force and preventing the occurrence of biting. <P>SOLUTION: The synchronizing device comprises a synchronizer ring 42 laid between a gear 22 and a hub sleeve 60 for synchronizing the gear 22 with the hub sleeve 60. The gear 22 has a first inclined face 134 having a first inclination angle θ1 to a rotating shaft 13 and a second inclined face 234 having a smaller second inclination angle θ2 than the first inclination angle 134. The synchronizer ring 42 has contact with the first inclined face 134 before and after synchronizing operation and with the second inclined face 234 during synchronizing operation. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a synchronization device and a transmission using the same, and more particularly to a synchronization device that synchronizes a first rotation member and a second rotation member via a synchronization member and a transmission using the same. It is.

Conventional synchronizers include, for example, Japanese Utility Model Laid-Open No. 5-81538 (Patent Document 1), Japanese Utility Model Laid-Open No. 5-8054 (Patent Document 2), Japanese Utility Model Laid-Open No. 5-52366 (Patent Document 3), No. 156259 (Patent Document 4) and Japanese Utility Model Publication No. 51-39151 (Patent Document 5).
Japanese Utility Model Publication No. 5-81538 Japanese Utility Model Publication No. 5-8054 Japanese Utility Model Publication No. 5-52366 JP 52-156259 A Japanese Utility Model Publication No. 51-39151

  Patent Document 1 discloses a technique in which a conical inner peripheral surface of a synchronizer ring, that is, a contact surface with a gear-side circular body is formed as a threaded continuous groove, and a contact area is smaller on the small diameter side than on the large diameter side.

  In Patent Document 2, the angle of the taper surface of the outer sync ring and the inner sync ring and the angle of each taper surface of the center cone combined therewith, the taper surface on the small diameter side of the center cone, the outer sync ring, and the inner sync ring A technique is disclosed in which only different angles can be brought into contact with only the tapered surface of the ring.

  Patent Document 3 discloses a technique in which a first cone surface is formed on the small diameter side, a second cone surface is formed on the large diameter side, and the opening half angle of the second cone surface is set larger than the cone surface of the gear. ing.

  In Patent Document 4, a synchronizer ring having a cone surface with an angle larger than the limit cone angle and substantially integral with the transmission gear, and a synchronizer ring having a cone surface with an angle smaller than the limit cone angle and receiving a shift operation. The inner and outer peripheral surfaces are in contact with the cone surface of the synchronizer ring and the synchronizer disc, are at least divided into two parts, rotate integrally in the main direction with respect to the transmission gear, and can slide in a certain amount in the axial direction and in the radial direction A transmission meshing device including an intermediate disk that can be divided and floated is disclosed.

  Patent Document 5 discloses a transmission synchronizer configured to start contact from a conical surface of a synchronizer ring and a large diameter portion of a conical surface of a gear that contacts the conical surface.

  However, the conventional technique has a problem that the synchronizer ring bites into the gear side.

  Accordingly, the present invention has been made to solve the above-described problems, and provides a synchronizer capable of generating a large frictional force while suppressing biting and a transmission using the same. The purpose is to do.

  The synchronization device according to the present invention includes a first rotating member capable of rotating around a rotating shaft, a second rotating member capable of rotating around the rotating shaft with respect to the first rotating member, And a synchronization member that is interposed between the first rotation member and the second rotation member and can synchronize the first rotation member and the second rotation member. The first rotating member has a first inclined surface having a first inclination angle θ1 with respect to the rotation axis, and a second inclined surface having a second inclination angle θ2 smaller than the first inclined surface. The synchronizing member contacts the first inclined surface before and after the synchronizing operation, and the synchronizing member contacts the second inclined surface during the synchronizing operation.

  In the synchronizer configured as described above, the synchronizing member comes into contact with the second inclined surface having a small inclination angle during the synchronization operation, and thus the frictional force can be increased.

  On the other hand, since it contacts the first inclined surface having a large inclination before and after the synchronization operation, it is possible to prevent biting. As a result, it is possible to provide a synchronizer that can suppress the occurrence of biting and can generate a large frictional force.

