JP2015190543A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent increase in size and mass while preventing deformation and breakage.SOLUTION: A power transmission device in which a jumping dog 53c and a standby dog 52b are engaged with each other, has a hub 55 having side faces 55aa opposed to each other while gradually increasing a groove width toward a radial outer side. The jumping dog 53c is provided with a torque transmission face 53bb kept in face-contact with the side faces 55aa of the groove, and a leading face kept in contact with the standby dog 52b in a power transmission state, at one side in the circumferential direction, and is provided with a flipping face 53g inclined to be moved in a direction separating from the standby dog 52b in collision of the standby dog 52b, and inclined from the other end to one end in the circumferential direction in accordance with directing from an inner side to an outer side in the radial direction in a face direction orthogonal to the rotating shaft direction, on the other side in the circumferential direction. The standby dog 52b is provided with a collision face 52bb kept in face-contact with the flipping face 53g in collision of the jumping dog 53c.

Description

  The present invention relates to a power transmission device mainly used for a transmission of a vehicle.

  Conventionally, for example, a transmission shown in Patent Document 1 is known. The transmission includes a low-speed gear and a high-speed gear that are rotatably mounted on an output shaft, a hub that is fixed to a shaft between the low-speed gear and the high-speed gear, and an axial movement of the hub. And a first key and a second key mounted so as to rotate integrally in the circumferential direction.

  According to this transmission, for example, when the first key and the second key are moved to the low speed gear side by the actuator during acceleration, the first key engages with the dog provided on the side surface of the low speed gear. Only with the first key, power transmission between the low-speed gear and the hub is realized. At this time, the second key is in a non-engagement state with respect to the low speed gear, and can be moved to the high speed gear side even during power transmission via the first key.

  Then, when the second key is moved to the high speed gear side, the second key is engaged with a dog provided on the side surface of the high speed gear, and the power between the high speed gear and the hub is determined by the second key. Communication is realized. When the power transmission path is switched from the low-speed gear to the high-speed gear, the rotational speed of the shaft is reduced. At the same time as the power transmission path is switched, the engagement between the first key and the low-speed gear is released, and the first The key can be switched to the high-speed gear side. If the first key is moved to the high speed gear side, the shift (upshift) from the low speed gear to the high speed gear can be completed without causing torque interruption.

Special table 2010-510464 gazette

  By the way, when the power transmission path is switched as described above, the first key that has been engaged with the dog of the low speed gear must be pulled out of the dog immediately after the second key is engaged with the high speed gear. However, the first key and the dog may collide before the first key is removed from the dog.

  At this time, the resultant force of the collision force input from the dog and the reaction force of the collision force input from the hub is input to the first key in the plane direction orthogonal to the rotation axis direction. If the resultant force is directed radially outward, the first key may be deformed or the first key may be damaged. In order to prevent these, a method of increasing the strength by increasing the width of the first key is conceivable. However, this leads to an increase in size and an increase in mass.

  Then, an object of this invention is to provide the power transmission device which can prevent an enlargement and a mass increase, preventing a deformation | transformation and a failure | damage.

  In order to solve the above-described problems, the power transmission device of the present invention is a rotating body that rotates about a predetermined rotation axis, and has a plurality of grooves that are recessed radially inward and extending in the rotation axis direction on the outer peripheral surface. A hub that is fitted in each of the plurality of grooves of the hub, slides in the direction of the rotation axis, and a first dog formed at the tip of the key portion in the direction of the rotation axis. And a sleeve that rotates integrally with the hub, and a dog member that is provided coaxially with the hub and has a plurality of second dogs that can mesh with the first dog arranged in a rotational direction. When the dog member relatively moves in the proximity direction close to the rotation axis direction, the first dog and the second dog mesh with each other, and the hub, the sleeve, and the dog member rotate integrally, The sleeve and the dog member are rotating shafts. A power transmission device in which the first dog and the second dog are disengaged when they move relative to each other in the direction of separation, and the hub, the sleeve, and the dog member rotate relative to each other. The groove has side surfaces facing each other so that the groove width gradually increases toward the outer side in the radial direction, and the key portion gradually increases in the circumferential direction toward the outer side in the radial direction. A torque transmission surface that is in surface contact with the hub and transmits torque to and from the hub via the torque transmission surface in the power transmission state, and the first dog and the second dog in the power transmission state The contact surface is formed on one side in the circumferential direction, and when the second dog collides when the sleeve and the dog member are separated in the rotation axis direction, the sleeve is caused by the collision with the second dog. In the surface direction that is inclined so as to move in the separation direction and that is orthogonal to the rotational axis direction, the repelled surface that is inclined from the other in the circumferential direction toward the other in the radial direction is the circumferential direction. The second dog has a collision surface that comes into surface contact with the struck surface when the first dog collides when the sleeve and the dog member are separated in the rotation axis direction. ing.

  In addition, the bounce surface has a direction of force input from the second dog to the first dog in a plane direction perpendicular to the rotation axis direction, and a torque transmission surface of the key portion from the side surface of the groove. You may make it incline in the direction orthogonal to the direction of this reaction force so that the direction of the input reaction force may be on a straight line.

  In addition, the first dog is inclined radially inward of the bounced surface so that the sleeve moves in the separation direction due to a collision with the second dog at a continuous portion with the torque transmission surface. A chamfered surface may be formed.

  According to the present invention, it is possible to prevent an increase in size and an increase in mass while preventing deformation and breakage.

It is a figure which shows the outline of the transmission for motor vehicles. It is a schematic sectional drawing explaining the axis | shaft switching mechanism in 1st Embodiment. It is a disassembled perspective view of the 2nd switching device in 1st Embodiment. It is a side view of the 2nd switching device in a 1st embodiment. It is a figure explaining switching of the power transmission path from the 2nd main shaft at the time of acceleration to the 1st main shaft. It is a figure explaining switching of the power transmission path from the 1st main shaft at the time of deceleration to the 2nd main shaft. It is a figure explaining the collision with the jumping dog at the time of acceleration and a standby dog. It is a figure which shows the disassembled perspective view of the conventional 2nd switching device. It is a figure explaining the shape of the conventional key part. It is a figure explaining the shape of the conventional standby dog. It is a figure which shows the fragmentary sectional view at the time of the conventional jump dog and the waiting dog colliding. It is a figure explaining the shape of the key part in 1st Embodiment. It is a figure which shows the fragmentary perspective view of the dog member in 1st Embodiment. It is a figure which shows the fragmentary sectional view at the time of a jumping dog and a standby dog colliding. In a 2nd switching device of a 1st embodiment, a dog member and a rotating shaft of a hub shift relatively, and it is a figure explaining a case where a jump dog and a standby dog collide. It is a figure explaining the shape of the key part thickened in the circumferential direction. It is a disassembled perspective view of the 2nd switching apparatus in 2nd Embodiment. It is a figure explaining the shape of the key part in 2nd Embodiment. It is a figure which shows the fragmentary sectional view at the time of a jumping dog and a standby dog colliding. In the 2nd switching device of 2nd Embodiment, it is a figure explaining the case where the rotation axis | shaft of a dog member and a hub mutually shifts | deviates, and a jumping dog and standby | waiting collide.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiments are merely examples for facilitating understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related to the present invention are not illustrated. To do.

