JP2015140851A - Dog clutch device for automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dog clutch device for an automatic transmission which can perform a quick gear change operation when moving a sleeve and making the sleeve engaged with a dog clutch at a gear change.SOLUTION: A control device 10 comprises: a first thrust load addition part 10c1 which adds a first thrust load for advancing a sleeve 36 to an axial direction by a shaft dynamic device 40 in order to make the sleeve engaged with a clutch ring 30; a co-rotation determination part 10b4 which determines a co-rotation state of high teeth 36a1 and clutch front teeth 30b1; a second thrust load addition part 10c2 which adds a second thrust load which is small in a load value when co-rotation is determined by the co-rotation determination part; a co-rotation release determination part 10b5 which determines whether or not the high teeth and the clutch front teeth are released from the co-rotation state; and a first thrust load re-addition part 10c3 which adds the first thrust load once again when the co-rotation release determination part determines the release.

Description

  The present invention relates to a dog clutch device used in an automatic transmission for a vehicle.

  2. Description of the Related Art Conventionally, in a power train of a vehicle, a transmission that converts torque and rotational speed in order to transmit rotation and torque from a driving device such as an engine and an electric motor used for driving to a driving wheel according to a traveling state. Is provided. There are several types of transmissions, for example, a plurality of idler gears that are fitted relative to a rotating shaft connected to a drive wheel and that are immovable in the direction of the rotating axis and are provided in parallel to the rotating shaft. There is known a constant meshing type in which a plurality of gears provided around the counter shaft are always meshed. This is because a sleeve spline-fitted to the rotation shaft so as to be movable in the direction of the rotation axis is juxtaposed with the idler gear, and the engagement teeth (splines) provided on the joint surface of the sleeve to the idler gear are idled. Is engaged with engaged teeth (dog clutch teeth) provided on the surfaces to be joined, and the engaged idle gear and the rotating shaft are rotated together. Then, the rotating gear that rotates integrally with the rotating shaft and the counter shaft gear that meshes with the rotating gear rotate in conjunction with each other, thereby transmitting the torque and the rotational speed of the rotating shaft to the counter shaft. Of the plurality of freewheeling gears having different numbers of teeth, a freewheeling gear that rotates integrally with the rotating shaft is selected and engaged with the sleeve to perform a shifting operation. Then, the engagement between the sleeve and the idle gear may not be successful depending on the timing of pressing the sleeve against the idle gear.

  In order to engage well in such a case, Patent Document 1 discloses that when the sleeve cannot be engaged with the idle gear, the torque that has pressed the sleeve against the idle gear is temporarily reduced, and then the torque is increased again. It is supposed to be pressed to the idle gear side.

  According to this, when the sleeve cannot be engaged with the idler gear, only the engaging operation is executed again, so that both can be engaged without re-starting the shifting operation itself from the beginning.

  According to Patent Document 2, when a shift to a desired shift position cannot be performed, the shift change output is turned off for a predetermined time. After that, the shift change output is turned on again. As a result, sufficient time required for switching the hydraulic pressure switching valve can be obtained, and a shift can be surely performed at the time of retry, thereby improving operability.

Japanese Patent No. 3709955 JP-A-6-50413

  However, in the speed change control method disclosed in Patent Document 1, a timer is used to determine that the sleeve cannot be engaged with the dog clutch of the idle gear. When it does not reach, re-entry control is performed to re-engage the sleeve with the idler gear. Therefore, it is necessary to set the entry control end time before re-entry by the timer to a value equal to or longer than the time for normally moving to a predetermined position (the time for the sleeve to engage without being hit by the dog clutch). As a result, when it is determined that the sleeve cannot be engaged with the dog clutch of the idle gear, the dog is already pressed against the sleeve, and the differential rotational speed between the sleeve and the idle gear becomes very small. It takes time to the position where it can be done, or it takes a long time until it is engaged and engaged next time. In this way, there is a risk that the shift time may take a long time.

  In the electronic shift device disclosed in Patent Document 2, when the shift to the desired shift position cannot be performed (when the shift cannot be engaged), the shift change output is turned off and waits for a predetermined time, and then the shift change output is turned on again. The timer is used to make it. Since the timer waits until the retry counter counts up, it takes time to determine that the sleeve cannot be engaged with the dog clutch, and there is a possibility that the shift time may be long.

  The present invention has been made in view of the above-described problems, and provides a dog clutch device for an automatic transmission that enables a quick shift operation by shortening a determination time when the sleeve cannot be engaged with the dog. With the goal.

  In order to solve the above-mentioned problem, the structural feature of the invention according to claim 1 is that a rotating shaft that is rotatably connected to one of an input shaft and an output shaft of an automatic transmission and is rotatably supported about an axis line, and the rotation A clutch ring rotatably supported on a shaft and rotationally connected to the other one of the input shaft and the output shaft, and provided on the rotating shaft adjacent to the clutch ring, the relative rotation with respect to the rotating shaft is restricted, and the axial direction A sleeve that is movably fitted to the clutch ring, an axial movement device that moves the sleeve in the axial direction between a neutral position where the sleeve does not contact the clutch ring and an engagement position where the sleeve is engaged with the clutch ring, and the clutch ring An engaged tooth that protrudes toward the sleeve and engages and disengages with an engaging tooth provided on the sleeve in accordance with the axial movement of the sleeve, the axial direction of the sleeve A stroke position sensor for detecting a moving position, and a rotation speed detection sensor for detecting the rotation speeds of the sleeve and the clutch ring, respectively. The engaged teeth are formed from the front end surface of the engaged teeth at a position where the outer diameter of the clutch is larger than the inner diameter of the high teeth and smaller than the inner diameter of the low teeth. The clutch rear teeth that extend to the rear end position of the engaged teeth and can mesh with the tooth grooves of the engagement teeth are retracted from the front end surface of the engaged teeth by a predetermined amount. A dog clutch transmission mechanism that extends to the rear end position of the engagement tooth, and a shaft that controls the operation of the shaft driving device based on the detection position of the stroke position sensor and the axial movement speed of the sleeve The directional motion control unit and the sleeve A first thrust load adding portion for applying a first thrust load to the sleeve by the axial movement device, the high teeth, and the clutch front teeth, in order to advance in the direction and engage the sleeve with the clutch ring; A rotation determination unit that determines whether or not the rotation is performed in a rotation state, and a load value that is applied to the sleeve by the axial movement device based on the first thrust load when the rotation determination unit determines that the rotation is in the rotation state. A second thrust load adding portion for applying a second thrust load having a small diameter, and an open position where the high teeth move relative to the clutch front teeth in the circumferential direction after the second thrust load is applied and are detached. When the follow-up / leave determination unit and the follow-up / leave determination unit determine that the high teeth are located at the open position with respect to the clutch front teeth. And a first thrust load re-addition part for re-adding the first thrust load to the sleeve by the axial movement device.

  According to this, when the accompanying determination unit determines that the high teeth and the clutch front teeth are in the accompanying state, the second thrust load having a smaller load value than the first thrust load is generated from the first thrust load that advances the sleeve in the axial direction. By changing to and adding, the revolving state is canceled, and the relative movement speed in the circumferential direction between the high teeth and the clutch front teeth is increased. When the high teeth and the front teeth of the clutch move from the revolving state where the high teeth come into contact with the front teeth of the clutch and move relative to each other in the circumferential direction, they are located at the release position where they are separated from the revolving state. Is determined, the high thrust is caused to enter between the front teeth of the clutch by applying the first thrust load again. As described above, the high gear and the front teeth of the clutch are separated from the revolving state, so that a quick shifting operation can be performed.

  The invention according to claim 2 is characterized in that chamfered portions are formed on both sides of the front end surface of the clutch front teeth in the circumferential direction, and the follow-up separation determining portion is configured such that the sleeve is earlier than the clutch ring. When synchronizing the rotation of the sleeve and the clutch ring from the rotating state, after the second thrust load is applied by the second thrust load adding portion, the sleeve and the clutch ring are relatively moved in the circumferential direction. The first standby required to move a distance obtained by subtracting the circumferential width of one of the chamfered portions from the length obtained by adding the tooth width of the high teeth to the tooth width of the front teeth of the clutch. When the time elapses, it is determined that the high teeth are located in the disengaged position with respect to the clutch front teeth, and the sleeve and the clutch release from the state where the sleeve rotates slower than the clutch ring. When the second thrust load is added by the second thrust load adding portion, the sleeve and the clutch ring have a relative moving speed in the circumferential direction and the height of the clutch front teeth is increased. It is determined that when the second waiting time necessary for moving the distance corresponding to the length including the tooth width of the teeth has elapsed, the high teeth are located in the open position with respect to the clutch front teeth. 1. A dog clutch device for an automatic transmission according to 1.

  According to this, when the sleeve is rotating faster than the clutch ring and the sleeve comes into contact with the clutch ring, the rotation of the sleeve is decelerated and synchronized with the clutch ring. , The length obtained by subtracting the circumferential width of the chamfered portion of one of the front teeth of the clutch from the length obtained by adding the tooth width of the high teeth to the width of the front teeth of the clutch was increased by the reduced thrust load. The first waiting time required to move at the relative speed in the circumferential direction is calculated, and it is determined that the disengaged position has come out of the facing state where the high teeth and the front teeth of the clutch rotate with the passage of the first waiting time. .

  In this case, when the follow-up state occurs, it is considered that the front end surface of the high tooth and the front end surface of the clutch front tooth are in contact with each other at any portion.

  There is a possibility that the sleeve may come into contact with the chamfered portion in front of the clutch front teeth in the rotational direction. In this case, since the sleeve is contacted from a faster state, the front of the clutch front teeth in the rotational direction. It is considered that the sleeve enters the shaft and the sleeve advances in the axial direction between adjacent clutch front teeth.

