JP6750166B2 - Automatic transmission - Google Patents

Description

The present invention relates to an automatic transmission capable of shifting without interruption of torque transmission.

Patent Document 1 discloses an automatic transmission capable of shifting without interruption of torque transmission (hereinafter referred to as seamless shift). For example, when an upshift to the second speed is performed while traveling at the first speed, when the second speed clutch ring that meshes with the second speed gear is engaged, a coasting torque acts on the first speed gear. By utilizing this coasting torque, an axial force in the disengagement direction is generated in the clutch ring for the first speed, and a seamless shift to the second speed is achieved. When achieving a seamless shift, a shift drum having a shift groove that engages with a shift fork on the outer periphery is rotated by a motor to shift gears.

JP 2012-127471 A

However, when the shift fork is operated and the second speed clutch ring is engaged, there is a problem that the driver feels uncomfortable due to the hitting sound and shift shock when the dog is engaged.
An object of the present invention is to provide an automatic transmission capable of suppressing hammering noise and shift shock when performing seamless shift.

To achieve the above object, in an automatic transmission according to the present invention, a first low speed gear and a first high speed gear fixedly or relatively rotatably supported by a first shaft and a second shaft fixedly or relatively rotatably supported by a second shaft. The second low-speed gear that constantly meshes with the first low-speed gear and the second high-speed gear that constantly meshes with the first high-speed gear and the second high-speed gear that achieves a high-speed gear; A low speed clutch ring dog that meshes with a dog of the low speed side relative rotating body that is either the low speed gear or the second low speed gear, and when torque acts from the dog of the low speed side relative rotating body to the low speed clutch ring dog, A first projection for a guide that is movable toward an axial disengagement side along a groove formed on the outer periphery of a first clutch ring cam fixedly installed on the first shaft or the second shaft and intersecting the axial direction. And a high speed clutch ring dog that meshes with the dog of the high speed side relative rotating body that is either the first low speed gear or the second high speed gear by moving toward the meshing side in the axial direction. When a torque acts on the high speed clutch ring dog from the dog of the high speed side relative rotating body, it intersects with the axial direction formed on the outer periphery of the second clutch ring cam fixedly installed on the first shaft or the second shaft. A high speed clutch ring having a guide second protrusion that is movable in the axial disengagement side along the groove, and the low speed clutch ring and the high speed clutch ring are axially meshed by moving to the axial meshing side. A shift actuator that is movable in the axial direction and allows movement to the axial meshing release side, and when the shift actuator moves the high speed clutch ring in the axial meshing direction to perform an upshift, When the rotation speed of the first shaft is equal to or higher than a predetermined rotation speed, the shaft required to move the first guide projections along the groove to the axial disengagement position by the inertia torque of the low speed clutch ring dog. The direction movement time is longer than the rotation direction movement time for moving the backlash between the dog of the low speed side relative rotating body and the low speed clutch ring dog by the relative speed of the dog of the low speed side relative rotating body and the clutch ring dog. Characterized by being short.

Therefore, the hitting sound can be suppressed during the upshift by the seamless shift.

1 is a schematic system diagram showing an automatic transmission according to a first embodiment. FIG. 3 is a perspective view showing a first clutch ring cam of the first embodiment. FIG. 3 is a perspective view showing a first clutch ring of the first embodiment. FIG. 3 is a schematic diagram showing an operation of a first dog clutch mechanism during an upshift from first speed to second speed in the automatic transmission according to the first embodiment. FIG. 5 is an enlarged partial cross-sectional view showing the action of the first dog clutch mechanism during an upshift from first speed to second speed in the automatic transmission according to the first embodiment.

[Example 1]
FIG. 1 is a schematic system diagram showing an automatic transmission according to a first embodiment. An automatic transmission 3 is connected to an engine output shaft 1a of the engine 1 via a clutch 2. The automatic transmission 3 has a first shaft 301 connected to the automatic transmission side of the clutch 2 and a second shaft 302 arranged in parallel with the first shaft 301. The first shaft 301 includes a first speed drive gear 311, a second speed drive gear 321, and a third speed drive gear 331 that are rotatably supported with respect to the first shaft 301. The second shaft 302 includes a first speed driven gear 312, which is fixed to the second shaft 302 and rotates integrally with the second shaft 302, a second speed driven gear 322, and a third speed driven gear 332. Each driven gear always meshes with each drive gear.