<First Embodiment>
(Outline of transmission 1)
FIG. 1 is a diagram showing an outline of a transmission 1 for an automobile. The transmission 1 according to this embodiment that transmits the driving force of the engine E to driving wheels is rotatably supported by a bearing held in a transmission case, and is connected to a crankshaft of the engine E via a starting clutch 2. An input shaft 3 is provided. The input shaft 3 is rotated by the driving force of the engine E, and the first input shaft 3a disposed on the upstream side of the power transmission path from the engine E and the second input shaft 3b disposed on the downstream side. The buffer mechanism 70 is provided between the first input shaft 3a and the second input shaft 3b. When a spike torque that causes torque fluctuations greater than the set torque occurs on the input shaft 3, the buffer mechanism 70 causes a sliding motion to cause the first input shaft 3a and the second input shaft 3b to rotate relative to each other so that the spike torque is reduced. Cut to preset torque.

  The transmission 1 includes a first main shaft 4 and a second main shaft 5 that are rotatably supported by bearings held in a transmission case and are disposed so as to be rotatable relative to the input shaft 3. The first main shaft 4 and the second main shaft 5 are arranged in parallel to the input shaft 3 and are arranged opposite to each other in the axial direction in a state where their axis centers coincide with each other. The first main shaft 4 is hollow, and the input shaft 3 (second input shaft 3b) is inserted into the first main shaft 4 so as to be relatively rotatable. Further, the transmission case accommodates an output shaft 6 that is rotatably supported by a bearing and arranged in parallel to the input shaft 3, the first main shaft 4, and the second main shaft 5.

  A plurality of drive gears Dv (first-speed drive gear 11 to fourth-speed drive gear 14) are fixed to the first main shaft 4 and the second main shaft 5, respectively. More specifically, a first-speed drive gear 11 and a third-speed drive gear 13 are fixed to the second main shaft 5, and a second-speed drive gear 12 and a fourth-speed drive gear are fixed to the first main shaft 4. The drive gear 14 is fixed. As described above, in the transmission 1 according to the present embodiment, the first main shaft 4 and the second main shaft 5 are provided with the multiple-stage drive gears Dv having different gear ratios, and the drive gears having the continuous gear ratio are provided. Dv is alternately arranged on the first main shaft 4 and the second main shaft 5.

  On the other hand, the output shaft 6 is connected to drive wheels, and is provided with a driven gear Dn (first-speed driven gear 21 to fourth-speed driven gear 24) that meshes with the drive gears Dv so as to be relatively rotatable. Further, the output shaft 6 is connected to the output shaft 6 with the driven gear Dn, and the driven gear Dn and the output shaft 6 are integrally rotated, and the output shaft 6 and the driven gear Dn are relatively disconnected. Gear switching mechanisms 60a and 60b that selectively switch any of the above are provided.

  The gear switching mechanism 60 a is provided between the first-speed driven gear 21 and the third-speed driven gear 23, and one of the first-speed driven gear 21 and the third-speed driven gear 23 is connected to the output shaft 6. At this time, either one of the first-speed driven gear 21 and the third-speed driven gear 23 is disconnected from the output shaft 6.

  More specifically, the gear switching mechanism 60a includes a hub 61a that is fixed to the output shaft 6 so as not to rotate relative to the output shaft 6 between the first-speed driven gear 21 and the third-speed driven gear 23, and the hub 61a. And a sleeve 62a held so as to be movable in the axial direction. A shift fork (not shown) is engaged with the outer periphery of the sleeve 62a, and is moved in the axial direction of the output shaft 6 by an actuator (electric cylinder or the like) not shown.

  The gear switching mechanism 60 a includes a hub 21 a fixed to the first-speed driven gear 21 and a hub 23 a fixed to the third-speed driven gear 23. The hubs 21a and 23a are arranged to face each other, and both are configured to be able to engage with the sleeve 62a. When the sleeve 62a is in the illustrated neutral position, the sleeve 62a is disconnected from the hub 21a of the first-speed driven gear 21 and the hub 23a of the third-speed driven gear 23, so that the first-speed driven gear 21 and the third-speed gear are used. The driven gear 23 rotates relative to the output shaft 6.

  On the other hand, when the sleeve 62a is moved to the first speed driven gear 21 side along the axial direction, the sleeve 62a engages with the hub 21a of the first speed driven gear 21, and the hub 61a of the output shaft 6 and 1 The hub 21a of the high speed driven gear 21 is bridged by the sleeve 62a. As a result, the first-speed driven gear 21 is connected to the output shaft 6, the first-speed driven gear 21 rotates integrally with the output shaft 6, and the third-speed driven gear 23 is disconnected from the output shaft 6, The third speed driven gear 23 rotates relative to the output shaft 6. When the sleeve 62a is moved along the axial direction toward the third-speed driven gear 23, the sleeve 62a engages with the hub 23a of the third-speed driven gear 23, and the hub 61a of the output shaft 6 and the third-speed driven gear. The 23 hubs 23a are bridged by the sleeve 62a. As a result, the 3-speed driven gear 23 is connected to the output shaft 6, the 3-speed driven gear 23 rotates integrally with the output shaft 6, and the 1-speed driven gear 21 is disconnected from the output shaft 6. The first speed driven gear 21 rotates relative to the output shaft 6.

  Although the gear switching mechanism 60a has been described here, the gear switching mechanism 60b is configured similarly to the gear switching mechanism 60a. That is, the gear switching mechanism 60b moves between the driven gear 22 for the second speed 22 and the driven gear 24 for the fourth speed so as not to rotate relative to the output shaft 6, and moves in the axial direction of the output shaft 6 to the hub 61b. A sleeve 62 b that is freely held, a hub 22 a fixed to the second-speed driven gear 22, and a hub 24 a fixed to the fourth-speed driven gear 24 are provided. When the sleeve 62b is in the illustrated neutral position, the sleeve 62b is disconnected from the hub 22a of the second-speed driven gear 22 and the hub 24a of the fourth-speed driven gear 24, so that the second-speed driven gear 22 and the fourth-speed gear are used. The driven gear 24 rotates relative to the output shaft 6.

  On the other hand, when the sleeve 62b is moved along the axial direction toward the second-speed driven gear 22, the sleeve 62b engages with the hub 22a of the second-speed driven gear 22, and the hub 61b of the output shaft 6 and the second-speed driven gear are engaged. The 22 hubs 22a are bridged by the sleeve 62b. As a result, the second speed driven gear 22 is connected to the output shaft 6, the second speed driven gear 22 rotates integrally with the output shaft 6, and the fourth speed driven gear 24 is disconnected from the output shaft 6, The 4-speed driven gear 24 rotates relative to the output shaft 6. When the sleeve 62b is moved along the axial direction toward the fourth speed driven gear 24, the sleeve 62b engages with the hub 24a of the fourth speed driven gear 24, and the hub 61b of the output shaft 6 and the fourth speed driven gear are engaged. 24 hubs 24a are bridged by the sleeve 62b. As a result, the 4-speed driven gear 24 is connected to the output shaft 6, the 4-speed driven gear 24 rotates integrally with the output shaft 6, and the 2-speed driven gear 22 is disconnected from the output shaft 6. The second speed driven gear 22 rotates relative to the output shaft 6.