  That is, relative to the circumferential direction starting from the position where the end of the front end surface of the high tooth in the rotational direction rearward is in contact with the front end of the front end surface of the clutch in the rotational direction, the high tooth becomes the clutch front tooth. The maximum relative movement distance required to leave the revolving state is the distance until the open position that does not face is reached. The maximum relative moving distance is a distance corresponding to a length obtained by subtracting the circumferential width of one chamfered portion of the clutch front teeth from the length obtained by adding the tooth width of the high teeth to the tooth width of the clutch front teeth. .

  In addition, when the sleeve rotates more slowly than the clutch ring and the sleeve contacts the clutch ring, the rotation of the sleeve is increased and synchronized with the clutch ring. The second waiting time required to move the distance corresponding to the length obtained by adding the tooth width of the high tooth to the tooth width of the clutch front tooth at the circumferential relative speed increased by the reduced second thrust load It is calculated, and it is determined that the release position deviates from the facing state in which the high teeth and the front teeth of the clutch rotate with the passage of the second waiting time.

  In this case, when the revolving state occurs, the front end surface of the high tooth and the front end surface of the clutch front tooth are in contact with each other at any portion, or the front end surface of the high tooth and the front end surface of the clutch are chamfered. The part is considered to be in contact with each other at any part.

  That is, starting from the position where the end portion of the front end surface of the high tooth in the rotational direction is in contact with the front end portion of the chamfered portion of the front tooth of the clutch in the rotational direction, the high tooth is engaged in the clutch. The maximum relative movement distance required to disengage from the follow-up state is reached until reaching an open position that does not face the front teeth. The maximum relative movement distance is a distance corresponding to the length obtained by adding the tooth width of the high teeth to the tooth width of the front teeth of the clutch.

  In this way, by the passage of the relative movement time (first or second waiting time) that is predicted to leave from the follow-up state, it is possible to easily and quickly determine the release from the follow-up state and enable a quick shift operation. be able to.

  The structural feature of the invention according to claim 3 is the case where the accompanying separation determination unit determines that the accompanying state of the sleeve and the clutch ring continues after the addition of the second thrust load. 2. The dog clutch device for an automatic transmission according to claim 1, further comprising a third thrust load adding portion that adds a third thrust load that reduces the second thrust load. 3.

  According to this, when it is determined that the accompanying state continues after the addition of the second thrust load, the third thrust load that further reduces the second thrust load is added. In this way, by changing the second thrust load, which is added by reducing the thrust to eliminate the revolving state, to the third thrust load, which is further reduced, it is possible to change the circumference between the high teeth and the front teeth of the clutch. The relative movement speed in the direction can be increased, and the high-tooth and the front tooth of the clutch can be quickly and reliably separated from the follow-up state in which the high-tooth and the clutch front tooth are brought together in a facing state.

  According to a fourth aspect of the present invention, in the third thrust load adding portion, the sleeve and the clutch ring are rotated by the rotation determining portion after the second thrust load is added. 4. The dog clutch device for an automatic transmission according to claim 3, which is a step-wise reduced thrust load adding portion capable of adding a step-wise reduced thrust load each time it is determined.

  According to this, when it is determined that the second thrust load, which is a reduced load in order to disengage the accompanying state, is further reduced and added, and it is determined that the accompanying state is the accompanying state at the reduced and added stage, At that stage, a further reduced thrust load is added. In this way, the thrust load is reduced and added stepwise while repeatedly confirming separation from the accompanying state, so that the accompanying state can be separated efficiently and reliably.

It is the schematic of the vehicle provided with the automatic transmission which has a dog clutch which concerns on this invention. It is a schematic diagram of an automatic transmission which has a dog clutch device concerning the present invention. It is a block diagram which shows the input / output relationship of the control apparatus shown in FIG. FIG. 3 is an exploded perspective view of the dog clutch transmission mechanism shown in FIG. 2. It is a front view of the clutch ring shown in FIG. It is a front view of the clutch hub shown in FIG. It is a front view of the sleeve shown in FIG. It is a flowchart which shows thrust load control of the axial drive which becomes a premise. It is a flowchart which shows the thrust load control which determines the detachment | leave from the accompanying state in 1st Embodiment by differential rotation. It is a flowchart which shows the thrust load control which re-adds the 1st thrust load which is common in each embodiment. It is a flowchart which shows thrust load control after detaching | leave from the accompanying state common in each embodiment. It is a figure which shows the relationship between the sleeve position (stroke) with respect to a dog clutch part and thrust load in progress of the time for gear shifting. In 2nd Embodiment, in the case where a sleeve and a clutch ring are rotationally synchronized from the state where rotation of a sleeve is earlier than rotation of a clutch ring, it is a figure which shows the positional relationship by the time passage of the high tooth with respect to a clutch front tooth. In 2nd Embodiment, it is a flowchart which shows the thrust load control which determines the separation | separation from a revolving state by the time required to move the relative distance after the reduced thrust load addition. In 3rd Embodiment, it is a figure which shows the relationship between the sleeve position (stroke) with respect to a dog clutch part and thrust load in progress of the time for gear shifting. In 3rd Embodiment, in the case where a clutch ring and a sleeve are rotationally synchronized from the state where rotation of a sleeve is slower than rotation of a clutch ring, it is a figure which shows the positional relationship by the time passage of the high tooth with respect to a clutch front tooth. In a 3rd embodiment, after adding reduced thrust load, it is a flow chart which shows thrust load control which compares the number of rotations of a sleeve with the number of rotations of a clutch ring. In 3rd Embodiment, it is a flowchart which shows the thrust load control which reduces a thrust load in steps. In the third embodiment, in the case where the sleeve and the clutch ring are rotationally synchronized from the state where the rotation of the sleeve is slower than the rotation of the clutch ring, when the thrust load F6 that is gradually reduced is added, It is a figure which shows the positional relationship by progress of time.

Example 1
Hereinafter, a first embodiment in which an automatic transmission including a dog clutch device 1 for an automatic transmission according to the present invention is applied to a vehicle will be described with reference to the drawings. FIG. 1 is a schematic diagram showing the configuration of the vehicle.

  As shown in FIG. 1, the vehicle M includes an engine 11, a clutch 12, an automatic transmission 13, a differential device 14, and drive wheels (left and right front wheels) Wfl and Wfr. The engine 11 generates driving force by burning fuel. The driving force of the engine 11 is configured to be transmitted to the driving wheels Wfl and Wfr via the clutch 12, the automatic transmission 13, and the differential device 14 (so-called FF vehicle).

  The clutch 12 is configured to be automatically connected and disconnected in response to a command from a control device (ECU) 10. The automatic transmission 13 incorporates a dog clutch transmission mechanism and automatically selects, for example, six forward speeds and one reverse speed. The differential device 14 includes both a final gear and a differential gear, and is formed integrally with the automatic transmission 13.

  As shown in FIG. 2, the automatic transmission 13 includes a housing 22, an input shaft (rotary shaft) 24, a first input gear 26, a second input gear 28, a third clutch ring (third input gear) 30, a fourth Clutch ring (fourth input gear) 32, clutch hub (hub) 34, sleeve 36, stroke position sensor 38, shaft movement device 40, output shaft (output shaft) 42, first clutch ring (first output gear) 44, A second clutch ring (second output gear) 46, a third output gear 48 and a fourth output gear 50 are included. Then, a first dog clutch speed change is made by a first clutch ring (first output gear) 44, a second clutch ring (second output gear) 46, a clutch hub (hub) 34, a sleeve 36, an axial gear (not shown), and the like. A mechanism is configured, and a third clutch ring (third input gear) 30, a fourth clutch ring (fourth input gear) 32, a clutch hub (hub) 34, a sleeve 36, a stroke position sensor 38, an axial movement device 40, etc. Thus, the second dog clutch transmission mechanism is configured. The automatic transmission dog clutch device 1 is constituted by the first and second dog clutch transmission mechanisms and the control device 10 and the like.

  The housing 22 includes a main body 22a formed in a substantially bottomed cylindrical shape, a first wall 22b that is a bottom wall of the main body 22a, and a second wall 22c that divides the main body 22a in the left-right direction.

  The input shaft 24 is rotatably supported by the housing 22. That is, one end (left end) of the input shaft 24 is supported by the first wall 22b via the bearing 22b1, and the other end (right end) side of the input shaft 24 is supported by the second wall 22c via the bearing 22c1. The other end of the input shaft 24 is rotationally connected to the output shaft of the engine 11 via the clutch 12. Therefore, the output of the engine 11 is input to the input shaft 24 when the clutch 12 is connected. The input shaft 24 is the rotating shaft of the present invention. Note that the input shaft (rotary shaft) 24 in the present embodiment is directly connected to the input shaft of the automatic transmission 13 and is rotationally connected, and is rotatably supported about the axis SCL.

  The input shaft 24 is provided with a first input gear 26, a second input gear 28, a third clutch ring (third input gear) 30, and a fourth clutch ring (fourth input gear) 32. The first and second input gears 26 and 28 are fixed so as not to rotate relative to the input shaft 24 by spline fitting or the like. The third input gear is formed on the outer periphery of the third clutch ring 30 that is rotatably supported with respect to the input shaft 24. The fourth input gear is formed on the outer periphery of the fourth clutch ring 32 that is rotatably supported with respect to the input shaft 24. Further, a clutch hub (hub) 34 is fixed to the input shaft 24 between the third clutch ring 30 and the fourth clutch ring 32 so as not to be relatively rotatable by spline fitting or the like. The third input gear (third clutch ring) 30 meshes with a third output gear described later, and the fourth input gear (fourth clutch ring) 32 meshes with a fourth output gear described later.

  A rotation speed detection sensor 39 is provided in the vicinity of the input shaft 24 and detects the rotation speed of the sleeve 36 from the rotation speed of the input shaft 24.

  The housing 22 is provided with an output shaft 42 in parallel with the input shaft 24. The output shaft (output shaft) 42 is rotatably supported by the housing 22. That is, one end (left end) of the output shaft 42 is supported by the first wall 22b via the bearing 22b2, and the other end (right end) of the output shaft 42 is supported by the second wall 22c via the bearing 22c2.