The transmission controller 3a determines a desired shift stage from a shift map described later based on various sensors and shift signals (not shown), and outputs a shift actuator drive signal to the shift actuator 30. The shift actuator 30 is configured to move the first shift fork 31 and the second shift fork 32 in the axial direction. The shift actuator 30 position-controls a shift drum 30a having a shift groove 30b engaging with the shift forks 31 and 32 on the outer circumference by a motor 30c. The first shift fork 31, the second shift fork 32, and the third shift fork 33 have positioning mechanisms 31b, 32b, and 33b that can be biased to predetermined axial positions. After the shift forks 31, 32, 33 are positioned by the shift actuator 30, the positioning mechanisms 31b, 32b, 33b slightly move in the axial direction in accordance with the change in the dog meshing position with the torque acting direction, which will be described later. Is allowed, and a holding force at a predetermined axial position is applied to each shift fork 31, 32, 33 at a plurality of positions. Details will be described later.

A first dog 311a that extends in the axial direction is provided on the side surface of the first speed drive gear 311. The first dog 311a includes a drive side engagement surface 311a2 that meshes with the first clutch ring dog 34c when the driving torque acts, a coast side engagement surface 311a3 that engages the first clutch ring dog 34c when the coasting torque acts, and And an end surface 311a1 parallel to the axis orthogonal direction facing the one-clutch ring dog 34c. The side surface of the second drive gear 321 has a second dog 321a extending in the axial direction. The second dog 321a includes a drive side engagement surface 321a2 that meshes with the second clutch ring dog 35c when the driving torque acts, a coast side engagement surface 321a3 that engages the second clutch ring dog 35c when the coasting torque acts, and And an end surface 321a1 facing the two-clutch ring dog 35c and parallel to the axis orthogonal direction. A side surface of the third drive gear 331 has a third dog 331a extending in the axial direction. The third dog 331a includes a drive side engagement surface 331a2 that meshes with the third clutch ring dog 36c when the driving torque acts, a coast side engagement surface 331a3 that engages the third clutch ring dog 36c when the coasting torque acts, and And an end surface 331a1 facing the three-clutch ring dog 36c and parallel to the axis orthogonal direction.

A first dog clutch mechanism DG1, a second dog clutch mechanism DG2 and a third dog clutch mechanism DG3 are provided at positions adjacent to the first speed drive gear 311, the second speed drive gear 321 and the third speed drive gear 331. The first dog clutch mechanism DG1 is installed on the first clutch ring cam 400 fixedly installed on the first shaft 301 and on the outer circumference of the first clutch ring cam 400, and meshes with the first shift fork 31 so as to be rotatable relative thereto. It has a first clutch ring 34. FIG. 2 is a perspective view showing the first clutch ring cam of the first embodiment. On the outer circumference of the first clutch ring cam 400, there is a V-shaped groove 401 formed on the outer peripheral surface. The V-shaped groove 401 has a first-speed-side lower inclined surface 401a inclined toward the forward rotation direction side of the first shaft 301 and a first-speed-side upper inclined surface 401e facing the first-speed-side lower inclined surface 401a. Have.

The upper end of the V-shaped groove adjacent to the first-speed-side upper inclined surface 401e is the neutral position 401f in a state in which it does not mesh with the first-speed drive gear 311. The one protrusion 33b is held at the neutral position 401f which is the tip of the V-shaped groove. Further, the first-speed-side downward inclined surface 401a has an angle θ intersecting the axial direction (see FIG. 5). An end portion of the first clutch ring cam 400 facing the first speed drive gear 311 side has a holding surface 401b connected to the first speed side downward inclined surface 401a and parallel to the axial direction. The second dog clutch mechanism DG2 and the third dog clutch mechanism DG3 have the same second and third clutch rings 35, 36, second and third clutch ring cams 500, 600, and V-shape as the first dog clutch mechanism DG1. Grooves 501, 601, lower inclined surfaces 501a, 601a on the second speed and third speed sides, and holding surfaces 501b, 601b are provided. Since the configuration is the same as that of the first dog clutch mechanism DG1, the description is omitted.

