JP2018076905A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission capable of suppressing striking noise or transmission shock, in performing seamless shift.SOLUTION: An automatic transmission has a shift actuator capable of moving a low-speed clutch ring and a high-speed clutch ring in an axial engagement direction with movement toward an axial engagement side, and configured to allow movement toward an axial engagement release side. When the high-speed clutch ring is moved to the axial engagement direction to perform upshift, an axial movement time of a clutch ring dog is set shorter than a rotational movement time of moving backlash.SELECTED DRAWING: Figure 5

Description

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

  Patent Document 1 discloses an automatic transmission capable of shifting without interrupting torque transmission (hereinafter referred to as a seamless shift). For example, when performing an upshift to the second speed during traveling at the first speed, if a second-speed clutch ring that meshes with the second-speed gear is engaged, a coasting torque acts on the first-speed gear. The coasting torque is used to generate an axial force in the meshing release direction in the first-speed clutch ring to achieve a seamless shift to the second speed. To achieve 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 perform a shift.

JP2012-127471A

However, when the shift fork is operated to engage the clutch gear for the second speed, there is a problem that the hitting sound and the shift shock give the driver a strange feeling when the dog is engaged.
An object of the present invention is to provide an automatic transmission capable of suppressing a hitting sound and a shift shock when performing a seamless shift.

  In order to achieve the above object, in the automatic transmission according to the present invention, the first low-speed gear and the first high-speed gear that are fixedly or relatively rotatably supported on the first shaft, and the second shaft that is fixedly or relatively rotatably supported. The second low-speed gear that always meshes with the first low-speed gear and the second high-speed gear that always meshes with the first high-speed gear and achieves the high-speed gear, and the movement toward the axial meshing side causes the first low-speed gear. Having a low-speed clutch ring dog that meshes with the 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 on the low-speed clutch ring dog from the dog of the low-speed side relative rotating body, It is movable to the axial meshing release side along a groove that intersects the axial direction formed on the outer periphery of the first clutch ring cam fixedly installed on the first shaft or the second shaft. A low-speed clutch ring having a first protrusion for id and a high-speed clutch ring that meshes with the dog of the high-speed relative rotating body that is either the first low-speed gear or the second high-speed gear by moving toward the axial meshing side. When a torque acts on the high-speed clutch ring dog from the dog of the high-speed side relative rotating body, it is 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 can move to the axial engagement release side along a groove intersecting with the axial direction, and the low-speed clutch ring and the high-speed clutch ring by movement to the axial engagement side A shift actuator capable of moving in the axial meshing direction and allowing movement toward the axial meshing release side, and the shift actuator Thus, when the high speed clutch ring is moved in the axial meshing direction to perform an upshift, and the rotational speed of the first shaft is equal to or higher than a predetermined rotational speed, the guide clutch is driven by the inertia shuttle of the low speed clutch ring dog. The axial movement time required to move one protrusion along the groove to the axial meshing release position causes the backlash between the dog of the low-speed side relative rotating body and the low-speed clutch ring dog to rotate relative to the low-speed side. It is characterized in that it is shorter than the moving time in the rotational direction in which it moves according to the relative speed between the body dog and the clutch ring dog.

  Therefore, the hitting sound can be suppressed at the time of upshift by seamless shift.

1 is a schematic system diagram illustrating an automatic transmission according to a first embodiment. It is a perspective view showing the 1st clutch ring cam of Example 1. FIG. FIG. 3 is a perspective view illustrating a first clutch ring according to the first embodiment. FIG. 6 is a schematic diagram illustrating an operation of a first dog clutch mechanism in an upshift from the first speed to the second speed in the automatic transmission according to the first embodiment. FIG. 6 is an enlarged partial cross-sectional view illustrating an operation of a first dog clutch mechanism in an upshift from the first speed to the 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 the engine output shaft 1 a of the engine 1 through 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 disposed in parallel with the first shaft 301. On the first shaft 301, there are a first speed drive gear 311, a second speed drive gear 321, and a third speed drive gear 331 supported so as to be rotatable relative to the first shaft 301. On the second shaft 302, there are a first speed driven gear 312, a second speed driven gear 322, and a third speed driven gear 332 that are fixed to the second shaft 302 and rotate integrally with the second shaft 302. Each driven gear always meshes with each drive gear.

