JPH0763230A - Synchro-mechanism for transmission - Google Patents

Abstract

PURPOSE:To improve a shift feeling by providing a chamfer part on an outer peripheral part having a diameter same as that of the clutch gear of the synchro-cone of a Warner type synchro-mechanism, and moreover providing play in a rotation direction on the joint part between the synchro-cone and the clutch gear. CONSTITUTION:A chamfer part 71 is provided on an outer peripheral part having a diameter same as that of the clutch gear 8 of a Warner type synchro- mechanism, and also play in a rotation direction is provided on the joint part between a synchro-cone 7 and the clutch gear 8. In this constitution, the spline 81 of the clutch gear 8 and the chamfer 71 are on a straight line when the synchro-cone 7 is at a position biased to the rotation direction side in the space of the play. Consequently a coupling sleeve 4 contacts the chamfer part 71 before engaging with the clutch gear 8, and at that time, the synchro-cone 7 is at the position biased opposite to the rotation direction in the space of the play, therefore the synchro-cone 7 and the coupling sleeve 4 are relatively rotated in the space of the play, generating few shock force. As a result, a shift feeling can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a synchronizing mechanism for a transmission.

[0002]

2. Description of the Related Art As a conventional transmission synchronizing mechanism,
The one described in the official gazette of Japanese Utility Model Laid-Open No. 5-136822 is known.

This is provided with an output shaft, two gears for shifting which are provided on the same output shaft at intervals in the axial direction, and a gear which is provided on the side of the gear for shifting and is integrated with each gear for shifting. The clutch gear that rotates in the direction described above and the synchro hub that is provided between the clutch gears and that is coupled to the output shaft, and that is spline-coupled to the synchro hub and that is displaced in the axial direction during a gear shifting operation to shift in the displacement direction. A coupling sleeve for coupling a gear to the output shaft via the clutch gear, and a synchronization means provided between the clutch gear and the coupling sleeve are provided. The synchronizing means includes an inner balk ring having a cone surface on the outer circumference, an outer balk ring concentric with the cone surface and having a cone surface on the inner circumference, and fixed to the clutch gear. And a synchro cone located between the outer balk ring and the outer balk ring.

When the shift is started, the coupling sleeve is slid toward the shift gear on the synchro hub by a shift fork that engages with a circumferential groove formed on the outer peripheral surface of the coupling sleeve to start synchronization. . First, the chamfer part at the tip of the spline part provided on the inner circumference of the coupling sleeve meshes with the chamfer part provided on the outer circumference of the outer balk ring, and the outer balk ring is pressed against the cone part to form a clutch gear. Synchronous torque is generated, and the rotation of the coupling sleeve and the synchronizing gear is completely synchronized through the balk ring. Then, the chamfer portion of the coupling sleeve slips through the balk ring and meshes with the chamfer portion at the tip of the spline portion provided on the outer periphery of the clutch gear, and the coupling sleeve moves toward the speed change gear side, and the spline portion of the sleeve is engaged. By being fitted over the synchro hub and the gear spline portion of the synchronizing gear, the gear is coupled to the output shaft via the gear for shifting, the coupling sleeve and the synchro hub, and the gear shifting is completed.

[0005]

However, in the conventional synchronizing mechanism as described above, when the synchronization is completed and the coupling sleeve slips through the balk ring, the balk ring is not pressed against the cone portion. The clutch gear is allowed to rotate freely, the rotation speed of the clutch gear starts to decrease, and before the coupling sleeve and the clutch gear mesh with each other, relative rotation occurs between them and synchronization is lost. Since the chamfer of the coupling sleeve and the chamfer of the clutch gear mesh with each other in a state where the synchronization is lost, an impact force is generated not only in the rotation direction but also in the axial direction. Therefore, there is a problem that the reaction force is transmitted to the driver's hand during meshing, which deteriorates the shift feeling.

