JP6330194B2 - Control device for automatic transmission - Google Patents

Description

  The present invention relates to a control device for an automatic transmission capable of shifting without interruption of torque transmission.

  Patent Document 1 discloses an automatic transmission that is capable of shifting without interruption of torque transmission (hereinafter referred to as a seamless shift) in a parallel two-shaft type continuously meshing transmission. 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.

JP2012-127471A

However, for example, when the 2nd speed clutch ring is engaged with the 2nd speed gear, the 2nd speed gear has a lower rotation than the 1st speed gear, and the 2nd speed clutch ring has the same rotation as the 1st speed gear. There is a problem that it is necessary to mesh the second-speed clutch ring while holding it, and the hitting sound associated with the meshing is large, which makes the driver feel uncomfortable.
An object of the present invention is to provide a control device for an automatic transmission that can perform a seamless shift while suppressing an impact sound.

In order to achieve the above object, in the automatic transmission control device of the present invention, the first low-speed gear and the first high-speed gear supported on the first shaft so as to be fixed or relatively rotatable, and the second shaft fixed or relative rotation. A second low-speed gear that is movably supported and always meshes with the first low-speed gear, a second high-speed gear that always meshes with the first high-speed gear, and the first low-speed gear or the second low-speed gear by movement toward the axial meshing side. A low-speed clutch ring dog that meshes with the dog of the low-speed relative rotating body, and when the torque acts on the low-speed clutch ring dog from the dog of the low-speed relative rotating body, it moves to the axial engagement release side slow and slow clutch ring having a side guide portion, the axial movement of the meshing side, the dog of the high-speed relative rotation body is either the first high-speed gear or the second high-speed gear to A high-speed clutch ring having a high-speed clutch ring dog that has a high-speed side guide portion that moves to an axial engagement release side when torque is applied to the high-speed clutch ring dog from the dog of the high-speed side relative rotating body; A shift actuator capable of moving the low-speed clutch ring and the high-speed clutch ring in the axial meshing direction by movement to the direction meshing side and allowing movement to the axial meshing release side; and the low-speed clutch ring dog And the dog of the low-speed relative rotating body mesh with each other, the axial movement speed of the shift actuator when the high-speed clutch ring is moved to the axial meshing side is defined as the high-speed clutch of the high-speed relative rotating body. e Bei shift actuator control unit to increase the larger the rotational speed of relative rotation between the ring and the Shifutoakuchu The data control means has a preset target relative rotational speed greater than 0, and the high-speed clutch ring dog and the dog of the high-speed relative rotating body start to overlap at the axial position at the axial initial position. The axial movement speed is calculated so that the relative rotational speed between the high-speed relative rotating body and the high-speed clutch ring matches the target relative rotational speed.

When the low-speed gear is selected, the first shaft and the first low-speed gear rotate together at the automatic transmission input rotation speed, and the second shaft and the second low-speed gear rotate at a predetermined rotation speed according to the gear ratio of the low-speed gear. Rotate together. The low speed clutch ring dog and the high speed clutch ring dog rotate together with the first shaft or the second shaft. At this time, the high-speed relative rotating body rotates at a lower rotational speed than the high-speed clutch ring dog according to the gear ratio of the high-speed gear. When the high speed clutch ring is moved to the axial meshing side in this state, the high speed clutch ring is moved in the axial direction while being rotated by the high speed side guide portion, and the rotational speed of the high speed clutch ring is reduced. . The axial movement speed of the shift actuator has a preset target relative rotational speed greater than 0, and the axial initial position at which the high-speed clutch ring dog and the dog of the high-speed relative rotating body start to overlap at the axial position. The relative rotational speed of the high-speed side relative rotating body and the high-speed clutch ring in FIG. 6 is calculated so as to match the target relative rotational speed. Accordingly, the higher the relative rotational speed of the high-speed relative rotating body, the faster the axial movement speed of the shift actuator and the initial axial position at which the high-speed clutch ring dog and the dog of the high-speed relative rotating body begin to overlap at the axial position. The rotational speed of the high-speed side relative rotator is moved by moving at the axial movement speed calculated so that the relative rotational speed of the high-speed side relative rotator and the high-speed clutch ring matches the target relative rotational speed. And the rotation speed of the high-speed clutch ring can be reduced, and the impact sound and the like when the high-speed clutch ring dog and the dog of the high-speed side relative rotation body are engaged with each other can be suppressed.