  The sleeve 62a and the hub 21a of the first-speed driven gear 21; the sleeve 62a and the hub 23a of the third-speed driven gear 23; the sleeve 62b and the hub 22a of the second-speed driven gear 22; A synchromesh mechanism (synchronization mechanism) is provided between 62b and the hub 24a of the driven gear 24 for the fourth speed.

  As shown in FIG. 1, the transmission 1 includes a shaft switching mechanism 50 that selectively switches the transmission path of the rotational power of the input shaft 3 to either the first main shaft 4 or the second main shaft 5. ing. In the shaft switching mechanism 50, when the first main shaft 4 is selected as a power transmission path, the input shaft 3 and the first main shaft 4 are integrally rotated, and the second main shaft 5 is selected as a power transmission path. The input shaft 3 and the second main shaft 5 are rotated together. Hereinafter, the configuration of the shaft switching mechanism 50 will be described in detail.

(Configuration of the axis switching mechanism 50)
FIG. 2 is a schematic cross-sectional view illustrating the shaft switching mechanism 50 in the first embodiment. The shaft switching mechanism 50 is provided on the dog member 51 (second rotating body) provided on the second input shaft 3 b, the first switching device 50 a provided on the first main shaft 4, and the second main shaft 5. The second switching device 50b. As shown in FIGS. 1 and 2, the second input shaft 3 b is formed to have a longer shaft length than the first main shaft 4, and the end of the second input shaft 3 b where the buffer mechanism 70 is provided. The end on the opposite side protrudes in the axial direction from the hollow first main shaft 4. A dog member 51 is provided between the first main shaft 4 and the second main shaft 5, that is, a portion protruding from the first main shaft 4 in the second input shaft 3 b.

  The dog member 51 is spline-engaged with the end of the second input shaft 3b, and rotates integrally with the second input shaft 3b while the movement in the axial direction is restricted. As will be described in detail later, the dog member 51 has a standby dog 52a (second dog) on the end face located on the first switching device 50a side, and a standby dog 52b (second dog) on the end face located on the second switching device 50b side. However, a plurality (three in the present embodiment) are provided protruding at regular intervals in the circumferential direction.

  The first switching device 50a is provided at the end of the first main shaft 4 on the dog member 51 side, and the second switching device 50b is provided at the end of the second main shaft 5 on the dog member 51 side. It has been. The first switching device 50a and the second switching device 50b have the same configuration except that some parts have different dimensions.

  Further, the first switching device 50a and the second switching device 50b are respectively provided with a drive-side sleeve 53 (first shaft) that is movable in the axial direction of the first main shaft 4 and the second main shaft 5 (hereinafter simply referred to as the axial direction). 1 rotation body) and the coast side sleeve 54 (1st rotation body) are provided.

  FIG. 3 is an exploded perspective view of the second switching device 50b according to the first embodiment. The second switching device 50b includes both the drive-side sleeve 53 and the coast-side sleeve 54, and the struck surface to be described later acts in the same manner on both of them. Illustration and description are omitted.

  As shown in FIG. 3, the second switching device 50 b includes a substantially cylindrical hub 55 that is fixed to the second main shaft 5 and rotates integrally with the second main shaft 5. On the outer peripheral surface of the hub 55, a plurality of grooves 55 a that are recessed inward in the radial direction of the hub 55 and extend in the axial direction are formed at equal intervals in the circumferential direction of the second main shaft 5 (hereinafter simply referred to as the circumferential direction). Has been. The groove 55a is formed such that, for example, a side surface 55aa and a side surface 55ab of an involute curve are opposed to each other in which the groove width (width in the circumferential direction) gradually increases toward the outer side in the radial direction.

  The dog member 51 has a through hole 51a that penetrates in the axial direction and has a spline groove (not shown). The dog member 51 is disposed opposite to the hub 55 in the axial direction, with the second input shaft 3 b inserted through the through hole 51 a. Further, as described above, a plurality of standby dogs 52b are arranged at equal intervals in the circumferential direction (rotation direction) on the outer peripheral side of the dog member 51.

  The drive-side sleeve 53 has an annular ring portion 53a, and the hub 55 is inserted through the center of the ring portion 53a. The drive side sleeve 53 has a key portion 53b. The key portion 53 b protrudes inward in the radial direction of the ring portion 53 a from the ring portion 53 a and extends in the axial direction toward the dog member 51. Further, the key portion 53b is formed with a torque transmission surface 53ba and a torque transmission surface 53bb whose key width (width in the circumferential direction) gradually increases toward the radially outer side. The key portion 53b is fitted into the groove 55a of the hub 55 so that the torque transmission surface 53ba and the torque transmission surface 53bb come into contact with the side surface 55aa and the side surface 55ab of the groove 55a in a surface contact state. When the key portion 53b slides in the groove 55a of the hub 55, the key portion 53b moves in the axial direction.

  Since the key portion 53b is fitted in the groove 55a of the hub 55, the drive-side sleeve 53 is restricted from rotating relative to the hub 55 and rotates together with the second main shaft 5 and the hub 55. .

  A plurality (three in this case) of key portions 53b are arranged at equal intervals in the circumferential direction (rotation direction), and a jump dog 53c (first dog) that can mesh with the standby dog 52b is disposed at the tip of the key portion 53b. ) Is formed. The shape of the jump dog 53c will be described later.

  As shown in FIGS. 1 and 2, the shift fork 7 is engaged with the drive side sleeve 53 and the coast side sleeve 54. The shift fork 7 moves in the axial direction in response to a pressing force from the actuator 8 driven by the control of the control unit 10 shown in FIG. An urging portion 9 formed of a coil spring is disposed between the shift fork 7 and the actuator 8, that is, in the transmission path of the pressing force from the actuator 8 to the drive side sleeve 53 and the coast side sleeve 54. The urging portion 9 is elastically deformed in response to the pressing force from the actuator 8 and the reaction force from the drive side sleeve 53 and the coast side sleeve 54. Then, the shift fork 7 is moved to mesh the jump dog 53c and the standby dog 52b, or release the mesh.

  FIG. 4 is a side view of the second switching device 50 b, and shows the vicinity of the jump dog 53 c of the drive side sleeve 53 and the standby dog 52 b of the dog member 51. In FIG. 4A, the jump dog 53 c of the drive side sleeve 53 and the standby dog 52 b of the dog member 51 are not meshed with each other. In this state, the drive side sleeve 53 rotates together with the second main shaft 5 together with the hub 55. On the other hand, the dog member 51 is rotatable relative to the second main shaft 5.

  Then, the shift fork 7 described above moves the drive side sleeve 53 to the dog member 51 side. Then, as shown in FIG. 4B, the jump dog 53 c of the drive-side sleeve 53 enters the circumferential gap between the plurality of standby dogs 52 b provided on the dog member 51.

  As described above, when the dog member 51 and the drive-side sleeve 53 are relatively moved in the proximity direction close to each other from FIG. 4A to FIG. 4B, the standby dog 52 b and the drive-side sleeve 53 are provided. The jump dog 53c meshes, and the standby dog 52b and the jump dog 53c are in a power transmission state in which they rotate integrally.

  Further, when the dog member 51 and the drive side sleeve 53 move relative to each other in the separating direction from FIG. 4B to FIG. 4A, the dog member 51 and the drive side sleeve 53 are disengaged from each other and wait. The dog 52b and the jump dog 53c are in a separated state in which they rotate relative to each other.

