JP2014185757A - Shift detent device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a shift detent device for preventing occurrence of gear stopper striking sound when a sleeve is engaged with a dog clutch and a contact sound generated by adjoining a ring when the sleeve is positioned at a shift neutral position.SOLUTION: This invention relates to a shift detent device for a dog clutch mechanism comprising a lock member 62 biased against a fork shaft 40b by a biasing member and a position setting groove 60 formed in a fork shaft into which the lock member is fitted to set a sleeve 36 to a neutral position and an engagement position where the sleeve 36 is engaged with a clutch part 30a. The shift fork 40a comprises a rotation adjustment part 47 that is supported at the fork shaft in a relative rotatable manner while restricting relative motion in an axial direction and that is adjusted and rotated around the axial line under a state in which its motion in an axial line direction is allowed. The position setting grooves 60 are spiral grooves each of which is formed at the fork shaft while the sleeve corresponds to each of the neutral position and a stop position where it stops at the engagement position, respectively.

Description

  The present invention relates to a shift detent 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 relatively rotatable on a rotating shaft connected to a driving wheel and are immovably fitted in the axial direction are provided in parallel with the rotating shaft. 2. Description of the Related Art A constant meshing type in which a plurality of gears provided around a counter shaft are always meshed is known. This is because a sleeve that is spline-fitted to the rotary shaft so as to be movable in the axial direction is juxtaposed to the idler gear, and the engagement teeth (splines) provided on the joint surface of the sleeve to the idler gear are connected to the idler gear. It 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 integrally rotated. 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.

  In the transmission, a shift that holds the sleeve at a neutral position (intermediate position) at which the sleeve is engaged with the selected idle gear or at which the sleeve is not engaged with the idle gear is provided. A detent device (holding device) is required.

  In Patent Document 1, as such a shift detent device, a fork shaft that moves the sleeve of the gear shaft in the axial direction has three positioning grooves corresponding to the gear shaft positions of L speed, neutral, and reverse gear. It describes a steel ball that is provided and biased by a spring and fits into a groove. By this shift detent device, the position of the fork shaft is held at a constant pressure. In the initial gear shift, the gear shift target value is set to the deepest gear shift position, and the sleeve does not move to a predetermined stop position that may occur during shift control, or the sleeve exceeds the predetermined stop position. Prevent excessive gear shifting. In addition to the gear stopper position, by opening the hydraulic valve of the shift actuator, the stop position by the lock ball load after the initial gear shift is learned, and the gear shift operation is performed without being affected by variations in the dimensions of the transmission coupling mechanism. Is to be executed reliably and safely.

  According to Patent Document 2, a plurality of rod grooves (positioning grooves) formed on the shift rod (fork shaft) of the transmission and arranged along the axial direction of the shift rod slide on the plurality of rod grooves. A lock ball freely engageable with the rod groove, and an urging means for urging the lock ball toward the shift rod, and a plurality of rod grooves and the lock ball from one shift rod. A shift detent device having a plurality of sets of shift load generating parts is described. Thus, the shift load characteristic is easily operated.

Japanese Patent Publication No. 6-72659 JP 2009-121580 A

  However, in the shift detent devices disclosed in Patent Document 1 and Patent Document 2, the stop position of the sleeve positioned by the lock ball load on the fork shaft is close to the position of the gear stopper where the sleeve is completely engaged with the dog clutch. Gear stopper collision noise is generated, or the distance between the block ring (clutch ring) fitted to the dog clutch and the sleeve at the time of neutral is narrow, so the contact sound between the sleeve and the ring end surface is generated when the sleeve moves to the middle position. It may have occurred.

  The present invention has been made in view of the above-described problems, and it is possible to detect a gear stopper collision sound when the sleeve is engaged with the dog clutch and a contact sound with the ring fitted to the fork shaft when the sleeve moves to the neutral position. It is an object of the present invention to provide a shift detent device that prevents generation.

