JP2017211055A - Dog clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dog clutch device capable of increasing a binding force of dog teeth to each other by a simple configuration.SOLUTION: A dog clutch device of this invention comprises: a movable ring 50 having an inner peripheral surface opposing against an outer peripheral surface of a hub 40 and having dog teeth D1, D2; a supporting mechanism for supporting the movable ring 50 in such a way that it can be moved in an axial direction and integrally in respect to the hub 40. A gear change has dog teeth D3, D4 oppositely facing against the dog teeth D1, D2. The supporting mechanism has a guide groove 41 extending in an axial direction at an outer peripheral surface of the hub 40 and a guide pin 51 protruded from the inner peripheral surface of the movable ring 50, engaged with the guide groove 41 and movable from its neutral position to an in-gear position. Side surfaces 42, 43 of the guide groove 41 have slant portions 42b, 43b that are inclined in respect to a virtual line CL3 in parallel with the axis line and extended toward the end part in an axial direction.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a dog clutch device used in a vehicle transmission or the like.

  Conventionally, there has been known a device in which a gear supported to be rotatable relative to a rotating shaft and a slide ring that is spline-engaged to the rotating shaft so as to be relatively movable in the axial direction are coupled via a dog clutch. (For example, refer to Patent Document 1). In the device described in Patent Document 1, the tooth bases are respectively connected from the tooth tip side so that the meshing force acts on the meshing surfaces of the teeth on the gear side and the slide ring side constituting the dog clutch in the mutual coupling direction. An inclined surface is provided to incline toward the wall thickness side.

Japanese Patent Application Publication No. 2005-308142

  However, in the apparatus described in Patent Document 1, it is necessary to perform back taper processing on the teeth so as to reduce the thickness of the teeth toward the tooth base side, which complicates the processing and increases the processing cost.

  One aspect of the present invention is a dog clutch device that combines a first rotating body that rotates about an axis and a second rotating body that is provided so as to be rotatable relative to the first rotating body about the axis. An inner peripheral surface facing the outer peripheral surface of the one rotating body, a movable ring having a first dog tooth, a relative movement in the axial direction relative to the first rotating body, and a rotation integrally with the first rotating body, A support mechanism for supporting the movable ring, wherein the second rotating body has a second dog tooth facing the first dog tooth, and the supporting mechanism includes an outer peripheral surface of the first rotating body and an inner periphery of the movable ring. A guide groove extending in the axial direction on one of the surfaces, and projecting from either the outer peripheral surface of the first rotating body or the inner peripheral surface of the movable ring. In-gear position where the first dog teeth mesh with the second dog teeth from the neutral position where the dog teeth are separated from the second dog teeth And a guide pin that regulates the moving direction of the movable ring that is movable toward the outer surface of the guide groove, and the side surface of the guide groove that contacts the outer peripheral surface of the guide pin is inclined with respect to a virtual line parallel to the axis and extends toward the end in the axial direction. It has an inclined part.

  According to the present invention, the side surface of the guide groove that contacts the outer peripheral surface of the guide pin has the inclined portion that is inclined with respect to the virtual line parallel to the axis and extends toward the end in the axial direction. There is no need to provide an inclined portion on the surface, the processing of the inclined portion is facilitated, and the processing cost can be reduced.

The skeleton figure which shows the principal part structure of the transmission for vehicles with which the dog clutch apparatus which concerns on embodiment of this invention is applied. The disassembled perspective view which shows the structure of the 1st gear coupling mechanism contained in the transmission of FIG. FIG. 2 is a cross-sectional view of a main part of the transmission showing an assembled state of a first gear coupling mechanism included in the transmission of FIG. 1. Sectional drawing which expands and shows the principal part structure of the 1st gear coupling mechanism cut | disconnected along the IV-IV line | wire of FIG. The figure which shows the positional relationship of a guide groove and a guide pin in case a 1st gear coupling mechanism exists in a neutral state. The figure explaining the operation | movement at the time of the acceleration driving | running | working by the dog clutch apparatus which concerns on embodiment of this invention. The figure explaining the operation | movement at the time of the deceleration driving | running | working by the dog clutch apparatus which concerns on embodiment of this invention. The figure which shows the comparative example of FIG. 6A. The figure which shows the comparative example of FIG. 6B. The figure explaining the operation | movement at the time of upshift by the dog clutch apparatus which concerns on embodiment of this invention. The figure which shows the modification of FIG. 6A. The figure which shows the comparative example of FIG. 9A.