FIG. 3 is a perspective view showing the first clutch ring of the first embodiment. The first clutch ring 34 includes a cylindrical member 34e that can move relative to the outer periphery of the first clutch ring cam 400, and a first sleeve 34a that is expanded from the axial center of the cylindrical member 34e toward the outer diameter side. Have. The first sleeve 34a is a disk-shaped member that is capable of relatively axially holding the shift fork 31 and applying an axial force to the shift fork 31. The first clutch ring 34 projects from the first sleeve 34a toward the inner peripheral side of the cylindrical member 34e and the first clutch ring dog 34c extending in the axial direction of the side surface facing the first speed drive gear 311. And a first guide protrusion 34b guided in the V-shaped groove 401 of the clutch ring cam 400. The first clutch ring dog 34c includes an inclined surface 34c1 that lifts in the direction away from the first speed drive gear 311 when the driving torque acts, a drive side engagement surface 34c2 that meshes with the first dog 311a when the driving torque acts, and a coasting torque. It has a coast side engagement surface 34c3 that meshes with the first dog 311a when operating, and an end surface 34c4 that faces the first dog 311a and that is parallel to the axis-perpendicular direction.

The second clutch ring 35 includes a cylindrical member 35e that is movable relative to the outer circumference of the second clutch ring cam 500, and a second sleeve 35a that is expanded from the axial center of the cylindrical member 35e toward the outer diameter side. Have. The second sleeve 35a is a disk-shaped member that is relatively rotatably held by the shift fork 32 and can apply axial force to the shift fork 32. The second clutch ring 35 projects from the second sleeve 35a to the second clutch ring dog 35c that extends in the axial direction on the side surface facing the second speed drive gear 321, and projects toward the inner peripheral side of the cylindrical member 35e. The second guide projection 35b is guided in the V-shaped groove 501 of the clutch ring cam 500.
The third clutch ring 36 includes a cylindrical member 36e that can move relative to the outer circumference of the third clutch ring cam 600, and a third sleeve 36a that is expanded from the axial center of the cylindrical member 36e toward the outer diameter side. Have. The third sleeve 36a is a disk-shaped member that is relatively rotatably held by the shift fork 33 and is capable of mutually applying an axial force to the shift fork 33. The third clutch ring 36 has a third clutch ring dog 36c extending from the third sleeve 36a in the axial direction on the side surface facing the third speed drive gear 331, and an inner peripheral side of the cylindrical member 36e. And a third guide projection 36b guided in the V-shaped groove 601 of the clutch ring cam 600. The second clutch ring dog 35c and the third clutch ring dog 36c each have an inclined surface, a drive side engagement surface, a coast side engagement surface, and an end surface, like the first clutch ring dog 34c.

Next, the upshift action will be briefly described. As a specific example, a case where an upshift to the second speed is performed in the first speed running state will be described. 4 and 5 are schematic diagrams showing the operation of the first dog clutch mechanism in the upshift from the first speed to the second speed in the automatic transmission according to the first embodiment. In the first speed, the first shift fork 31 is in a state of moving to the left side in FIG. As shown in FIG. 2A, in the state before the torque acts on the first speed drive gear 311, the first guide ring 34b of the first clutch ring 34 is positioned on the holding surface 401b, and the coasting torque is It does not move in the axial direction even if it acts. Further, the second guide projection 35b is located at the neutral position 501f in the V-shaped groove 501 of the second clutch ring cam 500, and when the second clutch ring cam 500 rotates, the guide second protrusion 35b abuts on the neutral position 501f. This is a state in which the second clutch ring 35 is being rotated through the two protrusions 35b.

As shown in FIG. 4( b ), at the tooth surface of the first clutch ring dog 34 c of the first clutch ring 34 and at the position where it engages with the first dog 311 a of the first speed drive gear 311 when the driving torque acts. The inclined surface 34c1 is formed. When the driving torque acts from the first speed drive gear 311 to the first speed driven gear 312, the first clutch ring 34 lifts along the inclined surface 34c1 toward the disengagement side. As a result, the first guide projection 34b moves from the holding surface 401b to the position of the first-speed side upper inclined surface 401e. However, the first dog 311a of the first speed drive gear 311 and the first speed clutch ring dog 34c continue to be meshed with each other, and the torque transmission state is established. In performing this operation, the above-mentioned positioning mechanism 31b operates. That is, while allowing the first shift fork 31 to slightly move in the axial direction with the lift, the axial position of the first clutch ring 34 after the lift is stably held.