  The transmission controller 3 a determines a desired shift stage from a shift map, which will be described later, based on various sensors and shift signals not shown in the figure, and outputs a shift actuator drive signal to the shift actuator 30. The shift actuator 30 is configured to be able to move the first shift fork 31 and the second shift fork 32 in the axial direction. The shift actuator 30 controls the position of a shift drum 30a having a shift groove 30b that engages with the shift forks 31 and 32 on the outer periphery 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 positions in the axial direction. The positioning mechanisms 31b, 32b, and 33b are slightly moved in the axial direction in accordance with changes in the dog meshing position in accordance with the torque acting direction described later after the shift forks 31, 32, and 33 are positioned by the shift actuator 30. 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 311 a extending in the axial direction is provided on a 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 is applied, a coast side engagement surface 311a3 that engages the first clutch ring dog 34c when the coasting torque is applied, 1 end face 311a1 parallel to the direction orthogonal to the axis facing one clutch ring dog 34c. A 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 is applied, a coast side engagement surface 321a3 that engages with the second clutch ring dog 35c when the coasting torque is applied, 2 end face 321a1 parallel to the direction orthogonal to the axis facing the clutch ring dog 35c. 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 is applied, a coast side engagement surface 331a3 that engages with the third clutch ring dog 36c when the coasting torque is applied, And an end face 331a1 parallel to the axial orthogonal direction facing the three clutch ring dog 36c.

  At positions adjacent to the first speed drive gear 311, the second speed drive gear 321 and the third speed drive gear 331, there are a first dog clutch mechanism DG1, a second dog clutch mechanism DG2 and a third dog clutch mechanism DG3. The first dog clutch mechanism DG1 is installed on the outer periphery of the first clutch ring cam 400 fixedly installed on the first shaft 301 and meshes with the first shift fork 31 so as to be relatively rotatable. A first clutch ring 34 is provided. FIG. 2 is a perspective view illustrating the first clutch ring cam of the first embodiment. On the outer periphery 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 includes a first-speed-side downward inclined surface 401a that inclines toward the positive rotation direction of the first shaft 301, and a first-speed-side upward inclined surface 401e that faces the first-speed-side downward inclined surface 401a. Have.

  The tip upper side of the V-shaped groove adjacent to the first-speed-side upper inclined surface 401e is a neutral position 401f in a state where it does not mesh with the first-speed drive gear 311. One protrusion 33b is held at a neutral position 401f that is the tip of the V-shaped groove. Further, the first-speed-side downward inclined surface 401a has an angle θ that intersects 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 lower inclined surface 401a and parallel to the axial direction. Note that the second dog clutch mechanism DG2 and the third dog clutch mechanism DG3 are also similar to the first dog clutch mechanism DG1 in the second and third clutch rings 35 and 36, the second and third clutch ring cams 500 and 600, and the V-shape. Grooves 501, 601, 2nd speed and 3rd speed side downward inclined surfaces 501 a and 601 a and holding surfaces 501 b and 601 b are provided. Since the configuration is the same as that of the first dog clutch mechanism DG1, description thereof is omitted.

  FIG. 3 is a perspective view illustrating 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 to the outer diameter side of the cylindrical member 34e. Have. The first sleeve 34 a is a disc-like member that can be applied to the shift fork 31 while being held rotatably relative to the shift fork 31. The first clutch ring 34 projects from the first sleeve 34a to the first clutch ring dog 34c extending in the axial direction on the side surface facing the first-speed drive gear 311 and the inner peripheral side of the cylindrical member 34e. And a guide first protrusion 34 b 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 away from the first-speed drive gear 311 when the driving torque is applied, a drive-side engagement surface 34c2 that meshes with the first dog 311a when the driving torque is applied, and a coasting torque A coast-side engagement surface 34c3 that meshes with the first dog 311a during operation, and an end surface 34c4 that faces the first dog 311a and is parallel to the direction perpendicular to the axis.