  FIG. 5 is a diagram illustrating switching of the power transmission path from the second main shaft 5 to the first main shaft 4 during acceleration. In the following, “acceleration” means a state in which the vehicle is accelerated by the driving force of the engine E, and does not mean a state in which the vehicle is accelerated by its own weight when going down a hill, for example. As shown in FIG. 5, in the shaft switching mechanism 50, the first switching device 50a is arranged on one side of the dog member 51 provided with the standby dog 52a, and the other of the dog members 51 provided with the standby dog 52b. The second switching device 50b is disposed on the side surface of the. Hereinafter, during forward travel of the vehicle, the dog member 51 (input shaft 3), the first switching device 50a (first main shaft 4), and the second switching device 50b (second main shaft 5) are all solid arrows. It demonstrates as what rotates in the direction shown.

  The standby dog 52a is formed with a leading surface 52af positioned on the front side in the rotation direction of the dog member 51 (input shaft 3) and a trailing surface 52ar positioned on the rear side in the rotation direction. The standby dog 52a has a wider width in the rotation direction of the dog member 51 (input shaft 3) on the distal end side (first switching device 50a side) than the proximal end side (dog member 51 side) in the projecting direction. That is, the tip has a wide shape. Similarly, the standby dog 52b includes a leading surface 52bf located on the front side in the rotational direction of the dog member 51 (input shaft 3) and a trailing surface 52br located on the rear side in the rotational direction. In the standby dog 52b, the width of the dog member 51 (input shaft 3) in the rotational direction is wider on the distal end side (second switching device 50b side) than the proximal end side (dog member 51 side) in the projecting direction. That is, the tip has a wide shape.

  The jump dog 53c of the drive side sleeve 53 of the first switching device 50a is formed with a leading surface 53f that can be engaged with the leading surface 52af of the standby dog 52a, and the coast side sleeve 54 of the first switching device 50a. The jumping dog 54c has a trailing surface 54r that can be engaged with the trailing surface 52ar of the standby dog 52a. The leading surface 53f and the trailing surface 54r are formed in a tapered shape so as to engage with the leading surface 52af and the trailing surface 52ar of the standby dog 52a in a surface contact state, respectively.

  On the other hand, the jump dog 53c of the drive side sleeve 53 of the second switching device 50b includes a leading surface 53f that can be engaged with the leading surface 52bf of the standby dog 52b, and the coast side sleeve of the second switching device 50b. The jumping dog 54c 54 includes a trailing surface 54r that can be engaged with the trailing surface 52br of the standby dog 52b. The leading surface 53f and the trailing surface 54r are formed in a tapered shape so as to engage with the leading surface 52bf and the trailing surface 52br of the standby dog 52b in a surface contact state, respectively.

  Then, as shown in FIG. 5A, when the control unit 10 does not control the actuator 8, that is, when both the first switching device 50a and the second switching device 50b are in the disconnected state, Both 53c and jump dog 54c are held at positions separated from dog member 51. At this time, the jump dog 53c and the jump dog 54c are not engaged with the standby dog 52a and the standby dog 52b, and the first main shaft 4 and the second main shaft 5 are connected to the input shaft 3. Separated and maintained in a relatively rotatable state.

  For example, when shifting the gear stage to the first speed from the above state, the second switching device 50b is set in the connected state, and the input shaft 3 and the second main shaft 5 are integrally rotated via the second switching device 50b. Let More specifically, when shifting to the first speed, the control unit 10 moves the sleeve 62a of the gear switching mechanism 60a to the first-speed driven gear 21 side in advance as described in FIG. The first gear driven gear 21 is connected to rotate integrally.

  In this state, the control unit 10 controls the actuator 8 to move the jump dog 53c and the jump dog 54c of the second switching device 50b to the dog member 51 side as shown in FIG. . At this time, the leading surface 53f of the jumping dog 53c is engaged with the leading surface 52bf of the standby dog 52b, and the rotational power of the input shaft 3 is supplied via the standby dog 52b and the jumping dog 53c of the dog member 51. It is transmitted to the main shaft 5 and the input shaft 3 and the second main shaft 5 rotate together. Thereby, the driving force of the engine E is driven through the input shaft 3, the dog member 51, the second switching device 50 b, the second main shaft 5, the first speed drive gear 11, the first speed driven gear 21 and the output shaft 6. It is transmitted to the wheel (see FIG. 1).

  Further, when upshifting from the first speed to the second speed in the acceleration state of the vehicle, the control unit 10 controls the actuator 8 as follows. That is, when upshifting from the first speed to the second speed, the control unit 10 moves the sleeve 62b of the gear switching mechanism 60b to the second speed driven gear 22 side in advance, and the output shaft 6 and the second speed driven gear 22 are integrated. A rotating connection state is set (see FIG. 1). As a result, the rotational power of the output shaft 6 is transmitted to the first main shaft 4 via the second-speed driven gear 22 and the second-speed drive gear 12, and the first main shaft 4 enters a rotating state.

  At this time, since the rotation speed of the first main shaft 4 is smaller than that of the dog member 51 (input shaft 3), differential rotation occurs between the dog member 51 and the first switching device 50a. In this state, the control unit 10 controls the actuator 8 to move the jump dog 54c of the second switching device 50b in a direction away from the dog member 51, as shown in FIG. The jump dog 53c of the first switching device 50a is moved to the dog member 51 side.

  In the first speed acceleration state, the leading surface 53f of the jumping dog 53c in the second switching device 50b is engaged with the leading surface 52bf of the standby dog 52b, but the trailing dog 52c and the standby dog 52b are trailing. The surface 52br is maintained in a disengaged state. Accordingly, the jump dog 54 c of the second switching device 50 b is movable in a direction away from the dog member 51.

  And as shown in FIG.5 (c), in the state which the differential rotation produced between the dog member 51 and the 1st switching device 50a, the jump dog 53c of the 1st switching device 50a is on the dog member 51 side. As shown in FIG. 5D, the leading surface 53f of the jump dog 53c of the first switching device 50a engages with the leading surface 52af of the standby dog 52a. As described above, when the jump dog 53c of the first switching device 50a is engaged with the standby dog 52a, the power transmission path is instantaneously maintained while the second main shaft 5 and the input shaft 3 maintain the power transmission state. Switch to the first main shaft 4 side. In other words, the power transmission path instantaneously switches to the second-speed drive gear 12 and the second-speed driven gear 22 while maintaining the power transmission state via the first-speed drive gear 11 and the first-speed driven gear 21. Thus, the gear shift is performed without causing torque interruption.

  At this time, when the jump dog 53c of the first switching device 50a and the standby dog 52a of the dog member 51 are engaged, the rotational speed of the input shaft 3 is decreased. As a result, the rotation speed of the jump dog 53c of the second switching device 50b is larger than the rotation speed of the dog member 51, and the relationship between the jump dog 53c of the second switch device 50b and the standby dog 52b of the dog member 51 is increased. The match is released. Therefore, the control unit 10 controls the actuator 8 to move the jump dog 54 c of the first switching device 50 a toward the dog member 51, and separates the jump dog 53 c of the second switching device 50 b from the dog member 51. Move in the direction you want. At the same time, the gear switching mechanism 60a is controlled so that the first speed driven gear 21 and the output shaft 6 are disconnected. As a result, as shown in FIG. 5E, the upshift during acceleration from the first speed to the second speed is completed.