Next, when the second shift fork 32 moves to the left side in FIG. 1 and the second clutch ring dog 35c and the second dog 321a start to engage with each other, the interlock state is established, and the first speed clutch ring dog 34c A coasting torque acts on the first dog 311a. Then, as shown in FIG. 5, the first guide protrusion 34b moves along the first-speed-side downward inclined surface 401a. Since the force generated in the axial direction by the coasting torque associated with the interlock state is sufficiently larger than the holding force of the positioning mechanism 31b, the first shift fork 31 moves quickly.

Then, the first guide projection 34b moves on the first-speed-side downward inclined surface 401a, and the axial tip of the first dog 311a of the first-speed drive gear 11 and the axial tip of the first-speed clutch ring dog 34c. When the predetermined axial position is exceeded, the first guide protrusion 34b moves along the first-speed-side downward inclined surface 401a to move the first-speed clutch ring dog 34c to the axial-release side. As a result, the first clutch ring 34 moves to the disengagement side, and the engagement between the first dog 311a of the first speed drive gear 11 and the first speed clutch ring dog 34c is completely released.

That is, the first speed drive gear 311 and the first speed drive gear 311 are engaged with each other by engaging the second speed drive gear 321 and the second clutch ring dog 35c at the time of the first speed, and utilizing the coasting torque associated with the interlocking state generated by the engagement. The engagement with the clutch ring 34 is released. Therefore, the torque transmission state can always be maintained during the upshift. Such a shift operation is called a seamless shift.

Here, the problem when the engagement between the first dog 311a and the first clutch ring dog 34c is released will be described. When the rotational speed of the first shaft 301 during upshift is V1 and the gear ratio of the first speed is G1, the rotational speed of the second shaft 302 is represented by V1·G1. When the second clutch ring dog 35c and the second dog 321a are engaged in this state, the rotation speed of the second shaft 302 does not change significantly, so that when the gear ratio of the second speed is G2, The rotation speed is V1·(G1/G2) (hereinafter, this speed is referred to as V2).

As described above, when the coasting torque acts on the upshift and the rotation speed of the first shaft 301 is reduced from V1 to V2, the first speed clutch ring dog 34c shown in the state (I) of FIG. The drive side engagement surface 311a2 and the drive side engagement surface 34c2 are separated from the state in which the torque is transmitted to the first dog 311a. Then, as shown in the state (V) of FIG. 5, the coast side engagement surface 311a3 and the coast side engagement surface 34c3 collide with each other. After this collision, the first speed clutch ring dog 34c is pushed downward in FIG. 5, the first guide projection 34b moves in the axial direction along the first speed side downward inclined surface 401a, and the first shift fork 31 moves. It moves in the axial direction and the engaged state of the first speed is released. However, there has been a problem that the above-mentioned collision deteriorates the sound vibration performance and durability.

Therefore, in the first embodiment, by utilizing the inertia torque of the first clutch ring dog 34c, the first clutch ring dog 34c is axially moved before the coast side engagement surface 34c3 and the coast side engagement surface 311a3 collide. Decided to move to. That is, since the first clutch ring cam 400 rotates integrally with the first shaft 301, the first clutch ring cam 400 is decelerated from V1 to V2 with an upshift. At this time, the first clutch ring 34 abuts on the first-speed side downward inclined surface 401a of the first clutch ring cam 400 while being V1 by the inertial force, and moves in the axial direction along the first-speed side downward inclined surface 401a. The time required for this axial movement is Tst (hereinafter also referred to as the axial movement time Tst). The axial movement time Tst is determined according to various parameters such as the inertia I1 of the first clutch ring 34, the rotational angular velocity ω, the angle θ of the first-speed side downward inclined surface 401a, and the set load of the positioning mechanism 31b. ..