The second clutch ring 35 includes a cylindrical member 35e that can move relative to the outer periphery of the second clutch ring cam 500, and a second sleeve 35a that is expanded in diameter from the axial center to the outer diameter side of the cylindrical member 35e. Have. The second sleeve 35a is a disk-like member that can be applied to the shift fork 32 and an axial force while being held by the shift fork 32 so as to be relatively rotatable. The second clutch ring 35 projects from the second sleeve 35a to the second clutch ring dog 35c extending in the axial direction on the side surface facing the second speed drive gear 321, and to the inner peripheral side of the cylindrical member 35e. And a guide second protrusion 35 b 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 periphery of the third clutch ring cam 600, and a third sleeve 36a that is expanded in diameter from the axial center to the outer diameter side of the cylindrical member 36e. Have. The third sleeve 36 a is a disk-shaped member that can be applied to the shift fork 33 and an axial force while being held by the shift fork 33 so as to be relatively rotatable. The third clutch ring 36 projects from the third sleeve 36a to the third clutch ring dog 36c extending in the axial direction on the side surface facing the third-speed drive gear 331, and to the inner peripheral side of the cylindrical member 36e. And a third guide projection 36 b guided in the V-shaped groove 601 of the clutch ring cam 600. Similarly to the first clutch ring dog 34c, 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.

  Next, the upshift operation will be briefly described. As a specific example, a case where the upshift to the second speed is performed in the first speed traveling state will be described. 4 and 5 are schematic views showing the operation of the first dog clutch mechanism in the upshift from the first speed to the second speed in the automatic transmission of the first embodiment. In the first speed, the first shift fork 31 is moved to the left side in FIG. As shown in FIG. 2A, in the first clutch ring 34, in a state before the torque acts on the first-speed drive gear 311, the first guide projection 34b is positioned on the holding surface 401b, and the coasting torque is Even if it acts, it does not move in the axial direction. The second guide projection 35b is positioned 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 projection 35b abuts on the neutral position 501f. This is a state in which the second clutch ring 35 is rotated through the two protrusions 35b.

  As shown in FIG. 4B, the tooth surface of the first clutch ring dog 34c of the first clutch ring 34 is engaged with the first dog 311a of the first speed drive gear 311 when the driving torque is applied. An inclined surface 34c1 is formed. When driving torque is applied from the first speed drive gear 311 to the first speed driven gear 312, the first clutch ring 34 is lifted toward the meshing release side along the inclined surface 34 c 1. As a result, the first guide projection 34b moves from the holding surface 401b to the position of the first-speed-side upward inclined surface 401e. However, the meshing of the first dog 311a of the first-speed drive gear 311 and the first-speed clutch ring dog 34c is continued, and the torque is transmitted. In performing this operation, the positioning mechanism 31b described above operates. That is, the axial position of the first clutch ring 34 after the lift is stably held while allowing the first shift fork 31 to move slightly in the axial direction along with the lift.

  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 be engaged, an interlock state is established, and the first speed clutch ring dog 34c A coasting torque acts between the first dog 311a. Then, as shown in FIG. 5, the first guide projection 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 is moved quickly.

  Then, the first guide projection 34b moves on the first-speed-side downward inclined surface 401a, and the axial tooth tip of the first dog 311a of the first-speed drive gear 11 and the axial tooth tip of the first-speed clutch ring dog 34c. When the axial position exceeds a predetermined position, the first guide projection 34b moves along the first-speed lower inclined surface 401a, and the first-speed clutch ring dog 34c moves to the axial release side. As a result, the first clutch ring 34 moves to the engagement release 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.

  In other words, at the first speed, the second speed drive gear 321 and the second clutch ring dog 35c are engaged, and the first speed drive gear 311 and the first speed are utilized by using the coasting torque accompanying the interlock 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 seamless shift.

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

  As described above, when the coasting torque acts upon 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 where 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. 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 lower inclined surface 401a, and the first shift fork 31 is The first-speed engaged state is released by moving in the axial direction. However, there has been a problem that sound vibration performance and durability deteriorate due to the collision.