  Preferably, when the friction coefficient between the synchronization member and the first and second inclined surfaces is μ, the first inclination angle θ1 and the friction coefficient satisfy the relationship represented by μ <tan θ1.

  A transmission according to the present invention includes the synchronization device described above.

  According to the present invention, it is possible to provide a synchronization device that can generate a large frictional force while suppressing biting of the synchronization member, and a transmission using the same.

  Embodiments of the present invention will be described below with reference to the drawings. In the following embodiments, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated. FIG. 1 is a cross-sectional view of a manual transmission according to an embodiment of the present invention.

  Referring to FIG. 1, manual transmission 100 is a power transmission device that converts the rotational speed and rotational torque of an engine and transmits it to drive wheels in accordance with the traveling state of an automobile. The manual transmission 100 may be a so-called remote control type manual transmission 100 in which a shift lever operated by a vehicle driver and the manual transmission 100 are separated from each other and are connected by a cable or a link. The manual transmission 100 may be a so-called direct control type manual transmission 100 in which a shift lever is directly attached to the manual transmission 100.

  In the remote control system, the position of the shift lever is not particularly limited, and the column shift type in which the shift lever is attached to the steering column portion is fitted to the rotary shaft 10 so as to be a shift lever.

  The fixing direction of the clutch hub 50 with respect to the rotary shaft 10 is not limited to spline fitting, and other methods such as welding may be used.

  In FIG. 1, the constituent members are arranged symmetrically about the rotation shaft 13. A gear 22 is fitted on the rotary shaft 10, and a bearing (not shown) exists between the gear 22 and the rotary shaft 10. Therefore, the gear 22 can rotate relative to the rotary shaft 10. In the state shown in FIG. 1, the rotational force of the rotary shaft 10 is not transmitted to the gear 22, and the gear 22 is idle. The inner peripheral surface side of the gear 22 faces the rotary shaft 10. Lubricating oil may be supplied between the gear 22 and the rotating shaft 10.

  The gear 22 is provided with a gear piece 32. The gear piece 32 may be integral with the gear 22 or may be a separate body. The gear piece 32 may be configured to rotate with the gear 22. The gear piece 32 is not engaged with the clutch hub 50 in the state shown in FIG. Therefore, the gear piece 32 can freely rotate with respect to the clutch hub 50.

  In the vicinity of the gear piece 32, a cone portion 34 that is inclined with respect to the rotation shaft 13 is provided. A synchronizer ring 42 is fitted on the cone portion 34. The synchronizer ring 42 is a member for synchronizing the gear 22, the clutch hub 50, and the hub sleeve 60, and has a cone portion 44 that is a tapered surface. The cone portion 44 provided on the inner peripheral side is in contact with the cone portion 34 of the gear 22 and slides by friction. The conical cone portion 44 is inclined with respect to the rotation shaft 13.

  The cone part 34 has a first inclined surface 134 having a large inclination angle and a second inclined surface 234 having a small inclination angle. The first inclination angle θ1 of the first inclined surface 134 is larger than the second inclination angle θ2 of the second inclined surface 234. The inclination angle gradually changes, and the inclination angle becomes smaller from the first inclined surface 134 toward the second inclined surface 234. That is, in this embodiment, the tilt angle is continuously changed, but the present invention is not limited to this, and the tilt angle may be intermittently changed. That is, it may be divided into a large first inclination angle θ1 and a small second inclination angle θ2 at a certain point.

  Before the start of the synchronization operation shown in FIG. 1, the cone portion 44 of the synchronizer ring 42 is in contact with the first inclined surface 134 of the cone portion 34 of the gear 22. The synchronizer ring 42 has outer peripheral teeth 46.

  A shifting key 65 is fitted to the clutch hub 50. The hub sleeve 60 is fitted to the shifting key 65. The hub sleeve 60 is slidable in the direction in which the rotary shaft 13 extends. The inner peripheral teeth 61 of the hub sleeve 60 are engaged with the clutch hub 50, and the inner peripheral teeth 61 can be engaged with the outer peripheral teeth 46 of the synchronizer ring 42 and the outer peripheral teeth 36 of the gear piece 32.