In order to solve the above-mentioned problem, the structural feature of the invention according to claim 1 is that the rotary shaft is rotatably connected to one of the input shaft and the output shaft of the automatic transmission and is rotatably supported about the axis. A clutch ring supported on the other of the input shaft and the output shaft, a hub fixed to the rotary shaft adjacent to the clutch ring, and a relative rotation with the hub is restricted and movable in the axial direction. A fork shaft that is slidably supported in the axial direction on the housing, and a shift fork that is supported by the fork shaft and moved in the axial direction. The shift fork is moved in the axial direction. An axial movement device is formed in a meshing portion projecting to the sleeve side of the clutch ring and meshes with the sleeve in a detachable manner according to the axial movement of the sleeve. A dog clutch mechanism comprising: a dog clutch mechanism; a locking member biased in a direction perpendicular to the fork shaft by a biasing member; a neutral position not contacting the clutch ring; and a meshing engagement with the dog clutch portion of the clutch ring In order to position the sleeve at a position, a positioning groove is provided on the outer peripheral surface of the fork shaft and into which the lock member is fitted, and the shift fork is moved relative to the fork shaft in the axial direction. The fork shaft is supported so as to be relatively rotatable, and includes a rotation adjusting unit that adjusts and rotates the fork shaft around the axis while allowing movement in the axial direction.
The positioning groove is a spiral groove formed on the outer peripheral surface of the fork shaft corresponding to a stop position where the sleeve stops at the neutral position and the meshing position.

  According to this, the sleeve is stopped at the stop position at the neutral position where the sleeve does not contact the clutch ring and the mesh position where the sleeve meshes with the dog clutch portion. These stop positions at which the sleeve stops are determined by the axial position of the fork shaft determined by the position of the positioning groove in which the lock member is inserted. A positioning groove for positioning the stop position of the sleeve is formed by a spiral groove. Therefore, for example, when the dog clutch is assembled, the fork shaft is adjusted and rotated with respect to the lock member even when the stop position positioned by the position of the positioning groove is the position where the sleeve comes into contact with the clutch ring or the gear stopper. Thus, the shift detent device can be reset so that the sleeve is positioned and stopped with a predetermined gap that does not contact the sleeve, the clutch ring, and the gear stopper. As a result, the sleeve is stopped by providing a predetermined gap between the back end of the dog clutch portion (gear stopper) and preventing the gear stopper from colliding with the clutch ring when the sleeve is in the neutral position. By preventing the contact, generation of contact noise between the sleeve and the clutch ring can be prevented.

  The structural feature of the invention according to claim 2 is the shift detent device for a dog clutch mechanism according to claim 1, wherein the spiral groove is a spiral groove formed around the axis of the fork shaft. It is.

  According to this, since the positioning groove is formed in a spiral shape around the outer periphery of the fork shaft, it can be manufactured very easily at a low manufacturing cost.

1 is a schematic view of a vehicle including an automatic transmission having a shift detent device according to a first embodiment of the present invention. 1 is a schematic diagram of an automatic transmission having a shift detent device according to the present invention. It is a block diagram of a control apparatus. It is a disassembled perspective view of a dog clutch mechanism. It is a front view of a clutch ring. It is a front view of a clutch hub. It is a front view of a sleeve. It is a figure which shows the spiral groove provided in the fork shaft. It is a figure which shows the outline | summary of a shift detent apparatus. It is a side view which shows the mechanism in which a fork shaft supports a shift fork. It is XI-XI sectional drawing in FIG. It is sectional drawing which shows a rotation adjustment part and an adjustment rotation restraint part. It is a front view which shows a rotation adjustment part and an adjustment rotation restraint part. It is sectional drawing which shows the dog clutch which has a sleeve in a neutral position. It is sectional drawing which shows the state which the sleeve contacted the clutch front tooth of the dog clutch. It is sectional drawing which shows the state which the sleeve contacted the clutch back tooth. It is a figure which shows the dog clutch which has a sleeve in a meshing position. It is a figure which shows the state which the lock member got on the edge of the positioning groove | channel corresponding to a neutral position by the slide of a fork shaft. It is a figure which shows adjusting and rotating a fork shaft around an axis line in the state where the lock member was inserted in the positioning groove corresponding to the meshing position. It is a figure which shows another example of a locking member. It is a schematic diagram of the automatic transmission which has the shift detent apparatus of 2nd Embodiment. It is a block diagram of a control apparatus. It is a figure which shows moving a lock member along a spiral positioning groove by rotating a fork shaft around an axis in a state where a lock member is inserted in a positioning groove corresponding to a neutral position. It is a figure which shows the state which the lock member moved to the position of the positioning groove corresponding to a meshing position by rotating a fork shaft around an axis line.