On the other hand, when the circumferential length from the coast side engagement surface 34c3 to the coast side engagement surface 311a3 when the driving torque is applied is R1 (hereinafter, also referred to as backlash R1), the first speed drive gear 311 is also V1. Since the speed is reduced from V2 to V2, the relative speed between the first speed drive gear 311 and the first clutch ring 34 becomes (V1-V2), and the time for moving R1 at this relative speed is Tbr (hereinafter, rotational direction moving time Tbr). Is also described.)
Tbr=R1/(V1-V2).

At this time, if the relationship of Tbr>Tst is obtained, the first clutch ring dog 34c can be moved to the axial disengagement position before the coast side engagement surface 34c3 and the coast side engagement surface 311a3 collide. The states (II) and (III) in FIG. 5). Therefore, when upshifting by crossing the upshift line from the 1st speed to the 2nd speed set in the shift map, various parameters are set so as to obtain the above relationship. If the rotation speed of the first shaft 301 is equal to or higher than a predetermined rotation speed, the setting can be made so that the relationship of Tbr>Tst is obtained, so that it is possible to cope with the manual shift.

Next, during the upshift from the 2nd speed to the 3rd speed, the first shaft 301 is upshifted at a relatively low speed as compared with the upshift from the 1st speed to the 2nd speed. Therefore, the various parameters set for the second speed are different from the various parameters set for the first speed. Specifically, the angle θ of the second-speed side downward inclined surface 501a is made larger than the angle θ of the first-speed side downward inclined surface 401a. Accordingly, by increasing the axial movement speed of the first clutch ring 34, it is possible to effectively promote the axial movement even at a low rotation speed.

The backlash R1 for the second speed is smaller than the backlash R1 for the first speed. That is, when upshifting at low rotation speed, it is easy to secure Tbr.

Further, the set load of the second speed positioning mechanism 32b is set lower than the set load of the first speed positioning mechanism 31b. That is, when the rotation speed is low, the inertia torque is small, and therefore, if the set load is large, it is difficult to obtain the force required for the axial movement.

Further, the inertia I2 of the second clutch ring 35 is made larger than the inertia I1 of the first clutch ring 34. Specifically, by increasing the diameter and increasing the mass by changing the wall thickness and changing the material, it is possible to secure sufficient inertia torque even at low speed.

Further, the gear ratio between the first speed and the second gear is made larger than the gear ratio between the second speed and the third gear. That is, since the relative speed between the drive gear and the clutch ring is determined by the inter-step ratio, Tbr can be lengthened by increasing the relative speed in the upshift on the high speed side.

The operation and effect based on the first embodiment will be described.
(1) A first speed drive gear 311 (first low speed gear) and a second speed drive gear 321 (first high speed gear) which are rotatably (fixed or) supported by the first shaft 301,
A first speed driven gear 312 (second low speed gear) fixed to the second shaft 302 (supported so as to be rotatable relative thereto) and constantly meshing with the first speed drive gear 311 to achieve the first speed and a second speed drive gear 321 and constantly meshing with the second speed. Achieved second speed driven gear 322 (second high speed gear),
The first clutch ring dog 34c (low-speed clutch) that meshes with the first dog 311a (the dog of the low-speed side relative rotating body that is either the first low-speed gear or the second low-speed gear) by moving toward the meshing side in the axial direction. When the coasting torque opposite to the driving torque acts on the first clutch ring dog 34c, the axial direction formed on the outer periphery of the first clutch ring cam 400 fixedly installed on the first shaft 301. A first clutch ring 34 (low speed clutch ring) having a first guide projection 34b that is movable toward the axial disengagement side along a V-shaped groove 401 that is a groove that intersects with
The second clutch ring dog 35c (high-speed clutch) that meshes with the second dog 321a (the dog of the high-speed side relative rotating body that is either the first low-speed gear or the second high-speed gear) by moving toward the meshing side in the axial direction. When the coasting torque opposite to the driving torque acts on the second clutch ring dog 35c, the axial direction formed on the outer periphery of the second clutch ring cam 500 fixedly installed on the first shaft 301. A second clutch ring 35 (high-speed clutch ring) having a guide second protrusion 35b that is movable toward the axial disengagement side along a V-shaped groove 501 that is a groove that intersects with
A first shift fork 31, which is capable of moving the first clutch ring 34 and the second clutch ring 35 in the axial meshing direction by the movement to the axial meshing side, and allows the movement to the axial meshing release side, A second shift fork 32 and a shift actuator 30,
Equipped with
The shift actuator 30 moves the second clutch ring 35 in the axial meshing direction to perform an upshift, and when the rotation speed of the first shaft 301 is equal to or higher than a predetermined rotation speed, the inertia lock of the first clutch ring dog 34c. Thus, the axial movement time Tst required to move the first guide projection 34b along the V-shaped groove 401 to the axial meshing disengagement position is determined by the backlash R1 between the first dog 311a and the first clutch ring dog 34c. Is shorter than the rotational direction moving time Tbr for moving by the relative speed between the first dog 311a and the first clutch ring dog 34c.
Therefore, at the time of upshifting by the seamless shift, before the coast side engaging surface 34c3 of the first clutch ring 34 and the coast side engaging surface 311a3 of the first speed drive gear 311 collide, the first clutch ring dog 34c is axially moved. It is possible to move to the non-engagement position, and it is possible to suppress the shift shock while suppressing the hitting sound accompanying the dog meshing.