  The clutch hub 50 holds the hub sleeve 60 so as to be slidable in the axial direction. The hub sleeve 60 has a recess 62, and the recess 62 is sandwiched and held by a shift fork. When the shift fork moves the recess 62 in the direction of the rotation shaft 13, the hub sleeve 60 and the shifting key 65 are also moved in the direction of the rotation shaft 13. A concave portion 63 provided on the inner peripheral side of the hub sleeve 60 is fitted with the convex portion 69 of the shifting key 65.

  The present invention is not limited to this embodiment, and the present invention can be applied to a synchronizer having a so-called multi-cone synchronizer ring in which two or more synchronizer rings exist.

  FIG. 2 is a perspective view of the synchronizer ring in FIG. Referring to FIG. 2, the synchronizer ring 42 has a plurality of outer peripheral teeth 46 arranged in the circumferential direction. The cone portion 44 of the synchronizer ring 42 is provided on the inner peripheral surface side of the synchronizer ring 42. In the synchronizer ring 42, a cut 45 is provided so as to extend in the radial direction. The reason for providing such a cut 45 is to greatly change the cone angle of the synchronizer ring 42 before and during synchronization. That is, the notch 45 is provided in order to increase the deformation amount of the synchronizer ring 42. The notch 45 is not necessarily provided. If a material that is sufficiently elastically deformed is used, the notch 45 is not necessarily provided.

Next, the synchronization operation of the manual transmission shown in FIGS. 1 and 2 will be described.
A shift lever is connected to the shift fork. The shift fork moves by moving the shift lever. The shift fork moves the hub sleeve 60 in the direction indicated by the arrow 301. Since the convex portion 69 of the shifting key 65 is engaged with the concave portion 63 of the hub sleeve 60, the movement of the hub sleeve 60 is transmitted to the shifting key 65. The shifting key 65 presses the synchronizer ring 42 against the cone portion 34 of the gear 22 to start a synchronization operation (synchronization operation).

  FIG. 3 is a cross-sectional view of the manual transmission during the synchronous operation. Referring to FIG. 3, when the synchronizer ring 42 is pressed against the cone portion 34 by the shifting key 65, the synchronizer ring 42 contacts the second inclined surface 234 having a small inclination angle by the pressure from the shifting key 65. To do. Further, the inner peripheral teeth 61 of the hub sleeve 60 are in contact with the outer peripheral teeth 46 of the synchronizer ring 42. That is, during the synchronization operation, the force acting on the hub sleeve 60 overcomes the synchronizer key spring, and the hub sleeve 60 moves over the convex portion 69 of the shifting key 65 and moves to the gear 22 side. However, the inner peripheral teeth 61 as the splines on the inner side of the hub sleeve 60 and the outer peripheral teeth 46 as the splines of the synchronizer ring 42 are kept in contact with each other. Accordingly, the force applied to the hub sleeve 60 remains inconsistent and the synchronizer ring 42 is pressed more strongly against the cone portion 34 of the gear 22 via the splines that are in contact with each other, and a strong synchronizing action (synchronizing action) is performed by the friction force. At this time, since the cone portion 44 of the synchronizer ring 42 is in contact with the second inclined surface 234 having a small second inclination angle θ2, the pressing between the cone portion 44 and the second inclined surface 234 is performed with a strong force. Done.

  FIG. 4 is a cross-sectional view of the manual transmission at the end of the synchronization operation. Referring to FIG. 4, when the rotational speeds of hub sleeve 60 and gear 22 are equal, synchronizer ring 42 is free in the rotational direction. Accordingly, the inner peripheral teeth 61 on the inner side of the hub sleeve 60 are pushed away from the outer peripheral teeth 46 of the synchronizer ring 42, and the outer peripheral teeth 36 of the gear piece 32 and the inner peripheral teeth 61 of the hub sleeve 60 are smoothly engaged. Further, when the synchronization is completed, no pressing force is generated on the synchronizer ring 42. Therefore, the synchronizer ring 42 returns to the position before the synchronization, and the cone portion 44 of the synchronizer ring 42 has a large first inclination angle θ1. In contact with the first inclined surface 134.