  The output shaft 42 is provided with a first clutch ring (first output gear) 44, a second clutch ring (second output gear) 46, a third output gear 48, a fourth output gear 50, and a fifth output gear 52. ing. The first clutch ring (first output gear) 44 meshes with the first input gear 26, and a helical gear that meshes with the first input gear 26 is formed on the outer peripheral surface. The second clutch ring (second output gear) 46 meshes with the second input gear 28, and a helical gear that meshes with the second input gear 28 is formed on the outer peripheral surface. The third output gear 48 meshes with the third clutch ring (third input gear) 30, and a helical gear that meshes with the third clutch ring (third input gear) 30 is formed on the outer peripheral surface. The fourth output gear 50 meshes with the fourth clutch ring (fourth input gear) 32, and a helical gear that meshes with the fourth clutch ring (fourth input gear) 32 is formed on the outer peripheral surface. The fifth output gear 52 meshes with an input gear (not shown) of the differential device 14, and a helical gear that meshes with the input gear is formed on the outer peripheral surface.

  In the vicinity of the output shaft 42, a rotational speed detection sensor 49 made of, for example, a rotary encoder is provided. By detecting the rotational speed of the output shaft 42, the rotational speed of the third clutch ring 30 and the like in the input shaft 24 is detected. .

  A clutch hub (hub) 34 is fixed to the output shaft 42 between the first clutch ring 44 and the second clutch ring 46 by spline fitting or the like. The configurations of the first clutch ring 44, the second clutch ring 46, the clutch hub 34, and the like are the same as those of the third clutch ring 30, the fourth clutch ring 32, and the clutch hub 34 in the input shaft 24, and thus the description thereof is omitted. The third output gear 48, the fourth output gear 50, and the fifth output gear 52 are fixed to the output shaft 42 by spline fitting or the like. The driving force of the engine 11 is input from the input shaft 24, transmitted to the output shaft 42, and finally output to the differential device 14 via the fifth output gear 52.

  Since the second dog clutch transmission mechanism of the input shaft 24 and the first dog clutch transmission mechanism of the output shaft 42 have the same configuration, the second dog clutch transmission mechanism of the input shaft 24 will be described as a representative.

  A clutch hub 34 is supported on the input shaft 24 so as to be integrally rotatable by spline fitting (not shown). As shown in FIGS. 4 and 6, the clutch hub 34 has a fitting hole for fitting with the input shaft 24 and is formed in a flat cylindrical shape, and spline teeth 34 a are formed on the outer peripheral surface of the clutch hub 34. ing. Twelve spline teeth 34a are formed at the same pitch in the circumferential direction, and each spline tooth 34a is formed with the diameter of the same tip circle. The diameters of the root circles of the spline teeth 34a are all the same so that the high teeth 36a1 and the low teeth 36a2 of the sleeve 36 become meshing grooves 34a1 having a depth that allows meshing together. The inner teeth (splines) 36a of the sleeve 36 are slidably engaged with the spline teeth 34a of the clutch hub 34.

  The sleeve 36 is formed in a substantially annular shape, and an outer peripheral groove 36b is formed on the outer periphery of the sleeve 36 in a circumferential direction in which a shift fork 40a (see FIG. 2) of the axial movement device 40 is slidably engaged. As shown in FIGS. 4 and 7, the inner teeth 36 a formed on the inner periphery of the sleeve 36 are formed with the same diameter of the root circle and a total of twelve teeth at the same pitch in the circumferential direction. ing. The internal teeth 36a are provided with high teeth 36a1 and low teeth 36a2 having different tooth heights, and a pair of high teeth 36a1 having a high tooth height are formed to face each other at 180 degrees on the circumference. The other ten low teeth 36a2 have the same height and are lower than the high teeth 36a1. An end surface (front end surface 36a4) of the sleeve 36 facing the third and fourth clutch rings 30 and 32, which is perpendicular to the axis SCL of the high teeth 36a1 and the low teeth 36a2, has a front and rear angle. A chamfered surface 36a3 of 45 degrees with respect to the rotation direction is formed (see FIG. 7). Thus, the corners are not lost due to the impact of the third and fourth clutch rings 30 and 32 with the dog clutch teeth described later. A tooth gap 36a5 is formed between the adjacent high teeth 36a1 and the low teeth 36a2 and between the adjacent low teeth 36a2. A clutch front tooth 30b1 and a clutch rear tooth 30b2 of a third clutch ring 30 to be described later are fitted into these tooth grooves 36a5. The high teeth 36 a 1 and the low teeth 36 a 2 of the sleeve 36 are engaged with the meshing grooves 34 a 1 of the clutch hub 34.

  The input shaft 24 is provided with a third clutch ring 30 and a fourth clutch ring 32 on both sides adjacent to the clutch hub 34. The third clutch ring 30 and the fourth clutch ring 32 have corresponding dog clutch portions that are substantially symmetrical with respect to the clutch hub 34, and therefore the third clutch ring 30 will be described as a representative.

  As shown in FIGS. 4 and 5, the third clutch ring 30 is provided on the input shaft 24 via a bearing (not shown) so as to be relatively rotatable and immovable in the direction of the axis SCL (see FIG. 2). . The third input gear formed on the outer peripheral surface of the third clutch ring 30 constitutes an idle gear that rotates relative to the input shaft 24 so as to be freely rotatable. A ring-shaped third dog clutch portion 30 a is formed on the surface (meshing portion) of the third clutch ring 30 facing the clutch hub 34. A plurality of dog clutch teeth 30b that mesh with the inner teeth 36a of the sleeve 36 are formed on the outer periphery of the third dog clutch portion 30a. The dog clutch tooth 30b includes two types of clutch front teeth 30b1 and clutch rear teeth 30b2 having different tooth heights. Further, the dog clutch teeth 30b have the same root circle diameter and are formed at the same pitch in the circumferential direction. A pair (two) of clutch front teeth 30b1 are provided at opposing positions that rotate 180 degrees in the circumferential direction. The clutch front teeth 30b1 are formed such that the outer diameter of the tip circle is larger than the inner diameter of the tip circle of the high tooth 36a1 of the sleeve and smaller than the inner diameter of the tip circle of the low tooth 36a2. The clutch front teeth 30b1 are formed to extend from the front end face FE of the third dog clutch portion 30a constituting the meshing portion to the rear end position RE of the third dog clutch portion 30a in the axis SCL direction. On both side surfaces 30b9 of the clutch front teeth 30b1 on the sleeve 36 side, chamfered portions 30b3 inclined by 45 degrees from the rotational direction are formed. When the sleeve 36 approaches the third clutch ring 30 while relatively rotating, the clutch front teeth 30b1 engage with the high teeth 36a1 of the sleeve 36 and do not engage with the low teeth 36a2. The front end portion of the clutch front teeth 30b1 is configured by the front end surface 30b5 and the chamfered portion 30b3 on the sleeve 36 side of the clutch front teeth.

  As shown in FIGS. 4 and 5, a total of ten clutch rear teeth 30b2 are arranged at the phase position between the two clutch front teeth 30b1, and the outer diameter of each tip circle is lower than that of the sleeve 36. It is formed larger than the inner diameter of the tip circle of the tooth 36a2. The clutch rear teeth 30b2 extend from the position retracted by a predetermined amount t from the sleeve 36 side in the axis SCL direction from the front end face FE of the third dog clutch part 30a constituting the meshing part to the rear end position RE of the third dog clutch part 30a. Formed. On both side surfaces 30b7 of the clutch rear teeth 30b2 on the sleeve 36 side, chamfered portions 30b4 inclined by 45 degrees in the rotational direction are provided. When the sleeve 36 approaches the third clutch ring 30 while rotating relatively, when the high teeth 36a1 and the low teeth 36a2 enter the position where the third clutch ring 30 is retracted by the predetermined amount t, the clutch rear teeth 30b2 The high teeth 36a1 and the low teeth 36a2 are engaged. By engaging the clutch rear teeth 30b2 with the high teeth 36a1 and the low teeth 36a2 of the sleeve, a large rotational torque is transmitted safely and reliably.

  As the stroke position sensor 38, for example, various position sensors such as an optical position sensor and a linear encoder are used. The relative position between the sleeve 36 and the third clutch ring 30 is detected and each stop position of the shift detent mechanism 58 is detected.

  As shown in FIG. 3, the control device 10 includes a storage unit 10a, a calculation unit 10b, and a control unit 10c. The tip of the sleeve 36 (the front end surface 36a4 of the high teeth 36a1) detected by the stroke position sensor 38 is the first one. Relative position (first stroke position) of the third dog clutch part 30a with respect to the front end face FE (fifth stroke position), relative position with respect to the chamfered part 30b3 of the third dog clutch part 30a (first stroke position), and relative position (first position) with respect to the front end part of the clutch rear teeth 30b2. (4 stroke position) and a relative position signal (third stroke position) with respect to the rear end position RE of the dog clutch portion 30a, etc., and the thrust load values F1 to F6 of the linear actuator 40i for driving the shaft driving device 40 and the high The movement position of the front end surface 36a4 of the tooth 36a1 is controlled.

  Further, based on the data detected by the sleeve rotation speed detection sensor 39 and the clutch ring rotation speed detection sensor 49, the sleeve 36 (high teeth 36a1) and the third clutch ring 30 (clutch front teeth 30b1) in the circumferential direction are relative to each other. The speed is calculated by the calculation unit 10b, which will be described later, and the relative positions of the high teeth 36a1, the clutch front teeth 30b1, and the circumferential direction can be estimated based on the detected position in the axial direction by the stroke position sensor 38 and the like. Based on the relative position estimated in the circumferential direction, a reduced thrust load (relative rotation securing thrust load) F5 or F6, which will be described later, is controlled.