1 is a schematic system diagram illustrating an automatic transmission according to a first embodiment. FIG. 2 is a schematic diagram illustrating 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. It is a control block diagram showing shift actuator control of Example 1. 3 is a characteristic map showing the relationship between a deviation Δωv and a shift speed Vs according to the first embodiment. FIG. 6 is a characteristic diagram illustrating a relationship between a dog relative position Δθ and a meshing length according to the first embodiment. 4 is a time chart when the automatic transmission of the first embodiment is upshifted from the first speed to the second speed. FIG. 3 is a schematic diagram illustrating a relationship between a clutch ring dog and a gear dog during upshifting 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 includes 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, a first speed drive gear 311 (corresponding to a first low speed gear) supported so as to be rotatable relative to the first shaft 301, and a second speed drive gear 321 (corresponding to a first high speed gear). And a third speed drive gear 331 and a fourth speed drive gear 341. On the second shaft 302, a first speed driven gear 312 (corresponding to a second low speed gear) fixed to the second shaft 302 and rotating integrally with the second shaft 302, and a second speed driven gear 322 (corresponding to a second high speed gear). ), A 3-speed driven gear 332, and a 4-speed driven gear 342. Each driven gear always meshes with each drive gear.

  The transmission controller 3 a determines a desired gear position 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 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 having a groove engaged with each shift fork on the outer periphery by a motor. The first shift fork 31 and the second shift fork 32 have positioning mechanisms 31b and 32b that can be biased to predetermined positions in the axial direction. The positioning mechanisms 31b and 32b allow a slight movement in the axial direction in accordance with a change in the meshing position of the dog in accordance with the torque acting direction described later after each shift fork is positioned by the shift actuator 30. A holding force at a predetermined axial position is applied to each shift fork at a plurality of positions. Details will be described later.

  The first speed drive gear 311 and the third speed drive gear 331 are disposed adjacent to each other. The second speed drive gear 321 and the fourth speed drive gear 341 are disposed adjacent to each other. A side surface of the first drive gear 311 facing the third drive gear 331 has a first dog 311 a extending in the axial direction. Similarly, a third dog 331a is provided on the side surface of the third drive gear 331 facing the first drive gear 311. A side surface of the second drive gear 321 facing the fourth drive gear 341 has a second dog 321a extending in the axial direction. Similarly, a fourth dog 341 a is provided on the side surface of the fourth drive gear 341 facing the second drive gear 321.

  Between the first speed drive gear 311 and the third speed drive gear 331 and between the second speed drive gear 321 and the fourth speed drive gear 341, there are first and second dog clutch mechanisms DG1 and DG2. 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 33 is provided. 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 inclined groove 401 a that is inclined toward the positive rotation direction side of the first shaft 301 and a third speed side inclined groove 401 c.

  The end of the first clutch ring 33 facing the first-speed drive gear 311 side has a holding groove 401b connected to the first-speed side inclined groove 401a and parallel to the axial direction. Similarly, the end portion of the first clutch ring 33 facing the third speed drive gear 331 side has a holding groove 401d connected to the third speed side inclined groove 401c and parallel to the axial direction. The second dog clutch mechanism DG2 also includes the second clutch ring 34, the second clutch ring cam 500, the V-shaped groove 501, the second speed side inclined groove 501a, and the fourth speed side inclined groove 501c similar to the first dog clutch mechanism DG1. And holding grooves 501b and 501d. Since the configuration is the same as that of the first dog clutch mechanism DG1, description thereof is omitted.

  The first clutch ring 33 includes a cylindrical member 33e that can move relative to the outer periphery of the first clutch ring cam 400, and a first sleeve 33a that is expanded in diameter from the axial center to the outer diameter side of the cylindrical member 33e. Have. The first sleeve 33 a is a disk-shaped member that can be applied to the shift fork 31 while being held rotatably relative to the shift fork 31. The first clutch ring 33 includes a first-speed first clutch ring dog 33c extending from the first sleeve 33a in the axial direction of the side surface facing the first-speed drive gear 311 and a side shaft facing the third-speed gear 331. First clutch ring dog 33d for the third speed extending in the direction, and a first guide protrusion 33b that protrudes to the inner peripheral side of the cylindrical member 34e and is guided into the V-shaped groove 401 of the first clutch ring cam 400. And having.