  In the operation of the synchronizer ring 42, the cone torque (friction force) Tc for rotating the synchronizer ring 42, the friction coefficient between the cone portion 44 of the synchronizer ring 42 and the cone portion 34 of the gear 22 are μ, and the cone portion. The inner diameter (cone diameter) of the contact portion between 44 and the cone portion 34 is Rc, the angle (cone angle) of the contact portion between the cone portion 44 and the cone portion 34 is θ, and the pressing force between the cone portion 44 and the cone portion 34 is Assuming F, the following relational expression holds.

Tc = μRcF / sin θ
In order to increase the cone torque Tc, the cone angle θ may be decreased. However, when the friction coefficient μ is larger than tan θ, biting occurs.

  Therefore, in the present invention, the first inclination angle θ1 and the second inclination angle θ2 are made as two types of cone angles on the cone portion 34 side. By changing the contact portion between when the chamfer part of the synchronizer ring 42 is pressed and when it is opened, the contact cone angle after synchronization can be changed. If the first inclination angle θ1 is set so that the friction coefficient μ is smaller than tan θ on the first inclined surface 134 as the contact portion, the cone angle can be reduced without this restriction during synchronization.

  That is, the synchronization device according to the present invention can rotate around the rotation shaft 13 with respect to the hub sleeve 60 as the first rotation member that can rotate around the rotation shaft 13 and the hub sleeve 60. A gear 22 as a possible second rotating member, and a synchronizer ring 42 as a synchronizing member that is interposed between the gear 22 and the hub sleeve 60 and can synchronize the gear 22 and the hub sleeve 60 are provided. The gear 22 includes a first inclined surface 134 having a first inclination angle θ <b> 1 with respect to the rotation shaft 13, and a second inclined surface 234 having a second inclination angle θ <b> 2 smaller than the first inclined surface 134. The synchronizer ring 42 contacts the first inclined surface 134 before and after the synchronization operation, and the synchronizer ring 42 contacts the second inclined surface 234 during the synchronization operation.

  Furthermore, when the friction coefficient between the synchronizer ring 42 and the first and second inclined surfaces 134 and 234 is μ, the first inclination angle θ1 and the friction coefficient μ satisfy the relationship expressed by μ <tan θ1.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is sectional drawing of the manual transmission according to embodiment of this invention. It is a perspective view of the synchronizer ring in FIG. It is sectional drawing of the manual transmission in synchronous operation. It is sectional drawing of the manual transmission at the time of completion | finish of synchronous operation | movement.

Explanation of symbols

  10 Shaft, 13 Rotating shaft, 22 Gear, 32 Gear piece, 33, 34 Cone, 36 Outer teeth, 42 Synchronizer ring, 60 Hub sleeve, 61 Inner teeth, 62 Recess, 134 First inclined surface, 234 Second inclined surface.

Claims (3)

A first rotating member capable of rotating about a rotation axis;
A second rotating member capable of rotating about the rotation axis with respect to the first rotating member;
A synchronization member that is interposed between the first rotation member and the second rotation member and capable of synchronizing the first rotation member and the second rotation member;
The first rotating member has a first inclined surface having a first inclination angle θ1 with respect to the rotation axis, and a second inclined surface having a second inclination angle θ2 smaller than the first inclined surface,
The synchronization device, wherein the synchronization member contacts the first inclined surface before and after the synchronization operation, and the synchronization member contacts the second inclined surface during the synchronization operation.   The friction coefficient between the synchronization member and the first and second inclined surfaces is μ, and the first inclination angle θ1 and the friction coefficient μ satisfy a relationship represented by μ <tan θ1. Synchronizer.   A transmission comprising the synchronization device according to claim 1.

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