  Therefore, in the first embodiment, the inertia clutch of the first clutch ring dog 34c is used to move the first clutch ring dog 34c in the axial direction before the coast side engagement surface 34c3 and the coast side engagement surface 311a3 collide with each other. It was 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 decelerates 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 maintaining 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 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 driving torque is applied is R1 (hereinafter also referred to as backlash R1), the first speed drive gear 311 is also V1. Therefore, the relative speed between the first-speed drive gear 311 and the first clutch ring 34 is (V1-V2), and the time for moving R1 at this relative speed is Tbr (hereinafter referred to as rotational direction moving time Tbr). As well))
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 axially disengaged position before the coast side engaging surface 34c3 and the coast side engaging surface 311a3 collide with each other ( (See states (II) and (III) in FIG. 5). Therefore, when the upshift is performed by crossing the upshift line from the first speed to the second speed set in the shift map, various parameters are set so that the above relationship is obtained. If the rotational speed of the first shaft 301 is equal to or higher than a predetermined rotational speed, it is possible to cope with a manual shift by setting so that the relationship of Tbr> Tst is obtained.

  Next, in the upshift from the second speed to the third speed, compared with the upshift from the first speed to the second speed, the first shaft 301 is upshifted at a relatively low rotation. 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 rotational speed.

  Also, the 2-speed backlash R1 is made smaller than the 1-speed backlash R1. That is, when the upshift is performed at a low rotation, it is easy to secure Tbr.

  Further, the set load of the second speed positioning mechanism 32b is made lower than the set load of the first speed positioning mechanism 31b. In other words, the inertia torque becomes small at low rotation, so that if the set load is large, it is difficult to obtain the force necessary 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 mass by increasing the diameter, changing the wall thickness, or changing the material, a sufficient inertia torque can be secured even at a low rotation.

  In addition, the interstage ratio between the 1st speed and the 2nd speed is made larger than the interstage ratio between the 2nd speed and the 3rd speed. That is, since the relative speed between the drive gear and the clutch ring is determined by the interstage ratio, the Tbr can be increased by increasing the relative speed in the upshift on the high speed side.

The effect based on the said Example 1 is demonstrated.
(1) a first speed drive gear 311 (first low speed gear) and a second speed drive gear 321 (first high speed gear) supported by the first shaft 301 so as to be (fixed or) relatively rotatable;
A first-speed driven gear 312 (second low-speed gear) that is fixed to the second shaft 302 (or supported so as to be relatively rotatable) and always meshes with the first-speed drive gear 311 and achieves the first speed, and the second-speed drive gear 321 always meshes with the second speed. 2-speed driven gear 322 to achieve (second high-speed gear);
A first clutch ring dog 34c (low-speed clutch) that meshes with the first dog 311a (the dog of the low-speed relative rotating body that is either the first low-speed gear or the second low-speed gear) by the movement toward the axial meshing side. 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 projection 34b that can move to the axial engagement release side along a V-shaped groove 401 that is a groove intersecting 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 the movement toward the axial meshing side. 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 movable to the axial engagement release side along a V-shaped groove 501 that is a groove intersecting with
A first shift fork 31 capable of moving the first clutch ring 34 and the second clutch ring 35 in the axial meshing direction by movement toward the axial meshing side and allowing movement toward the axial meshing release side; A second shift fork 32 and a shift actuator 30;
With
The shift actuator 30 moves the second clutch ring 35 in the axial meshing direction and performs an upshift. When the rotational speed of the first shaft 301 is equal to or higher than the predetermined rotational speed, the inertia clutch of the first clutch ring dog 34c is used. As a result, the axial movement time Tst required to move the first guide projection 34b along the V-shaped groove 401 to the axial engagement release position is the backlash R1 between the first dog 311a and the first clutch ring dog 34c. Is shorter than the rotational direction moving time Tbr in which the first dog 311a and the first clutch ring dog 34c move at a relative speed.
Therefore, during the upshift by the seamless shift, the first clutch ring dog 34c is axially moved before the coast side engagement surface 34c3 of the first clutch ring 34 and the coast side engagement surface 311a3 of the first speed drive gear 311 collide with each other. It is possible to move to the non-engagement position, and the shift shock can be suppressed while suppressing the hitting sound associated with the dog meshing.