  The calculation unit 10b includes a circumferential speed calculation unit 10b1, a first standby time calculation unit 10b2, a second standby time calculation unit 10b3, a accompanying calculation unit 10b4, and a accompanying removal calculating unit 10b5.

  The circumferential speed calculation unit 10b1 determines the circumferential direction between the high teeth 36a1 and the clutch front teeth 30b1 based on the diameter of the sleeve 36, the diameter of the third clutch ring 30, the rotational speed of the sleeve 36, and the rotational speed of the third clutch ring 30. Calculate the relative speed.

  When the sleeve 36 and the third clutch ring 30 are rotationally synchronized from the state in which the rotational speed of the sleeve 36 is higher than the rotational speed of the third clutch ring 30, the first standby time calculation unit 10 b 2 The maximum relative movement distance at which the facing state between the high teeth 36a1 and the clutch front teeth 30b1 can be eliminated when the state where 36a1 faces and abuts against the clutch front teeth 30b1 of the third clutch ring 30 and a co-rotating state is generated. ML1 is calculated as a first waiting time (Ta, Ta ′), which is the time for relative movement.

  When the sleeve 36 and the third clutch ring 30 are rotationally synchronized from the state in which the rotational speed of the sleeve 36 is slower than the rotational speed of the third clutch ring 30, the second standby time calculation unit 10 b 3 Facing the abutting clutch front teeth 30b1 of the third clutch ring 30 and generating a revolving state where they rotate together, the maximum relative movement distance ML2 at which the facing state between the high teeth 36a1 and the clutch front teeth 30b1 can be eliminated. Is calculated as the second waiting time Tb.

  The follow-up calculating unit 10b4 calculates, for example, the positions of the high teeth 36a1 and the clutch front teeth 30b1 and the deceleration gradient of the sleeve 36 by the stroke position sensor 38, and as another example of the rotation of the sleeve 36 and the third clutch ring 30. Calculate the difference.

  The follow-up detachment calculating unit 10b5 calculates, for example, a rotation speed difference between the sleeve 36 and the third clutch ring 30 detected by the rotation speed detection sensor 49, or a first waiting time after adding a reduced thrust load. Waiting times such as Ta (first waiting time Ta ′) and second waiting time Tb are calculated.

  The stroke position sensor 38, the sleeve rotation number detection sensor 39, the clutch ring rotation number detection sensor 49, the rotation calculation unit 10b4, and the like constitute a rotation determination unit. The stroke position sensor 38, the sleeve rotation number detection sensor 39, the clutch ring rotation number detection sensor 49, the rotation separation calculator 10b5, and the like constitute a rotation separation determination unit.

  The axial movement device 40 reciprocates the sleeve 36 along the axial direction. When the sleeve 36 is pressed against the third clutch ring 30 or the fourth clutch ring 32, the third clutch ring 30 or the second clutch ring 30 is moved. When a reaction force is applied from the four clutch ring 32, the sleeve 36 is configured to be allowed to move by the reaction force.

  The axial movement device 40 includes a fork 40a, a fork shaft 40b, and a drive device 40c. The front end of the fork 40 a is formed in accordance with the outer peripheral shape of the outer peripheral groove 36 b of the sleeve 36. The base end portion of the fork 40a is fixed to the fork shaft 40b. The fork shaft 40b is slidably supported on the housing 22 along the axial direction. That is, one end (left end) of the fork shaft 40b is supported on the first wall 22b via the bearing 22b3, the other end (right end) side of the fork shaft 40b is fixed to the bracket 40d, and the bracket 40d is axially connected to the second wall 22c. It is slidable by a guide member (rotating stopper) 40e projecting to the nut and fixed to the nut member 40f so as not to be relatively rotatable. The nut member 40f is screwed to a drive shaft 40h provided with a drive device 40c so as to be able to advance and retreat. The drive shaft 40h is supported on the second wall 22c via a bearing 22c3.

  The drive device 40c is a linear drive device that uses a linear actuator 40i as a drive source. As the linear actuator 40i, for example, there is a ball screw type linear actuator (see JP-A-11-69709). This is, for example, a housing that is formed in a cylindrical shape and in which a plurality of coils are arranged in the inner circumferential direction as a stator (not shown), and is rotatably provided with respect to the stator and is opposed to the stator by providing a magnetic gap. A rotor (not shown) in which a plurality of N-pole magnets and S-pole magnets are alternately arranged on the outer periphery, a drive shaft 40h (ball screw shaft) that rotates integrally with the rotor around the rotation axis of the stator, and a drive shaft It is comprised from the nut member 40f which consists of a ball nut screwed by 40h. The drive shaft 40h is screwed into the nut member 40f through a plurality of balls (not shown) so as to be relatively rotatable. By controlling energization to each coil of the stator, the drive shaft 40h is arbitrarily rotated in both forward and reverse directions, and the nut member 40f and the fork shaft 40b are reciprocated and positioned and fixed at arbitrary positions. Further, the drive device 40c has a long lead for the ball screw shaft, so that when a reaction force is applied from the third clutch ring 30 or the fourth clutch ring 32, the sleeve 36 is moved by the reaction force. It is configured to allow that.

  A shift detent mechanism 58 is provided in the vicinity of the first wall 22b of the fork shaft 40b. The shift detent mechanism 58 includes a lock member 62 that is biased in a direction perpendicular to the axis of the fork shaft 40b by a biasing member (coil spring) (not shown), and the lock member 62 extends along the axis of the fork shaft 40b. By being fitted into a plurality of positioning recesses (triangular grooves) 60 by spring force, the axial sliding of the fork shaft 40b can be positioned at an arbitrary position. The position of the sleeve 36 with respect to the clutch rings 30 and 32 is determined such that the spline (high teeth) 36a of the sleeve 36 does not contact the dog clutch portion 30a (clutch front teeth 30b1) of the third clutch ring 30 and the fourth clutch ring 32. 36, the spline 36a and the engagement position EP where the third clutch ring 30 or the dog clutch portion 30a of the fourth clutch ring 32 and the like are engaged with each other.

  In this embodiment, a ball screw type linear actuator is employed as the driving device. However, when the sleeve 36 is pressed against the third clutch ring 30 or the fourth clutch ring 32, the third clutch ring 30 or the fourth clutch is used. As long as the sleeve 36 is configured to be allowed to move by the reaction force when a reaction force is applied from the clutch ring 32, other drive devices such as a solenoid-type drive device and a hydraulic drive are available. It may be a device.

  Next, the operation of the above-described dog clutch device for an automatic transmission will be described below with reference to the flowcharts of FIGS. 8 to 11 and FIGS. 12 and 13. Here, for example, when shifting up, when the sleeve 36 rotates at a high speed and a small moment of inertia, and the third clutch ring 30 (third input gear) rotates at a low speed and a large moment of inertia, the sleeve 36 is decelerated. The On the other hand, if the sleeve 36 is rotated at a low speed and a small moment of inertia and the third clutch ring 30 is rotated at a high speed and a large moment of inertia during the downshift, the sleeve 36 is accelerated. In the following operation, the deceleration operation of the sleeve 36 when shifting up will be described as the first embodiment.

  First, the sleeve 36 is positioned between the third clutch ring 30 and the fourth clutch ring 32, and the spline (engagement tooth) 36 a of the sleeve 36 is any dog clutch of the third clutch ring 30 and the fourth clutch ring 32. It is positioned at a neutral position NP that is not engaged with the tooth 30b or the like. In this case, the lock member 62 of the shift detent mechanism 58 is in a state of being fitted into the neutral positioning recess 60N.

  As shown in FIG. 12, the boundary between the chamfered portion 30b3 of the clutch front tooth 30b1 of the third clutch ring 30 and the side surface 30b9 of the clutch front tooth 30b1 is defined as a first stroke position S1. A boundary side between the chamfered portion 30b4 of the clutch rear teeth 30b2 of the third clutch ring 30 and the side surface 30b7 of the clutch rear teeth 30b2 is defined as a second stroke position S2. The rear end position of the clutch rear teeth 30b2 (the rear end position RE of the third dog clutch portion 30a) is defined as a third stroke position S3. Further, the front end face 30b6 of the clutch rear teeth is set as the fourth stroke position S4. Further, the front end face 30b5 of the clutch front teeth 30b1 is set as the fifth stroke position S5.

  In FIG. 12, as the circumferential relative movement position, a position corresponding to the front end portion in the rotation direction of the front end surface 30b5 of the clutch front tooth 30b1 is Sc1, and corresponds to the side surface 30b9 on the rear side in the rotation direction of the clutch front tooth 30b1. The position to be performed is Sc2.

  The range in which the end surface (front end surface 36a4) of the high teeth 36a1 of the sleeve 36 on the third clutch ring 30 side moves is from the neutral position NP to the first stroke position S1, from the first stroke position S1 to the second stroke position S2. Thrust applied by the shaft drive device 40 in the range from the second stroke position S2 to the third stroke position S3, from the first stroke position S1 to the fourth stroke position S4, and from the first stroke position S1 to the fifth stroke position S5. The load is controlled in four stages of F1 to F5 (except for F4 that has been conventionally used) (see FIG. 12).

  In response to the shift start signal, the control device 10 applies a control current to which a predetermined thrust load is applied to the linear actuator 40i of the axial movement device 40 (step S101 in FIG. 8, hereinafter referred to as “S101”). ). By extending the drive shaft 40h by the linear actuator 40i, the fork shaft 40b is moved, and the sleeve 36 is slid to the third clutch ring 30 side by the fork 40a. The sleeve 36 approaches the third clutch ring 30 while relatively rotating by a rotational difference. At this time, the control device 10 adds a constant thrust load F1 (S102). For example, the mutual phase due to the relative rotation of the sleeve 36 and the third clutch ring 30 exceeds the thrust load F1 without the high teeth 36a1 engaging the predetermined clutch front teeth 30b1 of the third dog clutch portion 30a. After that, the high teeth 36a1 can enter between the adjacent clutch front teeth 30b1 during the time during which the third dog clutch portion 30a and the sleeve 36 further rotate and reach the next clutch front teeth 30b1. Thrust load that generates speed. Specifically, it is appropriately calculated and controlled by the outer diameter of the sleeve 36 and the third dog clutch portion 30a, the pitch of each tooth to be engaged, the relative rotational speed of the sleeve 36 and the third dog clutch portion 30a, and the like.