  Similarly, the second clutch ring 34 includes a cylindrical member 34e that can move relative to the outer periphery of the second clutch ring cam 500, and a second diameter that is expanded from the axial center to the outer diameter side of the cylindrical member 34e. It has a sleeve 34a. The second sleeve 34 a 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 34 includes a second-speed second clutch ring dog 34c extending from the second sleeve 34a in the axial direction of the side surface facing the second-speed drive gear 321, and a side shaft facing the fourth-speed gear 341. Second clutch ring dog 34d for the fourth speed extending in the direction, and the second guide protrusion 34b that protrudes to the inner peripheral side of the cylindrical member 34e and is guided into the V-shaped groove 501 of the second clutch ring cam 500. And having.

  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. FIG. 2 is a schematic diagram illustrating 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 33, the guide first protrusion 33b is positioned in the holding groove 401b before the torque is applied to the first-speed drive gear 311 and the coasting torque is reduced. Even if it acts, it does not move in the axial direction.

  As shown in FIG. 2B, the tooth surface of the first clutch ring dog 33c for the first speed of the first clutch ring 33 is engaged with the first dog 311a of the first speed drive gear 311 when the driving torque is applied. Is formed with an inclined surface 33c1. When driving torque is applied from the first speed drive gear 311 to the first speed driven gear 312, the first clutch ring 33 is lifted toward the meshing release side along the inclined surface 33 c 1. As a result, the first guide protrusion 33b moves from the holding groove 401b to the position of the first-speed inclined groove 401a. However, the meshing between the first dog 311a of the first-speed drive gear 311 and the first-speed clutch ring dog 33c 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 33 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 in FIG. 1 and the second-speed second clutch ring dog 34c and the second dog 321a start to be engaged, the interlock state is established and the first-speed clutch ring is engaged. A coasting torque acts between the dog 33c and the first dog 311a. Then, as shown in FIG. 2 (c), since the first guide projection 33b moves along the first speed side inclined groove 401a, the first clutch ring 33 moves to the mesh release side, and the first speed drive gear. 11 first dog 311a and first-speed clutch ring dog 33c are completely disengaged. 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.

  That is, the first-speed drive gear 311 is engaged by engaging the second-speed drive gear 321 and the second-speed second clutch ring dog 34c at the first speed, and using the coasting torque accompanying the interlock state generated by the engagement. And the first clutch ring 33 are disengaged. Therefore, the torque transmission state can always be maintained during the upshift. Such a shift operation is called seamless shift. The downshift is performed by the same action, and for details of the shift operation, refer to, for example, Japanese Patent Application Laid-Open No. 2012-127471.

(Shift actuator control processing)
Next, the shift actuator control process in the transmission controller 3a will be described. In the automatic transmission according to the first embodiment, when the seamless shift is performed as described above, the gear is immediately shifted if the engagement between the drive gear and the clutch ring is established at the post-shift gear stage. In order to achieve this shift, it is necessary to appropriately engage the drive gear and the clutch ring at the post-shift speed. For example, assuming that the first shaft 301 is rotating at 1000 rpm at the first speed, the second dog 321a of the second speed drive gear 321 is rotating at, for example, 500 rpm because of the gear ratio between the first speed and the second speed. Assume. At this time, even if the shift actuator 30 is operated and the second shift fork 32 is moved in the axial direction, the second clutch ring dog 34c for 2nd speed is rotated at 1000 rpm, so that the relative position with respect to the second dog 321a The rotation speed is large. In this state, if the second clutch ring dog 34c for the second speed and the second dog 321a mesh with each other, the striking sound becomes loud and the driver may feel uncomfortable. Further, since the phase of the second clutch ring dog 34c for the second speed and the second dog 321a are different from each other, if the tooth tips of the second clutch ring dog 34c for the second speed and the second dog 321a hit each other, they can mesh with each other. There is a risk that it will not be possible (hereinafter, this phenomenon will be described as incomprehensible).