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a skeleton diagram showing a main configuration of a vehicle transmission to which a dog clutch device according to an embodiment of the present invention is applied.

  The transmission 1 includes a gear mechanism 10 that changes the rotation of the engine 2 at a speed ratio corresponding to the speed stage, and a clutch 3 that transmits or does not transmit the torque of the engine 2 to the gear mechanism 10. Torque output via the gear mechanism 10 is transmitted to drive wheels via an operating gear mechanism, a drive shaft, and the like (not shown), thereby causing the vehicle to travel.

  The gear mechanism 10 has a plurality of rotating shafts, that is, an input shaft 11 and an output shaft 12, which are arranged substantially parallel to each other and are rotatably supported. Although not shown, the gear mechanism 10 also has a reverse shaft. The transmission 1 is, for example, a 6-speed forward and 1-speed manual transmission, and the speed stage can be changed by a shift operation by a driver. The transmission 1 can also be configured as an automatic transmission that automatically changes the speed stage according to the vehicle speed, the amount of depression of the accelerator pedal, and the like.

  One end of the input shaft 11 is connected to the output shaft 2a of the engine 2 via the clutch 3, and the input shaft 11 and the output shaft 2a are coupled or disconnected according to the connection / disconnection of the clutch 3. That is, when the clutch 3 is connected, the input shaft 11 and the output shaft 2 a are coupled, and torque from the engine 2 can be input to the input shaft 11. On the other hand, when the clutch 3 is disconnected, the input shaft 11 and the output shaft 2a are disconnected, and torque input from the engine 2 becomes impossible.

  Around the input shaft 11, a fifth speed gear 25, a second speed gear 22, a sixth speed gear 26, and a third speed gear 23 are arranged in this order from the opposite side of the clutch 3. These transmission gears 22, 25, and 26 are supported so as to be rotatable relative to the input shaft 11 via bearings (not shown). A plurality of drive gears 27 to 29 are fixed to the input shaft 11 on the side of the third speed gear 23 (clutch 3 side). Of these, the gear 28 meshes with a gear fixed to a reverse shaft (not shown).

  In this specification, the gear is fixed to the rotating shaft (input shaft 11, output shaft 12, etc.) when the gear is processed on the outer peripheral surface of the rotating shaft, or the gear separate from the rotating shaft is splined. The case where it supports to a rotating shaft by coupling | bonding etc., ie, the case where a gear is provided in a rotating shaft so that relative rotation is impossible.

  Around the output shaft 12, a fourth speed gear 24 and a first speed gear 21 are supported so as to be rotatable relative to the output shaft 12 via a bearing (not shown). The fourth speed gear 24 meshes with the drive gear 27, and the first speed gear 21 meshes with the drive gear 29. A 5-speed driven gear 35, a 2-speed driven gear 32, a 6-speed driven gear 36, and a 3-speed driven gear 33 are fixed to the output shaft 12 in this order. Further, a final gear 30 is fixed to the output shaft 12 on the side of the first speed gear 21 (clutch 3 side). The 5-speed driven gear 35 is engaged with the 5-speed gear 25, the 2-speed driven gear 32 is engaged with the 2-speed gear 22, the 6-speed driven gear 36 is engaged with the 6-speed gear 26, and the 3-speed driven gear 33 is 3-speed. Engage with the gear 23. The torque of the transmission 1 is output to an operating gear mechanism (not shown) via the final gear 30.