Example 1
An embodiment in which an automatic transmission provided with a shift detent device for a dog clutch according to the present invention is applied to a vehicle will be described below 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 drive wheels Wfl and Wfr via the clutch 12, the automatic transmission 13, and the differential device 14 (a 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 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 drive device 40 including shift detent device 58, output shaft (output shaft) 42, clutch hub 43, A clutch ring (first output gear) 44, a sleeve 45, a second clutch ring (second output gear) 46, a third output gear 48, and a fourth output gear 50 are configured. The first dog clutch mechanism includes a first clutch ring (first output gear) 44, a second clutch ring (second output gear) 46, a clutch hub (hub) 43, a sleeve 45, an axial movement device (not shown), and the like. The third clutch ring (third input gear) 30, the fourth clutch ring (fourth input gear) 32, the clutch hub (hub) 34, the sleeve 36, the stroke position sensor 38, the shaft movement device 40, etc. A second dog clutch mechanism is configured.

  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 (not shown) 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 around the axis CL.

  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, which will be described later, and the fourth input gear (fourth clutch ring) 32 meshes with a fourth output gear 50, which will be described later.

  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 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. A ring-shaped first dog clutch portion 44 a is formed on a surface (meshing portion) of the first clutch ring 44 facing the clutch hub 43. A ring-shaped second dog clutch portion 46 a is formed on the surface (meshing portion) of the second clutch ring 46 facing the clutch hub 43.

  A clutch hub (hub) 43 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 43, 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 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 mechanism of the input shaft 24 and the first dog clutch mechanism of the output shaft 42 have the same configuration, the second dog clutch 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 (spline shape omitted) 35 for spline fitting with the input shaft 24, is formed in a flat cylindrical shape, and is formed on the outer peripheral surface of the clutch hub 34. Spline teeth 34a are formed. 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 formed to be the same so that the high teeth 36a1 and the low teeth 36a2 of the sleeve 36 are 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 12 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 CL 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, which will be described later, are fitted in 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. Since the third clutch ring 30 and the fourth clutch ring 32 have a substantially symmetrical structure with the clutch hub 34 as the center, 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 not movable relative to the axis CL. 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 extending from the front end surface 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 CL 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 30b1.

  As shown in FIGS. 4 and 5, a total of ten clutch rear teeth 30b2 are disposed at the phase position between the two clutch front teeth 30b1, and the outer diameter of each tooth 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 CL 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. A tooth groove 30b8 is formed between adjacent clutch rear teeth 30b2, and a tooth groove 30b10 is formed between the clutch front teeth 30b1 and the clutch rear teeth 30b2. When the sleeve 36 approaches the third clutch ring 30 while rotating relatively, if the high teeth 36a1 and the low teeth 36a2 enter the position where the third clutch ring 30 is retracted by a 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. The front end portion of the clutch rear teeth 30b2 is constituted by the front end surface 30b6 and the chamfered portion 30b4 on the sleeve 36 side of the clutch rear teeth 30b2.

  As the stroke position sensor 38, for example, various position sensors such as an optical position sensor and a linear encoder are used.

  As shown in FIG. 3, the control device 10 includes a storage unit, a calculation unit, and a control unit, and a third dog clutch unit 30 a at the tip of the sleeve 36 (the front end surface 36 a 4 of the high teeth 36 a 1) detected by the stroke position sensor 38. The thrust load value of the linear actuator 40i for driving the shaft driving device 40 and the high tooth 36a1 based on the relative position signal with respect to the position of the front end surface FE, the front end portion of the clutch rear teeth 30b2 and the rear end position RE of the dog clutch portion 30a. The movement position of the front end face 36a4 is controlled.

  The axial movement device 40 reciprocates the sleeve 36 along the axis (CL) 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 When a reaction force is applied from the fourth clutch ring 32, the sleeve 36 is configured to be allowed to move by the reaction force.

  The axial movement device 40 includes a shift fork 40a, a fork shaft 40b, and a drive device 40c. The front end of the shift 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 shift fork 40a is formed in a U shape with an open front end, and as shown in FIGS. 10 and 11, a fork is provided on the outer periphery of a small-diameter fork support portion 40b1 provided in the middle portion of the fork shaft 40b. The shaft 40b is supported while allowing relative rotation. The fork support portion 40b1 is provided with a flange-shaped stopper portion 40b2 around the shift fork 40a. The stopper portion 40b2 restricts the relative movement of the fork shaft 40b in the axis SCL direction with respect to the shift fork 40a. A guide hole 40a1 is provided in a middle portion of the shift fork 40a so that a distal end side of a guide member (anti-rotation) 40e, which will be described later, is slidably inserted. The shift fork 40a slides smoothly by being guided by the guide member 40e. .