  The control device 10 detects the stroke position S of the high teeth 36a1 of the sleeve 36 by the stroke position sensor 38. It is determined whether or not the advance position of the front end surface 36a4 of the high teeth 36a1 is larger than the front end surface 30b5 (fifth stroke position S5) of the clutch front teeth 30b1 (S103).

  If it is determined that the stroke is larger, the routine proceeds to step 104, where it is determined whether or not the stroke position S of the high tooth 36a1 is smaller than the first stroke position S1 (S104).

  If it is determined in step 103 that the stroke position S of the high tooth 36a1 is smaller than the fifth stroke position S5, the process returns to step 102 to add the thrust load F1 to advance the high tooth 36a1 (S102). ).

  If it is determined in step 104 that the stroke position S of the high tooth 36a1 is smaller than the first stroke position S1, the process proceeds to step 105.

  If it is determined in step 104 that the stroke position S of the high tooth 36a1 is greater than the first stroke position S1, the routine proceeds to step 112. This is because the follow-up state does not occur and the possibility that the high teeth 36a1 are repelled by the clutch front teeth 30b1 and pushed back to the neutral position NP side from S1 is reduced.

  In step 105, it is determined whether or not the deceleration gradient ▽ V of the rotation speed of the sleeve 36 is larger than a predetermined threshold value ▽ Va. When it is determined that the deceleration gradient ▽ V of the rotation speed of the sleeve 36 is larger than the predetermined threshold value ▽ Va, the routine proceeds to step 107 (see FIG. 9). This is because there is a possibility that the sleeve 36 is rotated together with the third clutch ring 30 because the rotational speed of the sleeve 36 is suddenly decelerated and the stroke position S is smaller than the first stroke position S1. . In this case, for example, when the circumferential relative movement position in FIG. 12 is at Sc (the front end Sb of the high teeth 36a1 of the sleeve 36 is positioned at the chamfered portion 30b3r behind the clutch front teeth 30b1). It is.

  If it is determined in step 105 that the deceleration gradient ▽ V of the rotational speed of the sleeve 36 is smaller than the predetermined threshold value ▽ Va, the routine proceeds to step 106 (see FIG. 8), and the rotational speed of the sleeve 36 and the third clutch It is determined whether or not the differential rotation ΔR of the rotation speed of the ring 30 is larger than a predetermined differential rotation numerical value Ra. When the differential rotation ΔR between the rotational speed of the sleeve 36 and the rotational speed of the third clutch ring 30 is smaller than a predetermined differential rotational value Ra, the routine proceeds to step 107 (see FIG. 9). This is because the sleeve 36 and the third clutch ring 30 are determined to be in the accompanying state. When the differential rotation ΔR is larger than the predetermined differential rotation numerical value Ra, the routine returns to step 104 and it is repeatedly determined whether or not the stroke position S of the high tooth 36a1 is smaller than the first stroke position S1.

  In step 107, the control device 10 causes the axial load device 40 to add a thrust load F <b> 5 that is reduced from the thrust load F <b> 1 to the sleeve 36. When the high teeth 36a1 and the clutch front teeth 30b1 are in contact with each other at the end faces, the thrust load F5 is a relative rotation that reduces frictional force generated by the contact and releases the revolving state between the high teeth 36a1 and the clutch front teeth 30b1. This is the reserved thrust load.

  Next, the control device 10 determines whether or not the stroke position S in the axial direction of the high teeth 36a1 detected by the stroke position sensor 38 is smaller than the stroke position S1 (on the neutral position NP side) (S108).

  When it is determined that the axial stroke position S of the high teeth 36a1 is smaller than the stroke position S1, the routine proceeds to step 109, where the differential rotation ΔR between the rotation speed of the sleeve and the rotation speed of the third clutch ring is a predetermined value. It is determined whether or not the difference rotational value Rb is greater. Although the stroke position S in the axial direction of the high teeth 36a1 is smaller than the stroke position S1, the chamfered portion 30b3f (see FIG. 13) of the clutch front teeth 30b1 may be in a rotating state. And the third clutch ring rotation speed difference ΔR is larger than the predetermined rotation speed difference value Rb, so that it is determined that the wheel is separated from the accompanying state (on the chamfered portion 30Bb3r side). Can do. When the differential rotation ΔR is smaller than the differential rotation numerical value Rb that is a predetermined threshold value, the process returns to step 107 and the addition with the reduced thrust load F5 is continued.

  Then, when it is determined that the differential rotation ΔR between the rotational speed of the sleeve 36 and the rotational speed of the third clutch ring 30 is larger than the predetermined differential rotational value Rb, the open position in claim 1 shown in FIG. It is determined that the RP and the circumferential relative movement position Sc2 in FIG. 12 are located, the process proceeds to step 110, and the thrust load F1 that was originally added is added again (S110, FIG. 10).

  After adding the thrust load F1, the routine proceeds to step 111, where it is determined whether or not the stroke position S of the high tooth 36a1 is greater than the first stroke position S1 (is in a forward position). The high tooth 36a1 is located at a position advanced from the first stroke position S1, so that the high tooth 36a1 is released from the revolving state, and the high tooth 36a1 is repelled by the clutch front tooth 30b1 and may be pushed out to the neutral position NP side. Also lower. Therefore, the thrust load F1 is added again, but after that, by changing to the thrust load F2, generation of a follow-up state due to contact between the high teeth 36a1 and the clutch rear teeth 30b2 that are generated when the high teeth 36a1 further advance. To prevent.

  When the stroke position S of the high teeth 36a1 is larger than the first stroke position S1, the routine proceeds to step 112, where a thrust load F2 is added (FIG. 11).

  The applied thrust load F2 is between the high teeth 36a1 and the clutch rear teeth 30b2 when the end surface (front end surface 36a4) of the high teeth 36a1 and the end surface (front end surface 30b6) of the clutch rear teeth 30b2 come into contact with each other. This is a thrust load capable of ensuring relative rotation between the sleeve 36 and the third dog clutch portion 30a against the generated frictional force. As a result, it is possible to prevent a high speed gear 36a1 from moving at a relative speed with a small rotational difference (or to move around in a state in which the high teeth 36a1 are in contact with the clutch rear teeth 30b2), thereby realizing a rapid speed change operation.

  After that, whether the stroke position S of the high teeth 36a1 is larger than the second stroke position S2 that is the boundary between the chamfered portion 30b4 of the clutch rear teeth 30b2 and the side surface 30b7 of the clutch rear teeth 30b2 (is it in the advanced position)? It is determined whether or not (S113). When it is determined that the stroke position S of the high teeth 36a1 is larger than the second stroke position S2, the process proceeds to step 114, and a thrust load F3 is added (S114, FIG. 11).

  The added thrust load F3 resists the friction force generated between the high teeth 36a1 and the low teeth 36a2 and the clutch front teeth 30b1 and the clutch rear teeth 30b2 when the sleeve 36 is slid to the third clutch ring 30. This is a thrust load that allows the inner teeth (splines) 36a of the sleeve 36 to enter the dog clutch teeth 30b. The high load 36a1 is inserted between the clutch front tooth 30b1 and the clutch rear tooth 30b2 by being guided by the side surface 30b9 of the clutch front tooth 30b1 by the thrust load of F3.

  When the sleeve 36 is moved to the third clutch ring 30 side, the high teeth 36a1 do not use the side surface 30b9 of the clutch front teeth 30b1 as a guide, and any of the tooth grooves 30b8, 30b10 of the dog clutch teeth 30b (see FIG. 5). However, when the high teeth 36a1 (and the low teeth 36a2) try to fit into the tooth gap 30b8 between the clutch rear teeth 30b2, the inter-tooth distance between the adjacent clutch rear teeth 30b2 is short. It is considered that the clutch rear teeth 30b2 are often repelled. Therefore, in order to quickly mesh the high teeth 36a1 with the dog clutch teeth 30b, it is effective to guide the high teeth 36a1 with the side surface 30b9 of the clutch front teeth 30b1 and insert the high teeth 36a1 into the tooth gap 30b10 adjacent to the clutch front teeth 30b1. it is conceivable that.

  When it is determined in step 113 that the stroke position S has not reached the second stroke position S2, the process returns to step 112, and the stroke position S is detected with the relative rotation securing thrust load F2 added. repeat.

  Further, when the sleeve 36 is moved closer to the third clutch ring 30, it is detected by the stroke position sensor 38 that the front end surface 36a4 of the high teeth 36a1 has reached the third stroke position (rear end position RE) S3. (S115), the control device 10 determines that the sleeve 36 and the third clutch ring 30 are completely engaged with each other, and stops adding the thrust load by the shaft drive device 40 (S116). At this time, the low teeth 36a2 of the sleeve 36 mesh simultaneously with all the dog clutch teeth 30b including the clutch rear teeth 30b2 of the third clutch ring 30.

  When it is not detected that the front end surface 36a4 of the high teeth 36a1 has reached the third stroke position (rear end position RE) S3, the process returns to step 114 and the addition of the thrust load F3 is continued.

  As apparent from the above description, according to the dog clutch control device 10 for the automatic transmission according to the first embodiment, the control device 10 includes the high teeth 36a1 of the sleeve 36 and the third clutch front teeth 30b1 of the third clutch ring 30. Is determined to be in the accompanied state, the first thrust load F1 that advances the sleeve 36 in the axial direction is changed to the second thrust load F5 that is smaller in load value than the first thrust load, and the accompanying state is changed. It cancels and the relative moving speed of the circumferential direction of the high tooth 36a1 and the 3rd clutch front tooth 30b1 is increased. When the accompanying separation determination unit determines that the high tooth 36a1 and the third clutch front tooth 30b1 are located at the open position RP where the high tooth 36a1 and the third clutch front tooth 30b1 are separated from the accompanying state by moving relative to each other, the first thrust load again. By adding F1, the high teeth 36a1 are caused to enter between the adjacent third clutch front teeth 30b1. In this way, the high gear 36a1 and the clutch front tooth 30b1 can be separated from the accompanying state, thereby enabling a rapid speed change operation.