[0006]

In order to solve the above-mentioned problems, in a synchro mechanism of a transmission according to the present invention, a speed change gear provided coaxially with an output shaft and a clutch fixed to a side surface of the speed change gear. A gear, a synchro cone provided on a side surface of the clutch gear on the side opposite to the speed change gear, and a clutch gear that is provided coaxially with the output shaft and rotates integrally with the output shaft and moves in the axial direction. A coupling sleeve fitted between the coupling sleeve and the clutch gear, which is coaxial with the output shaft and frictionally contacts the synchro cone to synchronize the coupling sleeve with the clutch gear. In the warner type synchronizing mechanism having the above, a chamfer portion is provided on an outer peripheral portion having the same diameter as the clutch gear of the synchronizing cone, and There is play in the rotational direction at the joint between the gear and the clutch gear, and when the synchro cone is in a relative position deviated in the rotational direction between the play, the spline of the clutch gear and the chamfer part of the synchro cone are directly aligned. The structure is lined up.

[0007]

According to the above construction, the coupling sleeve contacts the chamfer of the synchro-cone before engaging with the clutch gear, and at this time, the synchro-cone is located in the relative position deviated between the play and the direction opposite to the rotational direction. Therefore, since the synchro cone and the coupling sleeve relatively rotate between the play, a large impact force is not generated. During the relative rotation between the play, the chamfer portion of the synchro cone meshes with the spline of the coupling sleeve, and a large impact force is generated when the relative rotation of the play is finished. However, at this time, since the chamfer portion of the synchro cone is on the side surface of the spline of the coupling sleeve, the impact occurs only in the rotation direction, and the impact force in the axial direction does not occur. Further, at this time, since the spline of the clutch gear and the chamfer portion of the synchro cone are aligned, the clutch gear and the coupling sleeve can be fitted smoothly.

[0008]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 shows a first embodiment of the present invention, and FIG. 2 shows a second embodiment of the present invention. FIG. 3 is an explanatory diagram of this embodiment. FIG. 4 is a sectional view showing the relationship between the clutch gear and the synchro cone.

First, the configuration of the first embodiment will be described. The synchro hub 2 connected to the output shaft 1 is provided with splines and three notches on the outer circumference. The coupling sleeve 4 has a circumferential groove on the outer circumference and a spline 41 on the inner circumference.
Is provided and is spline-fitted with the synchro hub 2, and is movable in the axial direction. The three insert springs 3 are mounted on the splines 41 of the coupling sleeve 4 and are respectively housed in the three cutout portions of the synchronizing hub 2. A first speed transmission gear 10 and a second speed transmission gear 9 are provided coaxially with the output shaft 1 on both sides of the synchro hub 2 with a space therebetween.

Although a synchronizing mechanism is provided between the synchronizing hub 2 and each transmission gear, the present invention is applied to the second-speed transmission gear 9 side. The description of the first speed transmission gear 10 side is omitted.

A clutch gear 8 is coupled to a side surface of the second speed transmission gear 9 on the synchro hub 2 side. A spline 81 is provided on the outer periphery of the clutch gear 8 and a chamfer is provided at the tip of the spline 81 on the synchro hub 2 side. Section is provided. An inner balk ring 6 is provided coaxially with the output shaft 1 between the clutch gear 8 and the synchronizing hub 2. The inner surface of the inner balk ring 6 is provided with a cone surface having a large diameter on the clutch gear 8 side. An outer balk ring 5 is provided coaxially with the inner balk ring 6. The outer balk ring 5 has a cone surface on the inner circumference, a spline 51 on the outer circumference, and a chamfer portion at the tip of the spline 51 on the synchro hub side. The outer balk ring 5 is engaged with the inner balk ring 6. A synchro cone 7 is provided coaxially with the inner balk ring 6 and between the outer balk ring 5 and the clutch gear 8. The outer peripheral portion of the synchro cone 7 on the clutch gear 8 side has the same diameter as the clutch gear, and the chamfer portion 71 is provided on this outer peripheral portion.
Further, a cone portion located between the cone surface of the outer balk ring 5 and the cone surface of the inner balk ring 6 is provided on the synchro hub 2 side. The synchro cone 7 and the clutch gear 8 are fitted with a rattle 72 provided in the synchro cone 7 and a hole 82 provided in the clutch gear 8 with a play of half the width of the spline in the rotational direction. I am fit. When the synchro cone 7 is in a relative position deviated from the play with the clutch gear 8 toward the rotation direction side, the side surface of the spline 81 of the clutch gear 8 and the chamfer portion 71 of the synchro cone 7 opposite to the rotation direction are It is configured to line up in a straight line.