  As described above, according to the transmission 1 of the present embodiment, it is possible to perform an upshift without causing torque interruption. Here, the upshift during acceleration from the first speed to the second speed has been described, but the upshift during acceleration from the third speed to the fourth speed is the same as described above.

  FIG. 6 is a diagram illustrating switching of the power transmission path from the first main shaft 4 to the second main shaft 5 during deceleration. In the following, “deceleration” refers to a vehicle deceleration state due to engine braking, and does not refer to a state where the vehicle decelerates when going up a hill. For example, as described above, it is assumed that the first main shaft 4 and the input shaft 3 are in a connected state after being upshifted from the first speed to the second speed. When the vehicle is traveling in the second speed deceleration state, as shown in FIG. 6A, the trailing surface 54r of the jump dog 54c in the first switching device 50a is the tray of the standby dog 52a. The input shaft 3 and the first main shaft 4 are integrally rotated via the jump dog 54c of the first switching device 50a and the standby dog 52a of the dog member 51.

  In the above state, when downshifting from the second speed to the first speed, the control unit 10 controls the actuator 8 as follows. That is, when downshifting from the second speed to the first speed, the control unit 10 moves the sleeve 62a of the gear switching mechanism 60a to the first-speed driven gear 21 side in advance, so that the output shaft 6 and the first-speed driven gear 21 are integrated. A rotating connection state is set (see FIG. 1). As a result, the rotational power of the output shaft 6 is transmitted to the second main shaft 5 via the first-speed driven gear 21 and the first-speed drive gear 11, and the second main shaft 5 enters a rotating state.

  At this time, since the rotation speed of the second main shaft 5 is larger than that of the dog member 51 (input shaft 3), differential rotation occurs between the dog member 51 and the second switching device 50b. In this state, the control unit 10 controls the actuator 8 to move the jump dog 53c of the first switching device 50a in the direction away from the dog member 51, as shown in FIG. The jump dog 54c of the second switching device 50b is moved to the dog member 51 side.

  In the second speed deceleration state, the trailing surface 54r of the jump dog 54c in the first switching device 50a is engaged with the trailing surface 52ar of the standby dog 52a, but the jump dog 53c and the standby dog 52a The leading surface 52af is maintained in a non-engaged state. Therefore, the jump dog 53 c of the first switching device 50 a is movable in a direction away from the dog member 51.

  Then, when the jump dog 54c of the second switching device 50b moves to the dog member 51 side in a state where a differential rotation has occurred between the dog member 51 and the second switching device 50b, it is shown in FIG. As described above, the trailing surface 54r of the jump dog 54c of the second switching device 50b is engaged with the trailing surface 52br of the standby dog 52b. As described above, when the dive dog 54c of the second switching device 50b is engaged with the standby dog 52b, the power transmission path is instantaneously maintained while the first main shaft 4 and the input shaft 3 maintain the power transmission state. Switch to the second main shaft 5 side. In other words, the power transmission path instantaneously switches to the first-speed drive gear 11 and the first-speed driven gear 21 while maintaining the power transmission state via the second-speed drive gear 12 and the second-speed driven gear 22. Thus, the gear shift is performed without causing torque interruption.

  At this time, when the dive dog 54c of the second switching device 50b and the standby dog 52b of the dog member 51 are engaged, the rotational speed of the input shaft 3 is increased. Thereby, the rotation speed of the jump dog 54c of the first switching device 50a becomes smaller than the rotation speed of the dog member 51, and the relationship between the jump dog 54c of the first switch device 50a and the standby dog 52a of the dog member 51 is obtained. The match is released. Therefore, the control unit 10 controls the actuator 8 to move the jump dog 54c of the first switching device 50a in the direction away from the dog member 51, and also moves the jump dog 53c of the second switching device 50b to the dog member. Move to 51 side. At the same time, the gear switching mechanism 60b is controlled so that the second speed driven gear 22 and the output shaft 6 are disconnected. As a result, as shown in FIG. 6D, the downshift at the time of deceleration from the second speed to the first speed is completed.

  Thus, according to the transmission 1 of the present embodiment, it is possible to perform a downshift without causing torque interruption. Here, the downshift at the time of deceleration from the 2nd speed to the 1st speed has been described, but the downshift at the time of deceleration from the 4th speed to the 3rd speed is the same as described above.

  As described above, according to the transmission 1, the jump dog 53c and the jump dog 54c of the first switching device 50a are moved to the standby dog 52a side, and the leading surface 52af and the jump dog 53c of the standby dog 52a are moved. Is engaged, or the trailing surface 52ar of the standby dog 52a and the jump dog 54c are engaged, and the input shaft 3 and the first main shaft 4 are in a power transmission state in which the input shaft 3 and the first main shaft 4 rotate integrally. Further, the jump dog 53c and the jump dog 54c of the second switching device 50b are moved to the standby dog 52b side, and the leading surface 52bf of the standby dog 52b and the jump dog 53c are engaged, or the standby The trailing surface 52br of the dog 52b and the jump dog 54c are engaged, and a power transmission state in which the input shaft 3 and the second main shaft 5 rotate integrally is brought about.

  FIG. 7 is a diagram for explaining a collision between the jump dog 53c and the standby dog 52b during acceleration. Here, in the acceleration upshift from the first speed to the second speed, the jump dog 53c of the first switching device 50a is engaged with the standby dog 52a of the dog member 51 as shown in FIG. The rotational speed of the jumping dog 53 c of the second switching device 50 b is larger than the rotational speed of the dog member 51. At this time, the engagement between the jump dog 53c of the second switching device 50b and the standby dog 52b of the dog member 51 is released, and the control unit 10 controls the actuator 8 to control the jump dog of the second switching device 50b. 53c is moved away from the dog member 51. However, as shown in FIG. 7B, before the jump dog 53c of the second switching device 50b is pulled out from the standby dog 52b of the dog member 51, the jump dog 53c and the standby dog 52b may collide. .

  Further, in the downshift at the time of deceleration from the second speed to the first speed, the jump dog 54c of the second switching device 50b is engaged with the standby dog 52b of the dog member 51 as shown in FIG. The rotational speed of the jump dog 54 c of the first switching device 50 a is smaller than the rotational speed of the dog member 51. At this time, the engagement between the jump dog 54c of the first switching device 50a and the standby dog 52a of the dog member 51 is released, and the control unit 10 controls the actuator 8 to control the jump dog of the first switching device 50a. 54c is moved away from the dog member 51. However, before the jump dog 54c of the first switching device 50a is pulled out from the standby dog 52a of the dog member 51, the jump dog 54c and the standby dog 52a may collide as in acceleration.

  FIG. 8 is an exploded perspective view of a conventional second switching device 150b. Here, the conventional second switching device 150b will be described. As shown in FIG. 8, the second switching device 150b includes a dog member 151, a drive side sleeve 153, a hub 55, and the like. The second switching device 150b includes both the drive-side sleeve 153 and the coast-side sleeve, and the struck surface described later acts in the same manner for both of them, so here the coast-side sleeve is Illustration and description are omitted. Moreover, the same code | symbol is attached | subjected about the structure same as the 2nd switching apparatus 50b in 1st Embodiment, and the description is abbreviate | omitted.