(Example 2)
Next, a second embodiment in which an automatic transmission having a dog clutch device for an automatic transmission according to the present invention is applied to a vehicle will be described with reference to FIGS.
Since the configuration of the automatic transmission including the dog clutch device for an automatic transmission in the present embodiment is the same as that of the first embodiment, the description thereof is omitted.

  In the present embodiment, the determination method as to whether or not the high teeth 36a1 has reached the open position RP where the high teeth 36a1 leave the revolving state in the revolving state of the high teeth 36a1 of the sleeve 36 and the clutch front teeth 30b1 of the third clutch ring 30. This is different from the first embodiment.

  More specifically, when it is determined that the high teeth 36a1 and the clutch front teeth 30b1 are in the accompanying state, the process continues to step 105 or step 106 (see Example 1), and it is determined to be in the accompanying state. Then, the process proceeds to step 201 (see FIG. 14), and the timer T is activated and starts counting (S201).

  Next, the routine proceeds to step 202, where the reduced thrust load F5 is added. Next, when it is determined that the stroke position S of the high tooth 36a1 is smaller than the first stroke position S1 (close to the neutral position NP) with the thrust load F5 applied, the routine proceeds to step 204.

  In step 204, it is determined whether the first waiting time Ta has elapsed. The first standby time Ta is a time estimated that the high teeth 36a1 and the clutch front teeth 30b1 that have become in the following state move relative to each other in the circumferential direction to reach the release position RP. For example, as shown in FIG. 13, after the rear end Sa located at the rear in the rotational direction of the high teeth 36 a 1 contacts the front end Ca at the front in the rotational direction of the front end surface 30 b 5 of the clutch front teeth 30 b 1, This is the time until the front end Sb in the rotational direction of the high teeth 36a1 passes through the rear outer end Cp2 of the chamfered portion 30b3r of the clutch front teeth 30b1 and is positioned at the open position RP. For example, the maximum relative movement distance ML1 obtained by subtracting the circumferential length CC of the chamfered portion 30b3 from the value obtained by adding the tooth width SW of the high teeth 36a1 and the tooth width CW of the clutch front teeth 30b1 is the rotation of the sleeve 36. The number of rotations of the third clutch ring 30 and the relative movement speed in the circumferential direction calculated by the calculation unit is the time for movement.

  In the present embodiment, the rotation speed of the third clutch ring 30 is slower than the rotation speed of the sleeve 36, and the sleeve 36 catches up with the third clutch ring 30. The sleeve 36 is in contact with the third clutch ring 30. Since there is no case of entering the position advanced from the front end face 30b5 (engagement position EP), the first contact position that may cause a follow-up state is the same as the front end face 30b5 in the third clutch ring 30. Become. Therefore, the maximum relative movement distance ML1 required from the position where the rear end portion Sa of the sleeve 36 contacts the front end portion Ca of the front end surface 30b5 of the clutch front teeth 30b1 in the rotational direction to the open position RP where the follow-up state is released. Was supposed to start.

  The maximum relative movement distance ML1 is a distance obtained by subtracting the circumferential length CC of the chamfered portion 30b3 from the value obtained by adding the tooth width SW of the high teeth 36a1 and the tooth width CW of the clutch front teeth 30b1. However, the present invention is not necessarily limited thereto. For example, two circumferential lengths CC of the chamfered portion 30b3 are subtracted from a value obtained by adding the tooth width SW of the high teeth 36a1 and the tooth width CW of the clutch front teeth 30b1. It may be a distance.

  As is clear from the above description, according to the dog clutch device 1 for an automatic transmission according to the second embodiment, the sleeve 36 is rotated from the third clutch ring 30 in a state where the sleeve 36 rotates faster than the third clutch ring 30. When the rotation of the sleeve 36 is decelerated by contacting the ring 30 and synchronized with the third clutch ring 30, the tooth width CW of the clutch front tooth 30b1 is added to the tooth width CW of the high tooth 36a1 after the second thrust load F5 is applied. The first waiting time required to move the length obtained by subtracting the circumferential width CC of one chamfered portion from the length added with SW at the relative speed increased by the reduced thrust load F5. Ta is calculated, and it is determined that the disengagement position RP has come out of the facing state in which the high teeth 36a1 and the clutch front teeth 30b1 rotate with the passage of the first waiting time Ta.

  In this case, when the follow-up state occurs, it is considered that the front end surface 36a4 of the high teeth 36a1 and the front end surface 30b5 of the clutch front teeth 30b1 are in contact with each other at any portion. The sleeve 36 may come into contact with the chamfered portion 30b3 in the rotational direction forward of the clutch front tooth 30b1, but in this case, since the sleeve 36 is brought into contact from a faster state, the clutch front tooth It is considered that the sleeve 36 enters in front of the rotation direction 30b1, and the sleeve 36 advances in the axial direction SCL between the adjacent clutch front teeth 30b1.

  That is, the rear end Sa in the rotation direction of the front end surface 36a4 of the high tooth 36a1 relatively moves in the circumferential direction starting from the position where the front end surface Ca of the front end surface 30b5 of the clutch front tooth 30b1 contacts the front end Ca in the rotation direction. Thus, the maximum relative movement distance ML1 required for the high tooth 36a1 to reach the disengagement position RP that does not oppose the clutch front tooth 30b1 is the maximum travel distance ML1 that is necessary to leave the accompanying state. The maximum relative movement distance ML1 is a length obtained by subtracting the circumferential width CC of one chamfered portion 30b3 from the length obtained by adding the tooth width SW of the high teeth 36a1 to the tooth width CW of the clutch front teeth 30b1. Is the distance.

  Thus, it is possible to easily and quickly determine the departure from the follow-up state by the passage of the relative movement time (first waiting time Ta) predicted to leave the follow-up state, and to enable a quick shift operation. it can.

(Example 3)
Next, a third embodiment in which an automatic transmission having a dog clutch device for an automatic transmission according to the present invention is applied to a vehicle will be described with reference to FIGS.
Since the configuration of the automatic transmission including the dog clutch device for an automatic transmission in the present embodiment is the same as that of the first embodiment, the description thereof is omitted.

  In the present embodiment, it is determined whether or not the rotational speed of the third clutch ring 30 is faster than the rotational speed of the sleeve 36, and the control method branches according to the result, and the sleeve 36 and the third clutch ring 30 are synchronized. That it is going. Further, when the high tooth 36a1 applies a reduced thrust load in order to disengage the revolving state in the revolving state of the high tooth 36a1 of the sleeve 36 and the clutch front tooth 30b1 of the third clutch ring 30, a stepwise process is performed. In the point which reduces a thrust load, it differs from 1st and 2nd embodiment.

  A case where the sleeve 36 rotates at a low speed and a small moment of inertia and the third clutch ring 30 rotates at a high speed and a large moment of inertia is, for example, when shifting down. In this case, the sleeve 36 is accelerated. The

  In addition, the circumferential relative movement position in FIG. 15 is a position facing the side surface 30b9 forward of the clutch front teeth 30b1 in the rotational direction, and the tooth width CW in the rotational direction of the clutch front teeth 30b1 from Sc1 and the rotational direction of the high teeth 36a1. The position of the distance including the tooth width SW was defined as Sc2.

  More specifically, when it is determined that the high teeth 36a1 and the clutch front teeth 30b1 are in the accompanying state, the process continues to step 105 or step 106 (see Example 1), and it is determined to be in the accompanying state. Then, the process proceeds to step 301 according to the present embodiment (see FIG. 17), the timer T is started, and the count C is started (S301).

  Subsequently, the process proceeds to step 302, and the control device 10 adds the thrust load F5 reduced by the axial movement device 40 to the sleeve 36 (see FIG. 15).

  Next, in a state where the thrust load F5 is added, the control device 10 determines whether or not the stroke position S of the high teeth 36a1 is smaller than the first stroke position S1 (close to the neutral position NP) (S303). ). When it is determined that the stroke position S of the high teeth 36a1 is smaller than the first stroke position S1, the routine proceeds to step 304.

  If it is determined in step 303 that the stroke position S of the high tooth 36a1 is larger than the first stroke position S1, it is considered that the follow-up state between the high tooth 36a1 and the clutch front tooth 30b1 has not occurred. The process proceeds to step 112 described in the embodiment.

  In step 304, the control device 10 determines that the rotation speed of the sleeve 36 is larger than the rotation speed of the third clutch ring 30 based on the detection values of the sleeve rotation speed detection sensor 39 and the third clutch ring rotation speed detection sensor 49. It is determined whether or not.

  When it is determined that the rotational speed of the sleeve 36 is larger than the rotational speed of the third clutch ring 30, the process proceeds to step 305, and the control device 10 releases the timer T started in step 301 from the accompanying state. Then, it is determined whether or not the first waiting time Ta ′ to reach the open position has elapsed. (This first waiting time Ta ′ is the same as the first waiting time Ta in the first embodiment.)

  If it is determined that the first waiting time Ta ′ has elapsed, it is considered that the first standby time Ta ′ has left the accompanying state, and thus the process proceeds to step 110 of the first embodiment.

  When it is determined that the first waiting time Ta ′ has not elapsed, the process returns to step 302, and the continuous addition with the reduced thrust load F5 is performed.

  If it is determined in step 304 that the rotational speed of the sleeve 36 is smaller than the rotational speed of the third clutch ring 30, the process proceeds to step 306.