(2) The third speed drive gear 331 (third high speed gear) rotatably supported by the first shaft 301 and the third speed drive gear 331 fixed to the second shaft 302 are always meshed with the third speed drive gear 331 and the third speed drive gear 331. The third driven gear 332 (fourth high speed gear) that achieves the third speed (second high speed) and the third dog 331a (the third high speed gear or the fourth high speed gear) by moving toward the axial meshing side. Of the second relative rotating body on the second high speed side, which is any one of the above, and has a third clutch ring dog 36c (second high speed clutch ring dog) which is opposite to the driving torque on the third clutch ring dog 36c. When the coasting torque is applied, it moves to the axial disengagement side along the V-shaped groove 600 formed on the outer periphery of the third clutch ring cam 600 fixedly installed on the second shaft 302 and intersecting the axial direction. A third clutch ring 36 (second high speed clutch ring) having a possible third guide projection 36b, and the shift actuator 30 moves the third clutch ring 36 in the axial direction by moving toward the meshing side in the axial direction. It is a shift actuator that is movable in the meshing direction and allows movement to the axial meshing release side. The inclination angle θ of the V-shaped groove 501 of the second clutch ring cam 35 is the V-shaped of the first clutch ring cam 400. It is larger than the inclination angle θ of the groove 401. Therefore, the axial movement speed of the first clutch ring 34 can be increased, and the axial movement of the first clutch ring cam 400 can be effectively promoted even at a low rotation speed.

(3) The backlash between the second dog 321a and the second clutch ring dog 35c is smaller than the backlash between the first dog 311a and the first clutch ring dog 34c. Therefore, even when the rotation speed of the first shaft 301 at the time of upshifting from the second speed to the third speed is low, the rotation direction moving time Tbr can be secured.

(4) The shift actuator 30 has positioning mechanisms 31b and 32b that allow the clutch ring to move toward the axial disengagement side due to the set load of the elastic body, and the set load of the positioning mechanism 35b of the second clutch ring 35 is , Lower than the set load of the positioning mechanism 31b of the first clutch ring. Therefore, even when the rotation speed of the first shaft 301 during the upshift from the second speed to the third speed is low and the inertia torque is small, the axial movement can be achieved.

(5) The inertia I2 of the second clutch ring 35 is larger than the inertia I1 of the first clutch ring 34. Therefore, even if the rotation speed of the first shaft 301 during the upshift from the second speed to the third speed is low, the inertia torque can be secured.

(6) The gear ratio between the first speed and the second gear is larger than the gear ratio between the second gear and the third gear. Therefore, the relative speed at the time of upshifting from the 2nd speed to the 3rd speed can be secured, and the rotation direction moving time Tbr can be secured.

(Other embodiments)
Although the above description is based on the first embodiment, the present invention is not limited to the above embodiment, and the present invention may be applied to an automatic transmission having another configuration. Specifically, the present invention is not limited to the third forward speed, and can be applied to a further multi-speed automatic transmission.
Further, although the V-shaped groove is used in the first embodiment, when the drive gear exists only on one side of the clutch ring, the V-shaped groove does not have to be the V-shaped groove, and the inclined groove on the side where the drive gear does not exist is not provided. May be.