  The fork shaft 40b is supported by the housing 22 so as to be slidable and relatively rotatable along the axis SCL direction. That is, one end (left end) of the fork shaft 40b is supported on the first wall 22b via a rotation adjusting portion 47 and a bearing (sliding bearing) 22b3, which will be described later, and the other end (right end) side of the fork shaft 40b is relatively rotated with respect to the bracket 40d. It is supported so that it cannot move in the axial direction. As shown in FIGS. 12 and 13, a rotation adjusting portion 47 formed in a cylindrical shape having a bowl-shaped head portion 47c is externally fitted to one end of the fork shaft 40b.

  The rotation adjusting portion 47 is rotatably supported by the bearing 22b3, and a fitting hole 47a into which the fork shaft 40b is fitted is provided at the center of the rotation adjusting portion 47. A key groove 47b is provided in the insertion hole 47a, and a key member 49 provided between the key groove 47b and a key portion 40b3 provided along the axis (SCL) direction on the outer wall of the fork shaft 40b is inserted. Yes. As a result, the fork shaft 40b cannot be rotated relative to the rotation adjusting portion 47 and can slide in the axis (SCL) direction. An anti-slip 47d is formed on the outer peripheral edge of the head 47c of the rotation adjusting unit 47 so that, for example, the operator can hold and rotate the hand. An elongated hole 47e having an arcuate edge formed in parallel along the circumferential direction is formed between the outer peripheral edge of the head 47c and the fitting hole 47a. The circumferential opening width of the elongated hole 47e is, for example, It is formed to correspond to 120 ° in the circumferential direction. The shaft portion of the bolt member 51 is loosely fitted in the elongated hole 47e. At positions corresponding to the long holes 47e on the outer wall (left side in FIG. 12) of the first wall 22b, positioning holes 53 are provided at four positions at a pitch of 90 °, for example, so as to surround the fork shaft 40b. A female screw is formed on the inner peripheral wall of the positioning hole 53 so that the bolt member 51 can be engaged and disengaged. The bolt member 51 is screwed into one of the positioning holes 53, and the edge of the elongated hole is pressed against the back side of the head of the bolt member 51, thereby fixing the rotation adjusting portion 47 so as not to rotate relative to the first wall 22b. It is possible to do. By fixing the four positioning holes arranged every 90 ° through the long holes 47e having an opening width of 120 °, an adjustable rotation range of 360 ° is secured for the fork shaft 40b.

  The bracket 40d is slidable by a guide member (anti-rotation) 40e protruding in the axial direction from the second wall 22c, and is 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 the linear actuator 40i as a drive source. As the linear actuator 40i, for example, there is a ball screw type linear actuator. 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 axis of the stator, and a drive shaft 40h And a nut member 40f made of a ball nut screwed into the nut. 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 device 58 is provided in the vicinity of the first wall 22b of the fork shaft 40b. The shift detent device 58 includes a positioning groove 60 provided on the outer periphery of the fork shaft 40b, a lock member (lock ball) 62 fitted into the positioning groove 60, a guide member 64 that guides the advancement and retraction of the lock member 62, a lock A biasing member (coil spring) 66 that biases the member 62 in a direction approaching the fork shaft 40b is mainly provided.

  As shown in FIG. 8, the positioning groove 60 is formed in a spiral shape that is continuous for three rounds around the axis SCL. The central groove 60N of the positioning groove 60 corresponds to a stop position where the sleeve 36 stops at a neutral position (neutral position) where the sleeve 36 does not contact the third clutch ring 30 and the fourth clutch ring 32. In FIG. 8 corresponds to a stop position where the sleeve 36 stops at the third engagement position (corresponding to the rear end position RE) where the sleeve 36 is engaged with the dog clutch portion 30a of the third clutch ring 30, and the left groove 60L on the left side in FIG. This corresponds to a stop position where the fourth clutch ring 32 stops at a fourth meshing position (not shown) that meshes with a dog clutch portion (not shown).