  In step 306, the control device 10 determines whether or not the timer T has elapsed Tc (the time during which the high teeth 36a1 move relatively in the circumferential direction by the circumferential width CC of the chamfered portion 30b3 of the clutch front tooth 30b1). Determine whether. If it is determined that Tc has elapsed, the process proceeds to step 307, and in step 307, the control device 10 adds 1 to the counter C and stores it, and then proceeds to step 308. If it is determined in step 306 that Tc has not elapsed, the process returns to step 302 and the thrust load F5 is continuously added.

  Next, at step 308, the control device 10 determines whether or not the stroke position S of the high teeth 36a1 is smaller than the fifth stroke position S5 (the front end face 30b5 of the clutch front teeth 30b1) (is on the neutral position NP side). judge.

  In step 308, when it is determined that the stroke position S of the high tooth 36a1 is smaller than the fifth stroke position S5, the high tooth 36a1 is closer to the neutral position NP side than the chamfered portion 30b3f in the rotational direction of the clutch front tooth 30b1. It is considered that the state is returned and relatively moved along the front end face 30b5 of the clutch front teeth 30b1 (see FIG. 16).

  Therefore, when it is determined in step 308 that the stroke position S of the high tooth 36a1 is smaller than the fifth stroke position S5, the process proceeds to step 309, and further, the stroke position S of the high tooth 36a1 is greater than the first stroke position S1. It is determined whether or not it is at a small position (neutral position NP side). In this case, the stroke position S1 determines whether or not the high tooth 36a1 has reached the chamfered portion 30b3r on the opposite side in the rotational direction via the front end surface 30b5 from the chamfered portion 30b3f on the front side in the rotational direction of the clutch front tooth 30b1. (See FIG. 16).

  In step 308, the state in which the stroke position S of the high tooth 36a1 is determined to be larger than the fifth stroke position S5 is a state in which the high tooth 36a1 is stopped in the chamfered portion 30b3f forward in the rotational direction, for example, Since it is considered to be at the first follow-up confirmation position FP (see FIG. 19), the process proceeds to step 311 (see FIG. 18).

  In step 311, the thrust load F5 reduced from the thrust load F1 is changed to a further reduced thrust load F6 to be added. As indicated by F6 = F5−C × Fa, the thrust load F6 is, for example, a thrust load value F6 obtained by subtracting 10% from the thrust load F5 (Fa is a ratio for reducing F5, and in this case, 10 percent). Further, the thrust load F6 is reduced stepwise so that the value is reduced by 20% if the counter C is 2 and 30% if the counter C is 3. As described above, when the high load 36a1 is not pushed back to the front end face 30b5 of the clutch front tooth 30b1 with the thrust load F6 due to an increase in sliding resistance between the high tooth 36a1 and the clutch front tooth 30b1, the thrust load F6 is further increased. Reduce.

  Subsequently, the process proceeds to step 312 and the control device 10 determines whether or not the stroke position S of the high tooth 36a1 is smaller than the first stroke position S1 with the thrust load F6 applied. The state in which the stroke position S is determined to be smaller than the first stroke position S1 indicates a state in which the high teeth 36a1 are located at the chamfered portion 30b3f of the clutch front teeth 30b1 (for example, the second follow-up confirmation position SP). (See FIG. 19). Therefore, when the stroke position S is smaller than the first stroke position S1, the process proceeds to step 313.

  When it is determined that the stroke position S is larger than the first stroke position S1, it is considered that the stroke position S has left the accompanying state, and thus the process proceeds to step 112 in the first embodiment.

  In step 313, it is determined whether or not the time Tc during which the high teeth 36a1 move in the circumferential direction of the chamfer 30b3f and the movement time Tc of the chamfer 30b3f added according to the counter C have elapsed. To do. Even in this case, when the counter C is 2, a value obtained by multiplying Tc by 2 is added. When the counter C is 3, a value obtained by multiplying Tc by 3 is added, and the timer T is extended. The high teeth 36a1 are pushed out from the chamfered portion 30b3f and moved to the front end surface 30b5. When it is determined that the predetermined time (Tc + C × Tc) for the timer T to move the chamfered portion 30b3f has not elapsed, the process returns to step 312 and the high tooth 36a1 is transferred to the chamfered portion 30b3f of the clutch front tooth 30b1. It is determined whether or not it is located.

  When it is determined that the predetermined time (Tc + C × Tc) for the timer T to move the chamfer 30b3f has elapsed, the process proceeds to step 314, where 1 is added to the counter C and the counter C is stored as 2. .

  Subsequently, at step 315, it is determined whether or not the stroke position S is smaller than the fifth stroke position (front end face 30b5) S5 (on the neutral position NP side).

  In step 315, the state where the stroke position S is determined to be larger than the fifth stroke position (front end surface 30b5) S5 indicates a state where the high teeth 36a1 are in contact with the chamfered portion 30b3f of the clutch front teeth 30b1, for example, This is a case where it is located at the third follow-up confirmation position TP. Therefore, when it is determined that the stroke position S is larger than the fifth stroke position S5, the process proceeds to step 311. In this case, since the counter C is 2, the thrust load F6 is reduced by 20%, and the thrust load F6 reduced by 20% is added to the high teeth 36a1.

  If it is determined in step 315 that the stroke position S is smaller than the fifth stroke position (front end face 30b5) S5, it is considered that the high teeth 36a1 are pushed back to the front end face 30b5 from the position of the chamfered portion 30b3f. 310.

  If it is determined in step 315 that the stroke position S is smaller than the fifth stroke position (front end face 30b5) S5, and in step 309, the stroke position S of the high tooth 36a1 is in a position smaller than the first stroke position S1. If it is determined, the process proceeds to step 310. Whether or not the timer T has elapsed in step 310 longer than the value obtained by subtracting the time (C × Tc) used for the distance moved by the high teeth 36a1 in the width direction in the chamfered portion 30b3f from the second waiting time Tb. Determine whether.

  The second waiting time Tb is determined when the sleeve 36 and the third clutch ring 30 are synchronized with each other when the sleeve 36 and the third clutch ring 30 are synchronized with each other. This is the time estimated that the front teeth 30b1 have moved relative to each other in the circumferential direction to reach the open position RP (corresponding to the circumferential relative movement position Sc2 in FIG. 15). For example, as shown in FIG. 19, the rear end Sa of the high teeth 36a1 contacts the front outer end Cp1 of the chamfered portion 30b3 of the clutch front teeth 30b1, and then relatively rotates in the circumferential direction to rotate the high teeth 36a1. This is the time until the front end Sb is located at the release position RP that passes through the rear outer end Cp2 of the clutch front teeth 30b1.

  For example, the maximum relative movement distance ML2 obtained by adding the tooth width SW of the high teeth 36a1 and the tooth width CW of the clutch front teeth 30b1 is calculated by the calculation unit from the rotation speed of the sleeve 36 and the rotation speed of the third clutch ring 30. The relative movement speed in the circumferential direction is the time for movement. The relative speed in the circumferential direction between the sleeve 36 and the third clutch ring 30 is calculated by the difference between the rotational speed of the sleeve 36 detected by the rotational speed detection sensor 49 and the rotational speed of the third clutch ring 30. The relative speed immediately before the calculated second waiting time Tb is obtained and used for calculating the second waiting time Tb.

  In the case of this embodiment, the rotation speed of the third clutch ring 30 is faster than the rotation speed of the sleeve 36, and the third clutch ring 30 catches up with the sleeve 36. Since the front end surface 36a4 may enter a position (engagement position EP) that is advanced from the front end surface 30b5 of the third clutch ring 30, the first contact position that may cause a follow-up state is In the three-clutch ring 30, not the front end portion Ca of the front end surface 30 b 5 but the front outer end portion Cp 1 that coincides with the boundary side between the side surface 30 b 9 of the clutch front tooth 30 b 1 and the chamfered portion 30 b 3 f forward in the rotation direction ( Correspondence). Therefore, the necessary maximum relative movement distance ML2 starts from the position where the rear end Sa of the sleeve 36 contacts the side surface 30b9 of the clutch front teeth 30b1 and the front outer end Cp1 of the chamfered portion 30b3f.

  In the present embodiment, the maximum relative movement distance ML2 is a distance obtained by adding the tooth width SW of the high teeth 36a1 and the tooth width CW of the clutch front teeth 30b1, but is not necessarily limited thereto. For example, the high teeth 36a1 The distance obtained by subtracting one of the circumferential length CC of the chamfered portion 30b3 from the value obtained by adding the tooth width SW of the tooth and the tooth width CW of the clutch front tooth 30b1 may be used.

  In step 310, a time longer than the value obtained by subtracting the time (C × Tc) that the high tooth 36a1 used for the distance moved in the width direction in the chamfered portion 30b3f from the second waiting time Tb in the timer T has elapsed. If it is determined that the high teeth 36a1 and the clutch front teeth 30b1 are separated from each other, the high teeth 36a1 are considered not to be repelled by the clutch front teeth 30b1. Transition. Then, a thrust load F1 larger than the thrust load F5 and the thrust load F6 is added again.

In the timer T, when the time (C × Tc) used for the distance moved by the high teeth 36a1 in the width direction in the chamfered portion 30b3 is less than the value obtained by subtracting from the second waiting time Tb, If it is determined, the process returns to step 309 to determine whether or not the stroke position S is smaller than the first stroke position S1.
Since other processes are the same as those in the first embodiment, description thereof will be omitted.

  As is apparent from the above description, according to the dog clutch control device 10 for an automatic transmission according to the third embodiment, the sleeve 36 is moved from the state in which the sleeve 36 rotates slower than the third clutch ring 30 to the first position. When the rotation of the sleeve 36 is accelerated by contacting the third clutch ring 30 and is synchronized with the third clutch ring 30, the high tooth 36a1 is added to the tooth width CW of the clutch front tooth 30b1 after the second thrust load F5 is applied. The second waiting time Tb required to move the distance corresponding to the length including the tooth width SW at the relative speed increased by the reduced second thrust load F5 is calculated, and the second waiting time Tb is calculated. With the progress, it is determined that the open position RP deviates from the facing state in which the high teeth 36a1 and the clutch front teeth 30b1 rotate.