The operation of the first embodiment will be described below.

While the vehicle is traveling at the first speed, the clutch gear 8 rotates at a higher rotational speed than the rotational speed of the coupling sleeve 4, as shown in FIG. When the driver operates the shift lever from the first speed to the second speed, the insert spring 3 together with the coupling sleeve 4 is moved to the second speed transmission gear 9 side. Here, the insert spring 3 contacts the outer balk ring 5 and presses the outer balk ring 5 toward the second speed transmission gear 9 side. Then, the cone surface of the outer balk ring 5 comes into contact with the synchro cone 7, and pushes the synchro cone 7 toward the clutch gear 8. Here, the cone surface of the inner baud ring 6 and the synchro cone 7 come into contact with each other to generate a frictional force. Due to this frictional force, the chamfer portion of the spline 51 of the outer balk ring 5 rotates to a position facing the chamfer portion of the spline 41 of the coupling sleeve 4, and the coupling sleeve 4 further presses the insert spring 3 and contracts the clutch gear 8 side. To the outer balk ring 5 facing the chamfer part of the coupling sleeve 4 as shown in FIG. 3 (B).
Contact with the chamfer part. In this way, the operation force is transmitted to the balk ring, frictional force is generated on both the upper and lower surfaces of the synchro cone 7, and synchronization is performed. Then, the difference in rotational speed between the synchro cone 7 and the outer balk ring 5 gradually disappears. Therefore, there is no difference in rotational speed between the coupling sleeve 4 and the clutch gear 8. Coupling sleeve 4
When the coupling sleeve 4 is further pushed toward the clutch gear 8 in a state where there is no difference in rotational speed between the clutch gear 8 and the clutch gear 8, the chamfer surface of the spline 41 of the coupling sleeve 4 becomes the chamfer surface of the spline 51 of the outer balk ring 5. Is moved while sliding, and is fitted with the spline 51 of the outer balk ring 5 as shown in FIG. Here, since the balk ring is not pushed to the clutch gear 8 side, the balk ring is not pushed to the clutch gear 8 side.
Since no force is transmitted to the clutch gear 8, the rotation speed on the clutch gear 8 side starts to decrease. At this time, since the synchro cone 7 is rotated by receiving the force from the clutch gear 8, the synchro cone 7 is loosened between the synchro cone 7 and the clutch gear 8 as shown in FIGS. 3 (C) and 4 (A). , The relative position is biased to the side opposite to the rotation direction. When the coupling sleeve 4 is further pushed toward the clutch gear 8, the chamfer surface of the spline 41 of the coupling sleeve 4 and the chamfer portion 71 of the synchro cone 7 come into contact with each other as shown in FIG. When the coupling sleeve 4 is further pushed to the clutch gear 8 side in this state, FIG. 3 (E) and FIG. 4 (B)
As shown in FIG. 5, the synchro cone 7 relatively rotates in the rotational direction by the amount of the backlash with the clutch gear 8, and the synchro cone 7
Is in a relative position deviated to the rotational direction side with respect to the play with the clutch gear 8, and the side surfaces of the spline 81 of the clutch gear 8 and the chamfer portion 71 of the synchro cone 7 are aligned. During this period, the chamfer portion of the synchro cone 7 and the chamfer portion of the spline 41 of the coupling sleeve 4 are fitted.

Here, since the force is not transmitted from the coupling sleeve 4 to the clutch gear 8 while the synchro cone 7 is rotating relative to the clutch gear 8 by the amount of backlash,
When the coupling sleeve 4 and the chamfer 71 of the synchro cone 7 come into contact with each other, a large impact force is not generated.

When the synchro cone 7 has finished rotating relative to the clutch gear 8 by the amount of backlash, and is in the relative position deviated in the direction of rotation as shown in FIG. 4 (B), the clutch is disengaged from the coupling sleeve 4. The force is transmitted to the gear 8,
At this time, a large impact force is generated. However,
At this time, since the chamfer portion 71 of the synchro cone 7 is in contact with the side surface of the spline 41 of the coupling sleeve 4, the impact force is generated only in the rotation direction and is not generated in the axial direction. In this state, the synchro cone 7 and the spline 81 of the clutch gear 8 are aligned with each other. Therefore, when the coupling sleeve 4 is further pushed toward the clutch gear 8, the spline 41 of the coupling sleeve 4 is pushed.
Smoothly fits with the spline 81 of the clutch gear 8,
Gear shifting ends.