1 engine 1a engine output shaft 2 clutch 3 automatic transmission 3a transmission controller 30 shift actuator 30a shift drum 30c motor 31 first shift fork 32 second shift fork 33 third shift fork 34 first clutch ring 34a first sleeve 34b guide First projection 34c first clutch ring dog 34c1 inclined surface 34c2 drive side engagement surface 34c3 coast side engagement surface 34c4 end surface 34e cylindrical member 35 second clutch ring 35a second sleeve 35b second projection 35c second clutch for guide Ring dog 36c Third clutch Ring dog 301 First shaft 302 Second shaft 311 First speed drive gear 311a First dog 311a1 End surface 311a2 Drive side engagement surface 311a3 Coast side engagement surface 312 First speed driven gear 321 Second speed drive gear 321a Second 2 dog 322 2nd driven gear 400 1st clutch ring cam 401 V-shaped groove 401a 1st speed side downward sloping surface 500 2nd clutch ring cam 501 V-shaped groove 501a 2nd speed side downward sloping surface 600 3rd clutch ring cam 601 V-shaped groove 601a 3rd speed side downward slope DG1 1st dog clutch mechanism DG2 2nd dog clutch mechanism DG3 3rd dog clutch mechanism

Claims (6)

A first low speed gear and a first high speed gear fixedly or relatively rotatably supported on the first shaft;
A second low speed gear that is fixedly or rotatably supported by the second shaft and that constantly meshes with the first low speed gear to achieve a low speed stage; and a second high speed gear that constantly meshes with the first high speed gear to achieve a high speed stage;
It has a low-speed clutch ring dog that meshes with the dog of the low-speed side relative rotating body that is either the first low-speed gear or the second low-speed gear by moving toward the meshing side in the axial direction, and the low-speed clutch ring dog is driven. When a coasting torque on the side opposite to the torque acts, the meshing in the axial direction is performed along a groove formed on the outer periphery of the first clutch ring cam fixedly installed on the first shaft or the second shaft and intersecting the axial direction. A low speed clutch ring having a guide first protrusion that is movable to the release side,
It has a high-speed clutch ring dog that meshes with the dog of the high-speed side relative rotating body that is either the first high-speed gear or the second high-speed gear by moving toward the meshing side in the axial direction, and the high-speed clutch ring dog is driven. When a coasting torque on the side opposite to the torque acts, the meshing in the axial direction is performed along a groove formed on the outer periphery of the second clutch ring cam fixedly installed on the first shaft or the second shaft and intersecting the axial direction. A high-speed clutch ring having a guide second protrusion that can move to the release side,
A shift actuator capable of moving the low-speed clutch ring and the high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and allowing movement to the axial meshing release side,
Equipped with
When the shift actuator moves the high speed clutch ring in the axial meshing direction to perform an upshift, and when the rotation speed of the first shaft is equal to or higher than a predetermined rotation speed, the inertia torque of the low speed clutch ring dog causes The axial movement time required to move the first guide projection along the groove to the axial disengagement position is such that the backlash between the dog of the low speed side relative rotating body and the low speed clutch ring dog is reduced to the low speed. An automatic transmission characterized in that it is shorter than a moving time in a rotation direction, which is moved by a relative speed between a dog of a side relative rotating body and the clutch ring dog. The automatic transmission according to claim 1,
A third high-speed gear fixedly or relatively rotatably supported on the first shaft;
A fourth high speed gear that is fixedly or rotatably supported by the second shaft and constantly meshes with the third high speed gear to achieve a second high speed side higher than the high speed side;
A second high speed clutch ring dog that meshes with a dog of the second high speed side relative rotating body that is either the third high speed gear or the fourth high speed gear by movement toward the meshing side in the axial direction; When a coasting torque on the side opposite to the driving torque acts on the second high-speed clutch ring dog, an axial direction formed on the outer periphery of the third clutch ring cam fixedly installed on the first shaft or the second shaft becomes A second high-speed clutch ring having a guide third protrusion that is movable in the axial disengagement side along the intersecting groove;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and allowing movement to the axial meshing release side.
An automatic transmission characterized in that the groove of the second clutch ring cam has a larger inclination angle than the groove of the first clutch ring cam. The automatic transmission according to claim 1 or 2,
A third high-speed gear fixedly or relatively rotatably supported on the first shaft;