  In this case, when the follow-up state is occurring, the front end surface 36a4 of the high teeth 36a1 and the front end surface 30b5 of the clutch front teeth 30b1 are in contact with each other at any portion, or the front end surface 36a4 of the high teeth 36a1. And the chamfered portion 30b3 of the clutch front tooth 30b1 are considered to be in contact with each other at any portion.

  That is, starting from the position where the rear end Sa of the front end surface 36a4 of the high tooth 36a1 contacts the front outer end Cp1 of the front end 30b3 of the clutch front tooth 30b1 in the rotation direction, the circumferential direction The maximum relative movement distance ML2 required to disengage from the accompanying state is obtained until the high tooth 36a1 reaches the open position RP where the high tooth 36a1 does not face the clutch front tooth 30b1. The maximum relative movement distance ML2 is a distance corresponding to the length obtained by adding the tooth width SW of the high teeth 36a1 to the tooth width CW of the clutch front teeth 30b1.

  In this way, it is possible to easily and quickly determine the departure from the accompanying state by the passage of the relative movement time (second standby time Tb) predicted to leave the accompanying state, and to enable a quick shift operation. it can.

  Further, after adding the second thrust load F5, when it is determined that the accompanying state continues, the third thrust load F6 that further reduces the second thrust load F5 is added. In this way, by changing the second thrust load F5 that is reduced and added to eliminate the follow-up state to the third thrust load F6 that is further reduced, the high teeth 36a1 and the clutch front teeth 30b1 are added. The relative movement speed in the circumferential direction can be increased, and the high teeth 36a1 and the clutch front teeth 30b1 can be quickly and reliably separated from the accompanying state where they are rotated in the facing state.

  Further, when it is determined that the second thrust load F5, which is a reduced load in order to disengage the revolving state, is further reduced and added, and it is determined that the revolving state is in the revolving state, The thrust load F6 further reduced at the stage is added. In this way, the thrust load is reduced and added stepwise while repeatedly confirming separation from the accompanying state, so that the accompanying state can be separated efficiently and reliably.

  In the present embodiment, the case where the high load 36a1 is in contact with the chamfered portion 30b3f at the front of the clutch front tooth 30b1 in the rotational direction has been described as the case where the thrust load F6 that is gradually reduced is applied. For example, when the high teeth 36a1 are in a rotating state in contact with the front end face 30b5 of the clutch front teeth 30b1, a thrust load F6 that is gradually reduced may be added.

  In the first to third embodiments, the clutch front teeth are two facing the circumference of the clutch ring. However, the present invention is not limited to this. For example, the clutch front teeth are arranged on the circumference of the clutch ring. Three or more may be arranged at an equal distance.

  In addition, the dog clutch transmission mechanism is configured by a sleeve, a third clutch ring, a fourth clutch ring, and the like, but is not limited thereto, and for example, a sleeve, a first clutch ring (first output gear), and a first clutch A two-clutch ring (second output gear) or the like may be used.

  The rotation shaft is the input shaft (input shaft) 22 of the automatic transmission that is rotationally connected to the output shaft of the engine 11 via the clutch 12, but is not limited to this. An output shaft that transmits rotational torque may be used as the rotation axis. Specifically, an input shaft of an automatic transmission that is connected to an output shaft of the engine via a clutch, a counter shaft that is provided in parallel to the input shaft and is rotationally connected via a transmission gear, In the structure of an automatic transmission having an output shaft having a rotation axis parallel to the counter shaft and provided with a plurality of idle gears meshing with a plurality of transmission gears provided on the counter shaft, The shaft may be a rotational axis. In this case, the sleeve side has a large moment of inertia and the clutch ring side has a small moment of inertia (free state).

  Further, the rotary shaft that is rotationally connected to the input shaft of the automatic transmission includes the case where the rotary shaft is directly connected to the input shaft as in this embodiment, and is rotationally connected to the output shaft of the automatic transmission. The rotating shaft includes a case where the rotating shaft is directly connected to the output shaft (output shaft).

  The present invention is not limited to the embodiment described above and shown in the drawings, and can be implemented with appropriate modifications within a range not departing from the gist.

  DESCRIPTION OF SYMBOLS 1 ... Dog clutch device for automatic transmissions, 10 ... Control device / Dog clutch control device for automatic transmissions, 10b1 ... Circumferential speed calculation unit, 10b2 ... First standby time calculation unit, 10b3,. Second standby time calculation unit, 10b4... Rotation determination unit, 10b5... Rotation removal determination unit, 10c1... First thrust load addition unit, 10c2. ... 1st thrust load re-addition part, 10c4 ... Axial direction operation control part, 10c5 ... 3rd thrust load addition part, 24 ... Input shaft / rotating shaft (input shaft), 30 ... Clutch ring / dog clutch speed change mechanism (third clutch ring), 30b .... engagement teeth (dog clutch teeth), 30b1 ... clutch front teeth, 30b2 ... clutch rear teeth, 30b3 ... chamfered parts (clutch front teeth 30b5 ... front end face (front end face of clutch front teeth), 36 ... sleeve / dog clutch speed change mechanism, 36a ... engagement teeth (inner teeth), 36a1 ... high teeth, 36a2,. Low teeth, 36a5 ... tooth gap, 38 ... stroke position sensor / dog clutch transmission mechanism, 39 ... rotation speed detection sensor (sleeve rotation speed detection sensor), 40 ... shaft drive / dog clutch transmission mechanism , 42 ... output shaft (output shaft), 49 ... rotation speed detection sensor (clutch ring rotation speed detection sensor), EP ... engagement position, FE ... front end face (front end face of the dog clutch part) NP, neutral position, RE, rear end position, RP, open position, SCL, axis (rotation axis), t, predetermined amount.

Claims (4)

A rotary shaft that is rotatably connected to one of the input shaft and output shaft of the automatic transmission and is rotatably supported about the axis;
A clutch ring rotatably supported on the rotary shaft and rotationally connected to the other of the input shaft and the output shaft. A sleeve fitted so as to be movable in the axial direction, an axial movement device for moving the sleeve in the axial direction between a neutral position where the sleeve is not in contact with the clutch ring and an engagement position where the sleeve is engaged with the clutch ring, the clutch ring The tooth to be engaged is formed so as to protrude toward the sleeve and engages with the engagement tooth provided on the sleeve in accordance with the axial movement of the sleeve, and the axial movement position of the sleeve is detected. A stroke position sensor that detects the rotation speed of the sleeve and the clutch ring, respectively.
The engaging teeth are formed such that a plurality of high teeth are higher in height than the remaining low teeth, and the engaged teeth are clutch front teeth whose outer diameter is larger than the inner diameter of the high teeth and smaller than the inner diameter of the low teeth. Is formed to extend from a front end surface of the engaged tooth to a rear end position of the engaged tooth at a position corresponding to the high tooth, and can be engaged with a tooth groove of the engaging tooth. Is a dog clutch transmission mechanism formed to extend from a position retracted by a predetermined amount from the front end surface of the engaged tooth to a rear end position of the engaged tooth;
An axial operation control unit that controls the operation of the axial movement device based on a detection position of the stroke position sensor and an axial movement speed of the sleeve;
A first thrust load adding portion for applying a first thrust load to the sleeve by the axial movement device in order to advance the sleeve in the axial direction and engage the sleeve with the clutch ring;
A follow-up determination unit that determines whether or not the high teeth and the clutch front teeth are rotating in a follow-up state;
A second thrust load adding unit that adds a second thrust load having a load value smaller than the first thrust load to the sleeve by the axial movement device when it is determined by the accompanying determination unit to be in the accompanying state;
A follow-up disengagement determining unit for determining that the high teeth are located in an open position where they are moved relative to the clutch front teeth in the circumferential direction after the second thrust load is applied;
A first thrust force that causes the first thrust load to be reapplied to the sleeve by the axial movement device when the follow-up disengagement determining unit determines that the high teeth are located at the open position with respect to the clutch front teeth. A load reapplying portion;
A dog clutch device for an automatic transmission comprising: Chamfered portions are formed on both sides of the front end surface of the clutch front teeth in the circumferential direction,
The accompanying withdrawal determination unit
When synchronizing the rotation of the sleeve and the clutch ring from a state in which the sleeve rotates faster than the clutch ring, after the second thrust load is applied by the second thrust load adding unit, the sleeve and The distance obtained by subtracting the circumferential width of one of the chamfered portions from the length obtained by adding the tooth width of the high teeth to the tooth width of the front teeth of the clutch at the relative movement speed in the circumferential direction of the clutch ring. When the first waiting time necessary for movement has elapsed, it is determined that the high teeth are located in the released position with respect to the clutch front teeth,
When synchronizing the rotation of the sleeve and the clutch ring from a state in which the sleeve rotates slower than the clutch ring, after the second thrust load is applied by the second thrust load adding portion, the sleeve and When the second waiting time required to move the distance of the length obtained by adding the tooth width of the high teeth to the tooth width of the front teeth of the clutch at the relative movement speed in the circumferential direction of the clutch ring,
The dog clutch device for an automatic transmission according to claim 1, wherein it is determined that the high teeth are located at the release position with respect to the clutch front teeth.   The third thrust that reduces the second thrust load when the follower detachment determination unit determines that the accompanying state of the sleeve and the clutch ring continues after the addition of the second thrust load. The dog clutch device for an automatic transmission according to claim 1, further comprising a third thrust load adding portion for applying a load.   The third thrust load adding portion is gradually reduced each time the follower determining portion determines that the sleeve and the clutch ring are in a follower state after the second thrust load is added. 4. The dog clutch device for an automatic transmission according to claim 3, wherein the dog clutch device is a stepwise reduced thrust load adding portion capable of adding a thrust load.

Images