As described above, since it is possible to suppress the generation of the impact force in the axial direction during the meshing, it is possible to suppress the reaction force to the driver's hand.

In the above-mentioned embodiment, the double cone type synchronizing mechanism having two balk rings of the inner balk ring and the outer balk ring has been described, but the present invention is not limited to this, and the second embodiment is not limited to this. As described above, by configuring the clutch gear and the synchro cone separately, the present invention can be applied to a single cone type synchro mechanism.

[0018]

As described above, according to the synchro mechanism of the transmission according to the present invention, the shifting gear provided coaxially with the output shaft, the clutch gear fixed to the side surface of the shifting gear, A synchro-cone provided on a side surface of the clutch gear opposite to the speed change gear, and an eccentric cone provided coaxially with the output shaft to rotate integrally with the output shaft and move in the axial direction to engage with the clutch gear. Warner type having a coupling sleeve and a balk ring provided coaxially with the output shaft between the coupling sleeve and the clutch gear to frictionally contact a synchro cone to synchronize the coupling sleeve and the clutch gear In the synchro mechanism, a chamfer portion is provided on the outer peripheral portion having the same diameter as the clutch gear of the synchro cone, and the synchro cone and the clutch are further provided. Since there is play in the rotation direction at the joint with the gear and the spline of the clutch gear and the chamfer of the synch cone are in a straight line when the synch cone is in a relative position where the play is biased in the direction of rotation. Before the coupling sleeve engages with the clutch gear, it contacts the chamfer of the synchro cone.At this time, the synchro cone is located in the relative position deviating from the rotation direction to the side opposite to the rotation direction, so the synchro cone and the cup Since the ring sleeve rotates relative to the backlash, a large impact force is not generated. During the relative rotation between the play, the chamfer portion of the synchro cone meshes with the spline of the coupling sleeve, and a large impact force is generated when the relative rotation between the play ends. However, at this time, since the chamfer part of the synchro cone is on the side surface of the spline of the coupling sleeve, the impact occurs only in the rotation direction,
Since no impact force is generated in the axial direction, the reaction force transmitted to the driver's hand is reduced. Further, at this time, since the spline of the clutch gear and the chamfer portion of the synchro cone are aligned, the clutch gear and the coupling sleeve can be fitted smoothly.

Therefore, there is an effect that the shift feeling can be improved.

[Brief description of drawings]

FIG. 1 is a first embodiment of the present invention.

FIG. 2 is a second embodiment of the present invention.

FIG. 3 is an explanatory diagram of this embodiment.

FIG. 4 is a sectional view showing a relationship between a clutch gear and a synchro cone according to the present embodiment.

[Explanation of symbols]

1 ... Output shaft, 2 ... Synchro hub, 3 ... Insert spring, 4 ... Coupling sleeve, 5 ... Outer balk ring, 6 ... Inner balk ring, 7 ... Synchro cone, 8 ... Clutch gear, 9 ... Second speed gear, 10 ... First speed transmission gear 41 ... Spline, 51 ... Spline 71 ... Chamfer part, 72 ... Claw part 81 ... Spline, 82 ... Hole part

Claims (1)

[Claims] 1. A shift gear provided coaxially with an output shaft, a clutch gear fixed to a side surface of the shift gear, and a synchro provided on a side surface of the clutch gear opposite to the shift gear. A cone, a coupling sleeve which is provided coaxially with the output shaft, rotates integrally with the output shaft, moves axially and fits with the clutch gear, and between the coupling sleeve and the clutch gear, A warner type synchronizing mechanism provided coaxially with an output shaft and having a balk ring for frictionally contacting the synchro cone and synchronizing the coupling sleeve and the clutch gear, the outer peripheral portion having the same diameter as the clutch gear of the synchro cone. A chamfer portion is provided in the synchro cone, and a play in the rotation direction is provided in the connecting portion between the synchro cone and the clutch gear. When there between backlash relative position offset in the rotational direction, synchronizing mechanism of a transmission chamfer portion of the spline and synchro cone clutch gear, characterized in that arranged on a straight line.