  The guide member 64 is formed in a cylindrical shape, and the base end portion of the guide member 64 is fixed to the housing 22 via a bracket (not shown). A biasing member (coil spring) 66 is fitted in the guide member 64 in a pressed state, and a steel lock member (lock ball) 62 is assembled to the tip of the biasing member 66 so as to be relatively rotatable. The lock member 62 is urged by the urging member 66 from a direction perpendicular to the fork shaft 40b. The urging force advances from the tip of the guide member 64 and fits into the positioning groove 60 of the fork shaft 40b, and retreats into the guide member 64 by an external force against the urging force of the urging member 66. Yes. When the fork shaft 40b slides in the direction of the axis SCL, the lock member 62 rides on the edge of the inserted positioning groove 60, moves to the adjacent positioning groove 60, and is inserted into the adjacent positioning groove 60. The movement of the fork shaft 40b in the axis SCL direction is restricted at the inserted position.

  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 shift detent device for the dog clutch mechanism used in the above-described automatic transmission will be described below. 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.

  The sleeve 36 is positioned between the third clutch ring 30 and the fourth clutch ring 32, and the spline (inner teeth) 36 a of the sleeve 36 is connected to any of the dog clutch teeth 30 b of the third clutch ring 30 and the fourth clutch ring 32. It is positioned in a neutral position that is not engaged (FIG. 14A).

At this time, in the shift detent device 58, as shown in FIG. 9, the lock member 62 is fitted into the central groove 60N of the positioning groove 60, and the axial movement of the fork shaft 40b is restricted to bring the sleeve 36 into the neutral position. keeping. When the sleeve 36 is close to either the third clutch ring 30 or the fourth clutch ring 32, the fork shaft 40b is rotated by turning the rotation adjusting portion 47. The stop position of the sleeve 36 with respect to the clutch rings 30 and 32 can be adjusted by moving the fork shaft 40b along the spiral positioning groove 60. As a result, it is possible to prevent generation of contact noise between the sleeve 36 and the clutch rings 30 and 32 in the neutral position (neutral position).
Further, at the time of this adjustment, a predetermined gap that does not generate a collision noise is generated between the sleeve 36 and the rear end position RE of the dog clutch portion 30a at the meshing position where the sleeve 36 meshes with the third clutch ring 30. It is configured.

  In response to the shift start signal, the control device 10 applies a control current to which a thrust load necessary for the movement is applied to the linear actuator 40 i of the shaft drive device 40, thereby engaging the sleeve 36 with the third clutch ring 30. Start (FIG. 14B). The fork shaft 40b is moved by extending the drive shaft 40h by the linear actuator 40i, and the sleeve 36 is slid to the third clutch ring 30 side by the shift fork 40a. The sleeve 36 approaches the third clutch ring 30 while relatively rotating by a rotational difference.

  At this time, in the shift detent device 58, as shown in FIG. 15, the lock member 62 is moved in the guide member 64 by the pressing force by the inclined surface of the edge of the central groove 60N by the movement of the fork shaft 40b in the axis SCL direction. The lock member 62 rides on the edge of the central groove 60N. At this time, a drive addition (shift load) at the time of shift is generated in the linear actuator 40i.

  The high teeth 36a1 of the sleeve 36 come into contact with the front end surface 30b5 (or chamfered portion 30b3) of the clutch front teeth 30b1 of the third clutch ring 30. By this contact, the rotational difference between the sleeve 36 and the third clutch ring 30 is slightly reduced. At this time, the low teeth 36a2 of the sleeve 36 are not in contact with anything.

  When the front end surface 36a4 of the high teeth 36a1 contacts the front end surface 30b5 of the clutch front teeth 30b1 but is repelled without being able to enter, the control device 10 causes the sleeve 36 to reattach the third clutch ring by the applied thrust load. Approach 30.

  Further, the sleeve 36 is moved closer to the third clutch ring 30, the stroke position sensor 38 causes the front end surface 36 a 4 of the high teeth 36 a 1 to enter deeper than the front end surface 30 b 5 of the clutch front teeth 30 b 1, and the high teeth 36 a 1 of the sleeve 36 It reaches the front end face 30b6 of the rear teeth 30b2 (FIG. 14C).

  When the stroke position sensor 38 determines that the high teeth 36a1 of the sleeve 36 have reached the clutch rear teeth 30b2, and the high teeth 36a1 of the sleeve 36 are in contact with the side surface 30b9 of the clutch front teeth 30b1, the control device 10 The load is continuously applied, and the high teeth 36a1 enter the tooth gap 30b10 to reach the rear end position RE of the clutch rear teeth 30b2 (FIG. 14D).