A fourth high speed gear that is fixedly or rotatably supported by the second shaft and constantly meshes with the third high speed gear to achieve a second high speed side higher than the high speed side;
A second high speed clutch ring dog that meshes with a dog of the second high speed side relative rotating body that is either the third high speed gear or the fourth high speed gear by movement toward the meshing side in the axial direction; When a coasting torque on the side opposite to the driving torque acts on the second high-speed clutch ring dog, an axial direction formed on the outer periphery of the third clutch ring cam fixedly installed on the first shaft or the second shaft becomes A second high-speed clutch ring having a guide third protrusion that is movable in the axial disengagement side along the intersecting groove;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and allowing movement to the axial meshing release side.
The backlash between the dog of the high speed side relative rotating body and the high speed clutch ring dog is smaller than the backlash between the dog of the low speed side relative rotating body and the low speed clutch ring dog. The automatic transmission according to any one of claims 1 to 3,
A third high-speed gear fixedly or relatively rotatably supported on the first shaft;
A fourth high speed gear that is fixedly or rotatably supported by the second shaft and constantly meshes with the third high speed gear to achieve a second high speed side higher than the high speed side;
A second high speed clutch ring dog that meshes with a dog of the second high speed side relative rotating body that is either the third high speed gear or the fourth high speed gear by movement toward the meshing side in the axial direction; When a coasting torque on the side opposite to the driving torque acts on the second high-speed clutch ring dog, an axial direction formed on the outer periphery of the third clutch ring cam fixedly installed on the first shaft or the second shaft becomes A second high-speed clutch ring having a guide third protrusion that is movable in the axial disengagement side along the intersecting groove;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and permitting the movement to the axial meshing release side. A positioning mechanism that allows the clutch ring to move toward the axial disengagement side by a set load,
The set load of the positioning mechanism of the high speed clutch ring is lower than the set load of the positioning mechanism of the low speed clutch ring. The automatic transmission according to any one of claims 1 to 4,
A third high-speed gear fixedly or relatively rotatably supported on the first shaft;
A fourth high speed gear that is fixedly or rotatably supported by the second shaft and constantly meshes with the third high speed gear to achieve a second high speed side higher than the high speed side;
A second high speed clutch ring dog that meshes with a dog of the second high speed side relative rotating body that is either the third high speed gear or the fourth high speed gear by movement toward the meshing side in the axial direction; When a coasting torque on the side opposite to the driving torque acts on the second high-speed clutch ring dog, an axial direction formed on the outer periphery of the third clutch ring cam fixedly installed on the first shaft or the second shaft becomes A second high-speed clutch ring having a guide third protrusion that is movable in the axial disengagement side along the intersecting groove;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and allowing movement to the axial meshing release side.
An automatic transmission characterized in that the inertia of the high speed clutch ring is larger than the inertia of the low speed clutch ring. The automatic transmission according to any one of claims 1 to 5,
A third high-speed gear fixedly or relatively rotatably supported on the first shaft;
A fourth high speed gear that is fixedly or rotatably supported by the second shaft and constantly meshes with the third high speed gear to achieve a second high speed side higher than the high speed side;
A second high speed clutch ring dog that meshes with a dog of the second high speed side relative rotating body that is either the third high speed gear or the fourth high speed gear by movement toward the meshing side in the axial direction; When a coasting torque on the side opposite to the driving torque acts on the second high speed clutch ring dog, an axial direction formed on the outer periphery of the third clutch ring cam fixedly installed on the first shaft or the second shaft becomes A second high-speed clutch ring having a guide third protrusion that is movable toward the axial disengagement side along the intersecting groove;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by moving to the axial meshing side and allowing movement to the axial meshing release side.
An automatic transmission characterized in that an interstage ratio between the low speed stage and the high speed stage is larger than an interstage ratio between the high speed stage and the second high speed stage.

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