  (2) A third speed drive gear 331 (third high speed gear) supported so as to be relatively rotatable on the first shaft 301 and a third speed drive gear 331 fixed to the second shaft 302 and always meshing with the second speed stage. A third speed driven gear 332 (fourth high speed gear) that achieves the third speed stage (second high speed stage) and a third dog 331a (the third high speed gear or the fourth high speed gear) by moving toward the axial meshing side. A second clutch ring dog 36c (second high speed clutch ring dog) meshing with the second high speed side relative rotating body dog), and the third clutch ring dog 36c is opposite to the driving torque. When the coasting torque is applied, the shaft extends along the V-shaped groove 600 that intersects the axial direction formed on the outer periphery of the third clutch ring cam 600 fixedly installed on the second shaft 302. And a third clutch ring 36 (second high-speed clutch ring) having a guide third protrusion 36b movable to the counter-meshing release side, and the shift actuator 30 is moved by the movement toward the axial meshing side. 3 is a shift actuator that can move the clutch ring 36 in the axial meshing direction and allows the clutch clutch 36 to move toward the axial meshing release side. The inclination angle θ of the V-shaped groove 501 of the second clutch ring cam 35 The inclination angle θ of the V-shaped groove 401 of the clutch ring cam 400 is larger. 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 rotational 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 rotational speed of the first shaft 301 at the time of upshift from the second speed to the third speed is low, the rotational direction movement time Tbr can be secured.

  (4) The shift actuator 30 includes positioning mechanisms 31b and 32b that allow the clutch ring to move in the axial engagement release side by the set load of the elastic body, and the set load of the positioning mechanism 35b of the second clutch ring 35 is The load is lower than the set load of the first clutch ring positioning mechanism 31b. Therefore, the axial movement can be achieved even when the rotational speed of the first shaft 301 at the time of upshift from the second speed to the third speed is low and the inertia torque is small.