  Here, as a result of intensive studies, the inventors have found that the clutch ring is decelerated by the action of the V-shaped groove when the shift fork moves in the axial direction. The V-shaped groove is originally set for the purpose of moving the already engaged clutch ring to the engagement release side when the coasting torque is applied in the interlock state. However, it has been found that when the clutch ring to be meshed is shifted to the meshing side during shifting, a deceleration phenomenon occurs in which the clutch ring moves while decelerating. Therefore, in the first embodiment, the speed of the shift fork in the axial direction is controlled using this deceleration phenomenon, and the relative rotational speed between the drive gear and the clutch ring at the post-shift gear stage is suppressed, and the shift timing is set. It was decided to perform shift actuator control to avoid incompletion by controlling.

  FIG. 3 is a control block diagram illustrating the shift actuator control according to the first embodiment. The clutch ring dog position detection sensor 101 includes a first clutch ring dog 33c for the first speed, a first clutch ring dog 33d for the third speed, a second clutch ring dog 34c for the second speed, and a second clutch ring dog 34d for the fourth speed (hereinafter referred to as the second clutch ring dog 34d). The clutch side dog rotational position θc of the clutch ring dog) is detected. The gear dog position detection sensor 102 detects the gear side dog rotation position θg of the first dog 311a, the second dog 321a, the third dog 331a, and the fourth dog 341a (hereinafter also collectively referred to as a gear dog). The first shaft rotation speed detection sensor 103 detects the first shaft rotation speed ω of the first shaft 301. In the inter-step ratio output unit 104, the inter-step ratio Δi between the gear ratios to be shifted (for example, if it is an upshift from the first speed to the second speed, i1 is the gear ratio of the first speed and i2 is the gear ratio of the second speed) At this time, Δi = i1 / i2) is output.

In the relative rotational speed calculation unit 110, the relative rotation between the post-shift drive gear and the first shaft 301, which is a relative rotational body in the shift stage after the shift, based on the detected first shaft rotational speed ω and the gear ratio Δi. The number Δω is calculated by the following formula.
(Formula 1)
Δω = ω × (1−Δi)

The target relative rotational speed output unit 111 outputs a target relative rotational speed Δω * (for example, 100 rpm) larger than 0 set in advance. Here, the reason why the target relative rotational speed Δω * is set larger than 0 is to engage the clutch ring dog and the gear dog in a state where the relative rotational speed is suppressed. If the target relative rotational speed Δω * is set to 0, the axial movement of the clutch ring dog may be completed before the two mesh with each other. If it does so, a clutch ring dog and a gear dog will mesh | engage in the state which cannot perform the axial movement for making a relative rotational speed small, and will mesh | engage after becoming a high relative rotational speed. This is because the striking sound and shock accompanying the engagement cannot be suppressed.
The deviation calculator 112 calculates a deviation Δωv between the relative rotational speed Δω and the target relative rotational speed Δω *.

  The shift speed calculation unit 113 calculates a shift speed Vs that is a moving speed of the shift fork based on the deviation Δωv. FIG. 4 is a characteristic map showing the relationship between the deviation Δωv and the shift speed Vs in the first embodiment. The inclination of this characteristic is defined by the inclination angle of the inclined groove formed in the V-shaped groove. If the inclination angle of the inclined groove is large, the decelerating action of the clutch ring with respect to the shift speed Vs increases. If the inclination angle of the inclined groove is small, the decelerating action of the clutch ring with respect to the shift speed Vs decreases. Since this characteristic depends on the inclination angle, the characteristic depends on the shape of the inclined groove. Now, for a V-shaped groove set at a certain inclination angle, the shift speed Vs for achieving the deviation Δωv can be easily calculated from a preset characteristic map. By moving the shift fork at the shift speed Vs calculated from this characteristic map, the relative rotational speed can be reduced to the target relative rotational speed Δω *. The shift speed Vs does not need to be generated from the initial stage of the shift fork operation, and may be generated at least at a timing at which both dogs mesh.

The dog relative position calculation unit 114 calculates the dog relative position Δθ (= θc−θg) based on the detected clutch side dog rotation position θc and the gear side dog rotation position θg.
The shift start position calculation unit 115 calculates a shift start position Δθ * representing the operation start timing of the shift fork based on the calculated shift speed Vs.