  In the dog member 151, a plurality of standby dogs 152 a and standby dogs 152 b are arranged at equal intervals in the circumferential direction (rotation direction) on the outer peripheral side of the dog member 151. A plurality of (here, three) key portions 153b of the drive-side sleeve 153 are arranged at equal intervals in the circumferential direction (rotation direction), and a jump dog that can mesh with the standby dog 152b is disposed at the tip of the key portion 153b. 153c is formed.

  FIG. 9 is a diagram illustrating the shape of a conventional key portion 153b. 9A is a perspective view of the key portion 153b, FIG. 9B is a top view of the key portion 153b, and FIG. 9C is a front view of the key portion 153b.

  As shown in FIG. 9A, the jump dog 153c formed at the tip of the conventional key portion 153b is formed with a bounce surface 153g that can be engaged with the leading surface 152bf (FIG. 10) of the standby dog 152b. ing. The bounce surface 153g is formed on the other circumferential side opposite to the leading surface 153f formed on one circumferential side. As shown in FIG. 9B, the bounce surface 153g has a circumferential direction of the key portion 153b on a plane through which a straight line L1 extending in the width direction of the key portion 153b and a straight line L2 perpendicular to the straight line L1 pass. With respect to the center, the inclination angle θ1 (acute angle, for example, 40 degrees) is inclined in the direction opposite to the leading surface 153f with respect to the straight line L1 and in the terminal direction. Further, as shown in FIG. 9C, the bounce surface 153g is opposite to the reading surface 153f with respect to the straight line L1 on the plane orthogonal to the rotation axis direction with respect to the radial center of the key portion 153b. It is a direction and is inclined by the inclination angle θ2 (acute angle) radially outward. In other words, the bounce surface 153g is inclined from one side to the other side in the circumferential direction as it goes from the inner side to the outer side in the radial direction on a plane orthogonal to the rotation axis direction. That is, the bounce surface 153g is formed along a plane through which a straight line L3 inclined at an inclination angle θ1 with respect to the straight line L1 and a straight line L4 inclined at an inclination angle θ2 with respect to the straight line L1 pass.

  FIG. 10 is a diagram illustrating the shape of a conventional standby dog 152b. As shown in FIG. 10, the standby dog 152 b of the conventional dog member 151 has a circumferential width that gradually decreases outward in the radial direction, and the trailing surface 152 br and the facing surface 152 ba that faces the hub 55. In the meantime, a collision surface 152bb is formed which is repelled when the dive dog 153c and the standby dog 152b collide with each other and comes into surface contact with the surface 153g. Further, the standby dog 152b is formed between the leading surface 152bf and the facing surface 152ba, and a repelling surface formed on the coasting sleeve jump dog when the coast dog jump dog and the standby dog 152b collide with each other. A collision surface 152bc that comes into surface contact is formed.

  Therefore, in the conventional second switching device 150b, for example, when the jump dog 153c and the standby dog 152b collide in the upshift from the first speed to the second speed, the bounce surface 153g of the jump dog 153c The collision surface 152bb of the standby dog 152b may come into surface contact.

  FIG. 11 is a diagram showing a partial cross-sectional view when the conventional jump dog 153c and the standby dog 152b collide with each other. When the jumping dog 153c and the standby dog 152b collide, a force in a direction away from the dog member 151 (see FIG. 8) is input to the key portion 153b, so that the drive side sleeve 153 is removed from the dog member 151. Move in the direction of separation. As shown in FIG. 11, the key portion 153b has a force F1 in a direction orthogonal to the collision surface 152bb (bounce surface 153g) and a side surface 55aa of the groove 55a as a force in a direction orthogonal to the rotation axis direction. The resultant force F3 with the reaction force F2 in the torque transmission direction determined by the pressure angle of the (torque transmission surface 53ba) is input. As can be seen from FIG. 11, the resultant force F3 input to the key portion 153b is input as a force directed outward in the radial direction. Thus, if the resultant force F3 is input as a force directed radially outward, the jump dog 153c and the standby dog 152b may be deformed or damaged. In order to prevent these, it is conceivable to increase the rigidity by increasing the thickness of the key portion 153b in the circumferential direction, but this leads to an increase in size and an increase in mass of the second switching device 150b. In order to solve this problem, the key portion 53b of the first embodiment has the following shape.

  FIG. 12 is a diagram illustrating the shape of the key portion 53b in the first embodiment. 12A is a perspective view of the key portion 53b, FIG. 12B is a top view of the key portion 53b, and FIG. 12C is a front view of the key portion 53b. As shown in FIG. 12A, the jumping dog 53c formed at the tip of the key portion 53b is formed with a bounce surface 53g that can be engaged with the leading surface 52bf (FIG. 13) of the standby dog 52b. . That is, the bounce surface 53g is provided on the other circumferential side opposite to the leading surface 53f formed on one circumferential side. As shown in FIG. 12 (b), the bounce surface 53g has a circumferential direction of the key portion 53b on a plane through which a straight line L11 extending in the width direction of the key portion 53b and a straight line L12 in the rotation axis direction orthogonal to the straight line L11 pass. With respect to the center, it is inclined with respect to the straight line L11 by the inclination angle θ11 (acute angle, for example, 40 degrees) in the direction opposite to the leading surface 53f and in the terminal direction. Further, as shown in FIG. 12C, the bounce surface 53g is relative to the straight line L11 with respect to the straight line L11 with respect to the straight line L11 on the plane orthogonal to the rotation axis direction. Inclined by an inclination angle θ12 (obtuse angle) opposite to the leading surface 53f and radially outward. In other words, the repelling surface 53g is inclined from the other side in the circumferential direction toward one side as it goes from the inner side to the outer side in the radial direction on a plane orthogonal to the rotation axis direction. That is, the bounce surface 53g is formed along a plane through which a straight line L13 inclined at an inclination angle θ11 with respect to the straight line L11 and a straight line L14 inclined at an inclination angle θ12 with respect to the straight line L11 pass. The inclination angle θ12 is set so that the torque transmission direction determined by the pressure angle of the collision surface 52bb (bounce surface 53g) and the bounce surface 53g are orthogonal to each other on a plane orthogonal to the rotation axis direction. .

  FIG. 13 is a partial perspective view of the dog member 51 according to the first embodiment. As shown in FIG. 13, the standby dog 52 b of the dog member 51 has a circumferential width that gradually increases outward in the radial direction, and between the trailing surface 52 br and the opposing surface 52 ba facing the hub 55. A collision surface 52bb that is repelled when the jump dog 53c collides with the standby dog 52b and makes surface contact with the surface 53g is formed. Further, the standby dog 52b has a collision that makes surface contact with the repelling surface of the jump dog 54c when the jump dog 54c of the coast side sleeve 54 and the standby dog 52b collide between the leading surface 52bf and the facing surface 52ba. A surface 52bc is formed.

  Therefore, in the second switching device 50b, when the jump dog 53c and the standby dog 52b collide, the struck surface 53g of the jump dog 53c and the collision surface 52bb of the standby dog 52b may collide with each other.