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

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

(Other examples)
As described above, the description is based on the first embodiment. However, the present invention is not limited to the above-described embodiment, and the present invention may be applied to an automatic transmission having another configuration. Specifically, the present invention can be applied not only to the third forward speed but also to an automatic transmission that is further multi-staged.
In the first embodiment, the V-shaped groove is used. However, when the drive gear is present only on one side of the clutch ring, the V-shaped groove is not necessary, and the inclined groove on the side where the drive gear is not present 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 for guide second clutch 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 drill Second gear 321 second gear 322 second gear driven gear 400 first clutch ring cam 401 V-shaped groove 401a first-speed side lower inclined surface 500 second clutch ring cam 501 V-shaped groove 501a second-speed side lower inclined surface 600 first 3 clutch ring cam 601 V-shaped groove 601a 3rd speed lower inclined surface 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 supported on the first shaft so as to be fixed or relatively rotatable;
A second low-speed gear that is fixedly or relatively rotatably supported on 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 always meshes with the first high-speed gear and achieves a high-speed stage;
A low-speed clutch ring dog that meshes with a dog of the low-speed relative rotating body that is either the first low-speed gear or the second low-speed gear by moving toward the axial meshing side, and driving the low-speed clutch ring dog When a coasting torque on the opposite side of the torque is applied, axial meshing occurs along a groove intersecting the axial direction formed on the outer periphery of the first clutch ring cam fixedly installed on the first shaft or the second shaft. A low-speed clutch ring having a first guide guide that is movable toward the release side;
A high-speed clutch ring dog that meshes with the dog of the high-speed relative rotating body that is either the first high-speed gear or the second high-speed gear by moving toward the axial meshing side, and driving the high-speed clutch ring dog When a coasting torque on the opposite side of the torque is applied, axial meshing occurs along a groove intersecting 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 second guide guide movable toward 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 movement toward the axial meshing side and allowing movement to the axial meshing release side;
With
When the shift actuator moves the high-speed clutch ring in the axial engagement direction to perform an upshift, and the rotational speed of the first shaft is equal to or higher than a predetermined rotational speed, the inertia shuttle of the low-speed clutch ring dog The axial movement time required to move the first guide protrusion along the groove to the axial meshing release position reduces the backlash between the low-speed relative rotating body dog and the low-speed clutch ring dog. An automatic transmission characterized in that it is shorter than a rotational direction moving time in which it moves according to a relative speed between a dog of a side relative rotating body and the clutch ring dog. The automatic transmission according to claim 1, wherein
A third high speed gear fixed to the first shaft or supported so as to be relatively rotatable;
A fourth high-speed gear fixed to the second shaft or supported rotatably relative to the third high-speed gear and constantly meshing with the third high-speed gear to achieve a second high-speed stage on the higher speed side than the high-speed stage;
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 axial meshing side; When a coasting torque 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; A second high-speed clutch ring having a third guide guide movable along the intersecting groove to the axial engagement release side;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by movement toward the axial meshing side and allowing movement to the axial meshing release side,
2. The automatic transmission according to claim 1, wherein an inclination angle of the groove of the second clutch ring cam is larger than an inclination angle of the groove of the first clutch ring cam. The automatic transmission according to claim 1 or 2,
A third high speed gear fixed to the first shaft or supported so as to be relatively rotatable;
A fourth high-speed gear fixed to the second shaft or supported rotatably relative to the third high-speed gear and constantly meshing with the third high-speed gear to achieve a second high-speed stage on the higher speed side than the high-speed stage;
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 axial meshing side; When a coasting torque 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; A second high-speed clutch ring having a third guide guide movable along the intersecting groove to the axial engagement release side;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by movement toward the axial meshing side and allowing movement to the axial meshing release side,
2. The automatic transmission according to claim 1, wherein a backlash between the dog of the high speed side relative rotating body and the high speed clutch ring dog is smaller than a 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 fixed to the first shaft or supported so as to be relatively rotatable;
A fourth high-speed gear fixed to the second shaft or supported rotatably relative to the third high-speed gear and constantly meshing with the third high-speed gear to achieve a second high-speed stage on the higher speed side than the high-speed stage;
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 axial meshing side; When a coasting torque 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; A second high-speed clutch ring having a third guide guide movable along the intersecting groove to the axial engagement release side;
Have
The shift actuator is a shift actuator that is capable of moving the second high-speed clutch ring in the axial meshing direction by movement toward the axial meshing side and allows movement to the axial meshing release side. A positioning mechanism that allows the clutch ring to move toward the axial engagement release side by a set load;
An automatic transmission characterized in that a set load of the positioning mechanism of the high speed clutch ring is lower than a 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 fixed to the first shaft or supported so as to be relatively rotatable;
A fourth high-speed gear fixed to the second shaft or supported rotatably relative to the third high-speed gear and constantly meshing with the third high-speed gear to achieve a second high-speed stage on the higher speed side than the high-speed stage;
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 axial meshing side; When a coasting torque 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; A second high-speed clutch ring having a third guide guide movable along the intersecting groove to the axial engagement release side;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by movement toward the axial meshing side and allowing movement to the axial meshing release side,
2. The automatic transmission according to claim 1, wherein an inertia of the high speed clutch ring is larger than an inertia of the low speed clutch ring. The automatic transmission according to any one of claims 1 to 5,
A third high speed gear fixed to the first shaft or supported so as to be relatively rotatable;
A fourth high-speed gear fixed to the second shaft or supported rotatably relative to the third high-speed gear and constantly meshing with the third high-speed gear to achieve a second high-speed stage on the higher speed side than the high-speed stage;
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 axial meshing side; When a coasting torque 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; A second high-speed clutch ring having a third guide guide movable along the intersecting groove to the axial engagement release side;
Have
The shift actuator is a shift actuator capable of moving the second high-speed clutch ring in the axial meshing direction by movement toward 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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