  FIG. 5 is a characteristic diagram showing the relationship between the dog relative position Δθ and the meshing length in the first embodiment. The meshing length represents the meshing depth of both dogs in the axial direction when the clutch ring dog and the gear dog mesh with each other. Since the clutch ring dog moves in the axial direction while rotating, the rotational position and the axial position have a corresponding relationship according to the shape of the V-shaped groove. When the position where the tooth tip of the clutch ring dog and the tooth tip of the gear dog begin to overlap in the axial position is defined as the axial initial position, and the position where the clutch ring dog has moved most to the axial meshing side is defined as the axial bottom position, It is necessary to mesh at a predetermined axial direction meshing position on the meshing side from the axial initial position and on the meshing release side from the axial bottom position. For example, when the predetermined axial meshing position is set to a position (meshing length 70%) moved from the axial initial position to a position that is about 70% of the axial bottom position, the gear dog Relative position Δθ is ensured, and the relative position Δθ with respect to the gear dog needs to be zero at the predetermined axial engagement position. The relationship between the axial position and the dog relative position Δθ is the characteristic diagram of FIG.

  In the region where the dog relative position Δθ is from 0 to Δθ1, it becomes a non-entry region where the tooth tips of the dog collide. Further, the region where the dog relative position Δθ is equal to or larger than Δθ2 represents the region where the clutch ring dog moves to the tooth bottom position of the gear dog. As described in the target relative rotational speed output unit 111, both dogs must be engaged while the clutch ring dog is moving in the axial direction, and cannot be engaged in the first place in the non-entry region.

Therefore, it is necessary to cause meshing within a region (OK region in FIG. 5) that is larger than Δθ1 and smaller than Δθ2. Since this characteristic diagram is a characteristic diagram that can be determined after the calculation of the shift speed Vs, after calculating the shift speed Vs, Δθ1 and Δθ2 are calculated. For example, the difference between Δθ1 and Δθ2 is closer to Δθ2 and is somewhat meshed. A target shift start position Δθ * that can secure a large length is calculated. For example,
Δθ * = Δθ1 + K (Δθ2−Δθ1)
Set as. However, K is a gain, and is set to 0.7 when it is desired to secure a meshing length of about 70%. Then, at the timing when the dog relative position Δθ reaches Δθ *, a command for operating the shift fork at the shift speed Vs is output to the shift actuator 30. Thereby, both dogs can be meshed in a state in which the relative rotational speed is suppressed while avoiding the non-entry area.

Next, the operation based on the above control will be described. FIG. 6 is a time chart when upshifting from the first speed to the second speed in the automatic transmission of the first embodiment, and FIG. 7 shows the relationship between the clutch ring dog and the gear dog at the time of upshifting in the automatic transmission of the first embodiment. FIG.
In the state of traveling at the first speed, as shown in the area (a) and FIG. 7 (a) of FIG. 6, the first dog 311a, the first clutch ring dog 33c for the first speed, and the second clutch ring for the second speed. The dog 34c rotates at 1000 rpm, and the second dog 321a rotates at 500 rpm. Therefore, the relative rotational speed Δω between the second-speed second clutch ring dog 34c and the second dog 321a is 500 rpm. In this state, an upshift command to the second speed is output.

  When the dog relative position Δθ reaches the shift start position Δθ * at time t1, a command for causing the shift actuator 30 to operate the second shift fork 32 to reach the shift speed Vs is output. As a result, as shown in the region (b) of FIG. 6 and FIG. 7 (b), the rotational speed of the second clutch ring dog 34c for the second speed gradually decreases as the shift speed increases (in FIG. 7B). (Represents 800 rpm).

  At time t2, when the second speed second clutch ring dog 34c reaches the predetermined axial engagement position and the relative position Δθ becomes 0, the second dog 321a and the second speed second clutch ring dog 34c are engaged. At this time, as shown in FIG. 7 (c), the second clutch ring dog 34c for 2nd speed is 600 rpm, the second dog 321a is 500 rpm, and the target relative rotational speed Δω * = 100 rpm. Thereby, it can mesh in the state in which the relative speed of both dogs was suppressed. Thereafter, as shown in region (c) of FIG. 6, the rotation speed of the second clutch ring dog 34c for the second speed is reduced to 500 rpm at a stroke.

  When the dogs are completely engaged at time t3, as shown in FIG. 7 (d), the rotation speed of the first dog 311a is reduced to 500 rpm, and therefore, between the first clutch ring dog 33c for the first speed. A coasting torque is generated, and the first clutch ring dog 33c for the first speed is moved in the disengagement direction by the coasting torque, and the seamless shift is completed.