  FIG. 14 is a partial cross-sectional view when the jumping dog 53c and the standby dog 52b collide with each other. The key portion 53b has a direction in which the drive-side sleeve 53 (see FIG. 3) is separated from the dog member 51 because the bounce surface 53g is inclined at an inclination angle θ11 when the jump dog 53c and the standby dog 52b collide. This force is input, and the drive-side sleeve 53 moves in a direction away from the dog member 51. Further, as shown in FIG. 14, the key portion 53b includes a force F11 in a direction orthogonal to the collision surface 52bb (bounce surface 53g) and a side surface 55aa ( The resultant force with the reaction force F12 in the torque transmission direction determined by the pressure angle of the torque transmission surface 53bb) is input. As can be seen from FIG. 14, the force F11 and the reaction force F12 input to the key portion 53b are opposite to each other on a straight line, so that the force F11 and the reaction force F12 cancel each other, and the radial direction The resultant force facing outward is not input to the key portion 53b. As a result, the jumping dog 53c and the standby dog 52a are not deformed or damaged, and the key portion 53b is not thickened in the circumferential direction, thereby preventing the second switching device 50b from increasing in size and mass. can do.

<Second Embodiment>
FIG. 15 is a diagram for explaining a case where the rotation axis of the dog member 51 and the hub 55 is relatively displaced and the jump dog 53c and the standby dog 52b collide with each other in the second switching device 50b of the first embodiment. It is. Here, in the second switching device 50b according to the first embodiment, the distance H1 (see FIG. 16C) from the tip on the radially innermost side of the key portion 53b to the torque transmission surface 53bb is equal to the standby dog 52b. The shape of the bounce surface 53g is determined so as to be longer than the height H2 in the rotation axis direction. Therefore, even if the jumping dog 53c and the standby dog 52b collide, the collision surface 52bb of the standby dog 52 comes into contact with the bounced surface 53g of the jumping dog 53c, and the collision surface 52bb of the standby dog 52 becomes the key portion 53b. The torque transmission surface 53bb is not contacted.

  However, if the rotation shafts of the dog member 51 and the hub 55 are relatively displaced due to some circumstances, the collision surface 52bb of the standby dog 52b contacts the repelling surface 53g of the jumping dog 53c as shown in FIG. Without being able to contact the radial direction inner side of the torque transmission surface 53bb of the key portion 53b. Further, for example, the shape of the standby dog 52b is deformed, and the distance H1 from the tip on the radially innermost side of the standby dog 52b to the torque transmission surface 53bb becomes shorter than the height H2 of the standby dog 52b in the rotation axis direction. . In such a case, the collision surface 52bb of the standby dog 52 does not come into contact with the bounce surface 53g of the jump dog 53c, but comes into contact with the torque transmission surface 53bb of the key portion 53b. Thus, as a method of avoiding contact between the collision surface 52bb of the standby dog 52b and the torque transmission surface 53bb of the key portion 53b, it is conceivable to increase the thickness of the key portion 53b in the circumferential direction.

  FIG. 16 is a diagram illustrating the shape of the key portion 253b that is thickened in the circumferential direction. 16 (a) shows a perspective view of the key portion 253b thickened in the circumferential direction, FIG. 16 (b) shows a side view of the key portion 253b thickened in the circumferential direction, and FIG. The side view of the key part 53b in 1 embodiment is shown. As shown in FIG. 16A, the key portion 253b thickened in the circumferential direction with respect to the key portion 53b in the first embodiment is a first plane on the same plane as the key portion 53b in the first embodiment. The repelling surface 253g is formed wider than the key portion 53b in the embodiment. As shown in FIGS. 16 (a) and 16 (b), in the key portion 253b thickened in the circumferential direction, a distance H3 from the tip on the radially innermost side to the torque transmission surface 53bb is set to the first embodiment. Can be made longer than the distance H1 from the tip on the radially innermost side of the key portion 53b to the torque transmission surface 53bb. Thereby, even when the rotating shafts of the dog member 51 and the hub 55 are relatively displaced, it is possible to avoid contact between the collision surface 52bb of the standby dog 52b and the torque transmission surface 53bb of the key portion 253b. However, since the key portion 253b is thicker in the circumferential direction than the key portion 53b in the first embodiment, the key portion 253b is increased in size and mass. Therefore, in the second embodiment, the circumferential width of the key portion 53b in the first embodiment is the same, and the distance from the tip on the radially innermost side to the torque transmission surface 53bb is increased.

  FIG. 17 is an exploded perspective view of the second switching device 350b in the second embodiment. As shown in FIG. 17, the second switching device 350 b is provided with a drive side sleeve 353 instead of the drive side sleeve 53 in the first embodiment. The second switching device 350b includes both a drive-side sleeve 353 and a coast-side sleeve, and a struck surface and a chamfered surface, which will be described later, act in the same manner on both of them. The illustration and description are omitted. The second switching device 350b of the second embodiment has the same configuration as that of the first embodiment except for the drive side sleeve 353, and here, the same configuration as that of the first embodiment. Description of is omitted. Further, in the second switching device 350b, the same reference numerals are given to the configurations having the same shape as the drive-side sleeve 53 of the first embodiment, and the description thereof is omitted.

  The drive side sleeve 353 includes a ring portion 53a and a key portion 353b. The key portion 353b protrudes radially inward from the ring portion 53a and extends in the axial direction toward the dog member 51. The key portion 353b has a torque transmission surface 53ba and a torque transmission surface 53bb. The key portion 353b is fitted into the groove 55a of the hub 55 so that the torque transmission surface 53ba and the torque transmission surface 53bb are in contact with the side surface 55aa and the side surface 55ab of the groove 55a, respectively, and the drive side sleeve 353 is The key portion 353b slides in the groove 55a of the hub 55 to move in the axial direction.

  Since the key portion 353b is fitted in the groove 55a of the hub 55, the drive side sleeve 353 is restricted from rotating relative to the hub 55 and rotates together with the second main shaft 5 and the hub 55. .

  A plurality of (three in this case) key portions 353b are arranged at equal intervals in the circumferential direction (rotation direction), and a jump dog 353c (first dog) that can mesh with the standby dog 52b is disposed at the tip of the key portion 353b. ) Is formed.

  FIG. 18 is a diagram illustrating the shape of the key portion 353b in the second embodiment. 18A is a perspective view of the key portion 353b, FIG. 18B is a top view of the key portion 353b, and FIG. 18C is a front view of the key portion 353b. (D) is a side view of the key part 353b. As shown in FIG. 18 (a), the jumping dog 353c formed at the tip of the key portion 353b is repelled on the other circumferential side opposite to the leading surface 53f formed on one circumferential side. 353g and a chamfered surface 353h are formed. The bounce surface 353g is formed on the radially outer side of the chamfered surface 353h. As shown in FIG. 18B, the bounce surface 353g has a circumferential direction of the key portion 353b on a plane through which a straight line L11 extending in the width direction of the key portion 353b and a straight line L12 in the rotation axis direction orthogonal to the straight line L11 pass. With respect to the center, the inclination angle θ11 is inclined in the direction opposite to the leading surface 53f and in the distal direction with respect to the straight line L11. Further, as shown in FIG. 18C, the bounce surface 353g is relative to the straight line L11 with respect to the straight line L11 with respect to the straight line L11 on the plane orthogonal to the rotation axis direction. The inclination angle θ12 is inclined in the opposite direction to the leading surface 53f and radially outward. In other words, the bounce surface 353g is inclined from the other in the circumferential direction toward one side as it goes from the inner side to the outer side in the radial direction on a plane orthogonal to the rotation axis direction. That is, the bounce surface 353g is radially outward of the jump dog 353c along a plane through which a straight line L13 inclined at an inclination angle θ11 with respect to the straight line L11 and a straight line L14 inclined at an inclination angle θ12 with respect to the straight line L11 pass. Is formed.