  At this time, in the shift detent device 58, as shown in FIG. 16, the lock member 62 is fitted into the right groove 60R of the positioning groove 60, and the axial movement of the fork shaft 40b is restricted to bring the sleeve 36 into the meshing position. keeping.

  The control device 10 determines whether the high teeth 36a1 of the sleeve 36 are in contact with the front end face 30b6 of the clutch rear teeth 30b2 and the high teeth 36a1 of the sleeve 36 are moved to the clutch front teeth 30b1 with a slight rotational difference, or the sleeve 36 and the third clutch. When it is determined that the ring 30 rotates at exactly the same rotational speed and is causing so-called rotation, the friction force between the high teeth 36a1 and the clutch rear teeth 30b2 is reduced by reducing the thrust load. This reduces the rotation difference between the sleeve 36 and the third clutch ring 30 and allows the high teeth 30a1 to move quickly to the side surface 30b9 of the clutch front teeth 30b1, thereby allowing the sleeve 36 and the third clutch ring 30 to move. (Fig. 14D).

As is clear from the above description, according to the shift detent device 58 for the dog clutch mechanism of the present embodiment, the neutral position where the sleeve 36 does not contact the clutch rings 30 and 32 and the sleeve 36 become the dog clutch portion (third dog clutch portion) 30a. The sleeve 36 is stopped at the stop position at the meshing position where it meshes. These stop positions are determined by the position of the fork shaft 40b in the axis SCL direction determined by the position of the positioning groove 60 in which the lock member 68 is fitted. The positioning groove 60 for positioning the stop position of the sleeve 36 is formed by a spiral groove. Therefore, for example, when the dog clutch is assembled, the rotation adjustment is performed even when the stop position positioned by the position of the positioning groove 60 becomes a position where the sleeve 36 contacts the clutch ring 30 or the gear stopper (rear end position RE). The fork shaft 30b is adjusted and rotated by the portion 47 and moved along the spiral groove with respect to the lock member 68, so that the sleeve 36 does not contact the sleeve 36, the clutch rings 30, 32, and the gear stopper (rear end position RE). The shift detent device 58 can be reset so that positioning is stopped with a predetermined gap. As a result, the sleeve 36 is stopped by providing a predetermined gap between the rear end (rear end position RE) of the dog clutch portion (engagement position) 30a, thereby preventing the gear stopper collision noise from occurring and the sleeve 36 being neutral. By preventing contact with the clutch rings 30 and 32 when positioned, the generation of contact noise between the sleeve 36 and the clutch rings 30 and 32 can be prevented.
Further, since the positioning groove 60 is formed in a spiral shape around the outer periphery of the fork shaft 40b, it can be manufactured very easily at a low manufacturing cost.

(Example 2)
Hereinafter, a second embodiment of an automatic transmission provided with a shift detent device for a dog clutch according to the present invention will be described with reference to FIGS.

  In the present embodiment, as shown in FIGS. 18 and 19, a rotation actuator 70 assembled to the bracket 40d is provided on the other end side of the fork shaft 40b, and the rotation for detecting the rotation angle of the fork shaft 40b is provided. The difference from the first embodiment is that an angle sensor 72 is provided and the rotation adjusting unit 47 is omitted.

  As the rotary actuator 70, for example, a motor capable of rotating both forward and reverse and capable of rotational position control, such as a servo motor, is used. The rotation angle sensor 72 uses, for example, a rotary encoder. Since other configurations are the same, the same reference numerals are given and description thereof is omitted.

The operation of the shift detent device 74 for the dog clutch mechanism of this embodiment will be described below.
When shifting the fork shaft 40b in the direction of the axis SCL at the time of shifting, the fork shaft 40b is rotated around the axis SCL by the rotary actuator 70 simultaneously with the movement in the axis direction. As a result, the lock member 62 moves relative to the spiral groove without riding on the edge of the positioning groove 60, and, for example, from the central groove 60N corresponding to the stop position corresponding to the neutral position to the third clutch ring 30. It moves to the right groove 60R corresponding to the stop position corresponding to the meshing position. In this way, when moving from the central groove 60N to the right groove 60R, the lock member 62 does not ride on the edge of the central groove 60N, so that the linear actuator 40i is subjected to driving addition (shift load) during shifting. I won't let you.
The rotation of the fork shaft 40b at this time is detected by the rotation angle sensor 72, and the movement position of the fork shaft 40b in the axial direction is detected by the stroke position sensor 38. The detected position signal is transmitted to the control device 10, and the control device 10 controls the operations of the linear actuator 40i (drive device 40c) and the rotary actuator 70 in synchronization.