As described above, the effects listed below are obtained in the first embodiment.
(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) fixed to the second shaft 302 (or supported so as to be relatively rotatable) and always meshed with the first-speed drive gear 311 and a second-speed driven gear 322 always meshed with the second-speed drive gear 321 (second high-speed) Gear),
A first clutch ring dog 33c for first speed 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. A V-shaped groove 401 of the first clutch ring cam 400 that moves to the axial engagement release side when torque is applied from the first dog 311a to the first speed first clutch ring dog 33c. A first clutch ring 33 (low speed clutch ring) having a first guide projection 33b (low speed side guide portion);
The second clutch ring dog 34c for the second speed meshing with the second dog 321a (the dog of the high-speed 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. A V-shaped groove 501 of the second clutch ring cam 500 that moves to the axial meshing release side when torque is applied from the second dog 321a to the second clutch ring dog 34c for the second speed. A second clutch ring 34 (high speed clutch ring) having a guide second protrusion 34b (high speed side guide portion);
A first shift fork 31 capable of moving the first clutch ring 33 and the second clutch ring 34 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;
The axial movement speed of the second shift fork 32 when the second clutch ring 34 is moved to the axial meshing side in the state where the first clutch ring dog 33c for the first speed and the first dog 311a are meshed with each other, A transmission controller 3a (shift actuator control means) that speeds up as the relative rotational speed of the two dogs 321a increases;
Equipped with.

  That is, in the state where the first speed is selected, the first shaft 301 and the first speed drive gear 311 rotate integrally at the input speed of the automatic transmission, and the second shaft 302 and the second speed drive gear 321 are in the first gear ratio. Rotate integrally at a predetermined rotational speed according to The first speed first clutch ring dog 33 c and the second speed second clutch ring dog 34 c rotate integrally with the first shaft 301. At this time, the second dog 321a rotates at a lower rotational speed than the second clutch ring dog 34c for the second speed according to the gear ratio of the second speed. In this state, when the second clutch ring 34 is moved to the axial meshing side, the second clutch ring 34 is rotated by the action of the V-shaped groove 501 of the second clutch ring cam 500 and the guide second protrusion 34b. While moving in the axial direction. As the axial movement speed of the second shift fork 32 increases, the rotational speed of the second clutch ring 34 during the axial movement decreases. Therefore, the relative rotational speed between the rotational speed of the second dog 321a and the rotational speed of the second clutch ring 34 is increased by increasing the axial movement speed of the second shift fork 32 as the relative rotational speed of the second dog 321a increases. It is possible to reduce the hitting sound and the like when the second clutch ring dog 34c for the second speed meshes with the second dog 321a.

(2) The transmission controller 3a has a target relative rotational speed Δω * (for example, 100 rpm) larger than 0 set in advance, and the second speed second clutch ring dog 34c and the second dog 321a are in the axial position. The shift speed Vs (axial movement speed) is set so that the relative rotational speed Δω between the second dog 321a and the second-speed second clutch ring dog 34c at the initial position in the axial direction at which they start to coincide with the target relative rotational speed Δω *. ) Is calculated.
Therefore, the second speed second clutch ring dog 34c and the second dog 321a can be engaged with each other while the relative rotational speed is suppressed, and a hitting sound or the like at the time of engagement can be suppressed. That is, if the target relative rotational speed Δω * is set to 0, the second-speed second clutch ring dog 34c may be moved in the axial direction before the two mesh with each other. Then, the second-speed second clutch ring dog 34c and the second dog 321a mesh with each other in a state in which the axial movement for reducing the relative rotational speed cannot be performed, and mesh with each other after reaching a high relative rotational speed. . This is because the striking sound and shock accompanying the engagement cannot be suppressed.