  The chamfered surface 353h is inclined at an inclination angle θ11 on a plane through which the straight line L11 and the straight line L12 pass. Further, as shown in FIG. 18C, the chamfered surface 353h is read with respect to the straight line L11 with respect to the straight line L11 on the plane orthogonal to the rotation axis direction with respect to the radial center of the key portion 353b. The tilt angle θ13 (obtuse angle) is tilted in the direction opposite to the surface 53f and radially inward. That is, the chamfered surface 353h is formed on the radial inner side of the jump dog 353c along the plane through which the straight line L13 inclined by the inclination angle θ11 with respect to the straight line L11 and the straight line L15 inclined by the inclination angle θ13 with respect to the straight line L11 pass. Has been. In other words, the chamfered surface 353h is inclined from one side in the circumferential direction toward the other side in the radial direction from the inner side to the outer side on a plane orthogonal to the rotation axis direction. Thereby, in the key portion 353b, as shown in FIG. 18D, the radially inner distance H3 from the radially innermost tip to the torque transmission surface 53bb is set to the radial direction of the key portion 53b in the first embodiment. The distance H1 from the tip on the innermost side to the torque transmission surface 53bb (see FIG. 16C) can be made longer.

  When the dog member 351 and the hub 55 are arranged on the same axis, the jump dog 353c is similar to the jump dog 53c in the first embodiment as the jump dog 353c and the standby dog 52b. When the collision occurs, the bounce surface 353g of the jump dog 353c and the collision surface 52bb of the standby dog 52b collide.

  FIG. 19 is a diagram showing a partial cross-sectional view when the jumping dog 353c and the standby dog 52b collide with each other. The key portion 353b receives a force in a direction away from the dog member 51 from the dog member 51 because the bounced surface 353g is inclined at an inclination angle θ11 when the jump dog 353c and the standby dog 52b collide. Move in the direction of separation. Further, as shown in FIG. 19, the key portion 353b has a force F21 in a direction orthogonal to the collision surface 52bb (bounce surface 353g) and a side surface 55aa of the groove 55a as a force in a surface direction orthogonal to the rotation axis direction. The resultant force with the reaction force F22 in the torque transmission direction determined by the pressure angle of the torque transmission surface 53bb) is input. As can be seen from FIG. 19, the force F21 and the reaction force F22 input to the key portion 353b are opposite to each other on a straight line, so that the force F21 and the reaction force F22 cancel each other, and the radial direction The resultant force facing outward is not input to the key portion 353b. Accordingly, the jump dog 353c and the standby dog 52b are not deformed or damaged, and the second switching device 50b can be prevented from being enlarged and increased in mass.

  FIG. 20 is a diagram for explaining a case where the rotation axis of the dog member 51 and the hub 55 are relatively displaced and the jump dog 353c and the standby dog 52b collide with each other in the second switching device 350b of the second embodiment. It is. As shown in FIG. 20, even if the rotation axes of the dog member 51 and the hub 55 are relatively displaced, the collision surface 52bb of the standby dog 52b comes into contact with the chamfered surface 353h of the jumping dog 353c, and the collision surface of the standby dog 52b. Contact between 52bb and the torque transmission surface 53bb of the key portion 353b can be avoided.

  The preferred embodiments of the present invention have been described above with reference to the accompanying drawings. However, the present invention is not limited to the above-described embodiments, and various modifications within the scope described in the claims. Needless to say, the modified examples also belong to the technical scope of the present invention.

  In the above-described embodiment, when the diving dogs 53c and 353c collide with the standby dog 52b, the force F11 and the reaction force F12 input to the key portion 53b are straight in the plane direction orthogonal to the rotation axis direction. The bounced surface was inclined at an inclination angle θ12 so as to face the opposite direction on the line. However, the repelling surface 53g only needs to be inclined from one side to the other side in the circumferential direction from the outside in the radial direction to the inside on the plane orthogonal to the rotation axis direction.

  The present invention can be used for a power transmission device mainly used for a transmission of a vehicle.

50 Axis switching mechanism (power transmission device)
51 Dog members 52a, 52b Standby dog (second dog)
52bb, 52bc Colliding surface 53, 353 Drive side sleeve (sleeve)
53b, 353b Key portion 53ba, 53bb Torque transmission surface 53c, 353c Jumping dog (first dog)
53g, 353g Rebound surface 54 Coast side sleeve (sleeve)
54c Jumping dog (first dog)
55 Hub 55a Groove 55aa, 55ab Side surface 353h Chamfered surface

Claims (3)

A hub that rotates about a predetermined rotation axis, a hub that is recessed radially inward on the outer peripheral surface and has a plurality of grooves extending in the rotation axis direction; and
A key portion that is fitted in each of the plurality of grooves of the hub and slides in the direction of the rotation axis; and a first dog formed at a tip end of the key portion in the direction of the rotation axis. A integrally rotating sleeve;
A dog member provided coaxially with the hub and having a plurality of second dogs meshable with the first dog arranged in a rotational direction;
With
When the sleeve and the dog member move relative to each other in the proximity direction close to the rotation axis direction, the first dog and the second dog mesh with each other, and the hub, the sleeve, and the dog member rotate integrally. When the sleeve and the dog member move relative to each other in the direction of separation in the direction of the rotation axis, the engagement of the first dog and the second dog is released, and the hub, the sleeve, and the dog member rotate relative to each other. A power transmission device in a disconnected state,
The grooves are formed with side surfaces facing each other so that the groove width gradually increases toward the radially outer side,
The key portion has a circumferential width that gradually increases outward in the radial direction, and a torque transmission surface that is in surface contact with each of the side surfaces of the groove is formed. In the power transmission state, the key portion is connected to the hub via the torque transmission surface. Transmit torque between
The first dog has a surface in contact with the second dog in one of the circumferential directions in the power transmission state, and the second dog when the sleeve and the dog member are separated in the rotation axis direction. When the sleeve collides with the second dog, the sleeve is inclined so as to move in the separation direction, and in the plane direction perpendicular to the rotational axis direction, from the inner side to the outer side in the radial direction, A repelled surface tilted from the other circumferential direction to the other is formed on the other circumferential direction,
The second dog is formed with a collision surface that comes into surface contact with the struck surface when the first dog collides when the sleeve and the dog member are separated in the rotation axis direction. Power transmission device. The bounce surface is
In the surface direction orthogonal to the rotation axis direction, the direction of the force input from the second dog to the first dog, and the direction of the reaction force input from the side surface of the groove to the torque transmission surface of the key portion 2. The power transmission device according to claim 1, wherein the power transmission device is inclined in a direction orthogonal to the direction of the reaction force so that the two are aligned.   The first dog is chamfered inwardly in the radial direction of the bounced surface and inclined to the continuous portion with the torque transmission surface so that the sleeve moves in the separation direction due to a collision with the second dog. The power transmission device according to claim 1, wherein a surface is formed.

Images