In the case where the shifted position is held at the time of shifting, by restricting the rotation of the rotary actuator 70, the lock member 62 rides on the edge of the positioning groove 60 when the fork shaft 40b is moved in the direction of the axis SCL. As a result, a holding force can be generated.
Further, when adjusting the stop position of the sleeve 36 that stops at the neutral position or the meshing position, for example, the linear actuator 40i is set in a free state, and the rotary actuator 70 is driven to rotate. As a result, the fork shaft 40b is moved in the direction of the axis SCL, and the stop position of the sleeve 36 is adjusted. The stop position at that time can be determined as the initial position of the control at which the linear actuator 40i starts the shift operation.

  In addition, although the lock member in the said embodiment was used as the spherical lock ball, it is not limited to this, For example, as shown in FIG.

  Further, although the rotation range of the rotation adjusting unit 47 is secured to 360 °, the present invention is not limited to this, and the rotation range may be a 120 ° rotation range or a rotation range wider than 360 °.

  In addition, the clutch front teeth are two opposed to each other on the circumference of the clutch ring. However, the present invention is not limited to this. For example, three or more clutch teeth are arranged at equal distances from each other on the circumference of the clutch ring. May be used.

  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).

  Moreover, although the rotation angle sensor 72 is a rotary encoder, it is not limited to this, For example, well-known sensors, such as a resolver, can be used.

  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 13 ... Automatic transmission, 22 ... Housing, 24 ... Input shaft / rotary shaft (input shaft), 30 ... Clutch ring / dog clutch mechanism (third clutch ring), 30a ... Dog clutch part ( 3rd dog clutch part), 30b1 ... clutch front teeth, 30b2 ... clutch rear teeth, 32 ... dog clutch mechanism (fourth clutch ring), 34 ... clutch hub / dog clutch mechanism, 36 ... sleeve Dog clutch mechanism, 36a1 ... high teeth, 36a2 ... low teeth, 38 ... stroke position sensor / dog clutch mechanism, 40 ... shaft actuator / dog clutch mechanism, 40a ... shift fork, 40b ... Fork shaft, 42 ... Output shaft (output shaft), 43 ... Clutch hub, 45 ... Sleeve, 47 ... Rotation adjustment 58, shift detent device, 60, positioning groove, 62, lock member, 66, biasing member, CL, axis, SCL, axis, RE, rear End position, t ... predetermined amount.

Claims (2)

A clutch ring that is rotatably connected to one of an input shaft and an output shaft of the automatic transmission and is rotatably supported around an axis, and is rotatably supported and rotatably connected to the other of the input shaft and the output shaft; A hub that is fixed to the rotating shaft adjacent to the clutch ring, a sleeve that is controlled to rotate relative to the hub and that can move in the axial direction, and a housing that is slidably supported in the axial direction. A fork shaft and a shift fork supported by the fork shaft and moved in the axial direction. The shaft driving device moves the shift fork in the axial direction. The engaging portion projects from the clutch ring toward the sleeve. A dog clutch mechanism comprising: a dog clutch portion detachably engaged with the sleeve according to the axial movement of the sleeve;
A lock member biased in a direction perpendicular to the fork shaft by a biasing member;
A positioning groove that is engraved on the outer peripheral surface of the fork shaft and into which the lock member is fitted in order to position the sleeve at a neutral position that does not contact the clutch ring and a meshing position that meshes with a dog clutch portion of the clutch ring. And
The shift fork is supported on the fork shaft so as to be relatively rotatable by restricting relative movement in the axial direction,
The fork shaft is provided with a rotation adjusting section that adjusts and rotates around the axis while allowing movement in the axial direction,
The shift detent device for a dog clutch mechanism, wherein the positioning groove is a spiral groove formed on the outer peripheral surface of the fork shaft corresponding to a stop position where the sleeve stops at the neutral position and the meshing position. The shift detent device for a dog clutch mechanism according to claim 1, wherein the spiral groove is a spiral groove formed around the axis of the fork shaft.

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