(3) The gear-side dog rotation position θg of the second dog 321a (the rotation direction position of the dog of the high-speed relative rotating body) and the clutch-side dog rotation position θc of the second-speed second clutch ring dog 34c (high-speed clutch ring dog) A dog relative position calculation unit 114 (rotation direction relative position detection means) for detecting a dog relative position Δθ (rotation direction relative position) to
Based on the shift speed Vs, the transmission controller 3a is an axial position between the axial bottom position where the second-speed second clutch ring dog 34c is most moved to the axial meshing side and the axial initial position. The shift start position Δθ * at which the second gear second clutch ring dog 34c and the second dog 321a start to mesh is calculated, and the second position is detected when the detected dog relative position Δθ reaches the shift start position Δθ *. The shift fork 32 starts to move.
Therefore, both dogs can be engaged with each other in a state where the relative rotational speed is suppressed while avoiding the non-entry area.

(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. For example, in the first embodiment, an example in which a drive gear that is a relative rotating body is arranged on the first shaft 301 and a dog clutch mechanism that can selectively fix the drive gear to the first shaft 301 is provided. The first shaft 301 may be provided on the second shaft 302, or may be set to both the first shaft 301 and the second shaft 302 in combination.
Further, the present invention can be applied not only to the fourth forward speed but also to the second forward speed and further automatic transmissions with multiple stages.
Further, in explaining the operation, the upshift from the first speed to the second speed has been illustrated, but the present invention can be similarly applied to other upshifts, and can also be applied to a downshift.

DESCRIPTION OF SYMBOLS 1 Engine 1a Engine output shaft 2 Clutch 3 Automatic transmission 3a Transmission controller 30 Shift actuator 31 First shift fork 32 Shift fork 33 First clutch ring 33a First sleeve 33b Guide first protrusion 33c First speed first clutch ring Dog 33c1 Inclined surface 33d 3rd speed first clutch ring dog 33e Cylindrical member 34 Second clutch ring 34a Second sleeve 34b Guide second protrusion 34c 2nd speed second clutch ring dog 34d 4th speed second clutch ring dog 34e Cylindrical member 101 Clutch ring dog position detection sensor 102 Gear dog position detection sensor 103 Shaft rotation speed detection sensor 301 First shaft 302 Second shaft 311 First speed drive gear 311a First dog 312 First speed driven gear 321 Second speed dog Eve gear 321a Second dog 322 Second speed driven gear 400 First clutch ring cam 401 V-shaped groove 401a First speed side inclined groove 401b, 401d Holding groove 401c Third speed side inclined groove 500 Second clutch ring cam 501 V-shaped groove 501a Second speed side Inclined grooves 501b, 501d Holding groove 501c Fourth-speed inclined groove DG1 First dog clutch mechanism DG2 Second dog clutch mechanism

Claims (2)

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 fixed to the second shaft or supported so as to be relatively rotatable, and a second low-speed gear that always meshes with the first low-speed gear; and a second high-speed gear that always meshes with the first high-speed gear;
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 movement toward the axial meshing side; A low-speed clutch ring having a low-speed side guide portion that moves to an axial meshing release side when torque is applied from the dog to the low-speed clutch ring dog;
A high-speed clutch ring dog that meshes with a 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 axial meshing side; A high-speed clutch ring having a high-speed side guide portion that moves to an axial engagement release side when torque acts on the high-speed clutch ring dog from a dog;
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;
The axial movement speed of the shift actuator when the high speed clutch ring is moved to the axial meshing side in a state where the low speed clutch ring dog and the dog of the low speed side relative rotating body are meshed with each other is the high speed side relative rotation. Shift actuator control means for speeding up as the relative rotational speed of the body with the high-speed clutch ring increases,
Bei to give a,
The shift actuator control means has a preset target relative rotational speed greater than 0, and the high-speed clutch ring dog and the dog of the high-speed side relative rotating body start to overlap at the axial position at the axial initial position. Calculating the axial movement speed such that the relative rotational speed of the high-speed relative rotating body and the high-speed clutch ring matches the target relative rotational speed;
A control device for an automatic transmission. The control apparatus for an automatic transmission according to claim 1,
A rotation direction relative position detection means for detecting a rotation direction relative position between a rotation direction position of the dog of the high speed side relative rotation body and a rotation direction position of the high speed clutch ring dog;
The shift actuator control means is an axial position between the axial bottom position where the high-speed clutch ring dog has moved most to the axial meshing side and the axial initial position based on the axial movement speed. Calculating a shift start position where the high-speed clutch ring dog and the dog of the high-speed side relative rotating body start meshing, and when the detected rotational relative position reaches the shift start position, Start moving,
A control device for an automatic transmission.

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