  The transmission 1 has a plurality of gear coupling mechanisms (dog clutches) that couple the transmission gears 21 to 26 to a torque transmission rotary shaft (input shaft 11 or output shaft 12) via dog teeth. That is, a first gear coupling mechanism 1GE that couples the second gear 22 or the fifth gear 25 to the input shaft 11, a second gear coupling mechanism 2GE that couples the third gear 23 or the sixth gear 26 to the input shaft 11, A third gear coupling mechanism 3GE for coupling the first speed gear 21 or the fourth speed gear 24 to the output shaft 12;

  FIG. 2 is an exploded perspective view showing the configuration of the first gear coupling mechanism 1GE, and FIG. 3 is a cross-sectional view of the main part of the transmission 1 showing the assembled state of the first gear coupling mechanism 1GE. As shown in FIGS. 2 and 3, the first gear coupling mechanism 1GE is disposed between the second speed gear 22 and the fifth speed gear 25, is fixed to the input shaft 11, and rotates about the axis CL0. And a movable ring 50 supported so as to be movable in the axial direction (the direction of arrow AB in FIG. 3) along the outer peripheral surface of the hub 40.

  More specifically, a plurality of substantially cylindrical guide pins 51 in the circumferential direction project from the inner peripheral surface of the movable ring 50 toward the radially inner side. A plurality of substantially V-shaped guide grooves 41 in the circumferential direction are provided on the outer peripheral surface of the hub 40 from the one end surface in the axial direction to the other end surface corresponding to each guide pin 51. The guide pin 51 engages with the guide groove 41, and the guide pin 51 moves integrally with the movable ring 50 in the axial direction (direction of arrow AB in FIG. 3) while being guided by the guide groove 41. That is, the guide pin 51 functions as a movement restricting portion that restricts the moving direction of the movable ring 50 with respect to the hub 40. Dog teeth D1 project from one end surface in the axial direction of the movable ring 50 at equal intervals in the circumferential direction, and dog teeth D2 project from the other end surface in the axial direction at equal intervals in the circumferential direction.

  The second-speed gear 22 has a gear portion 22a formed on the outer peripheral surface and dog teeth D3 provided at the end in the axial direction facing the dog teeth D1. More specifically, the second speed gear 22 includes a gear body 221 having a gear portion 22a meshing with the second speed driven gear 32 (FIG. 1) formed on the outer peripheral surface, and an end portion of the gear body 221 on the movable ring 50 side. And a meshing ring 222 attached by spline coupling. The meshing ring 222 is provided with a plurality of openings 22b in the circumferential direction corresponding to the dog teeth D1 of the movable ring 50, and the axial end surface of the second gear 22 (meshing ring 222) is formed in an uneven shape in the circumferential direction. The Thereby, the dog tooth D3 is provided at the axial end portion of the second gear 22 so as to face the dog tooth D1.

  The fifth speed gear 25 has a gear portion 25a formed on the outer peripheral surface and dog teeth D4 provided at the end in the axial direction facing the dog teeth D2. More specifically, the fifth speed gear 25 is provided with a gear portion 25a meshing with the fifth speed driven gear 35 (FIG. 1) on the outer peripheral surface, and a plurality of circumferential directions corresponding to the dog teeth D2 of the movable ring 50 are provided. The opening 25b is provided, and the end surface in the axial direction of the fifth speed gear 25 is formed in an uneven shape in the circumferential direction. Thereby, the dog tooth D4 is provided at the axial end portion of the fifth speed gear 25 so as to face the dog tooth D2.

  In FIG. 3, the dog teeth D1 and D2 of the movable ring 50 are not meshed with any of the dog teeth D3 and D4 of the second gear 22 and the fifth gear 25, and the movable ring 50 is located at the neutral position. The one gear coupling mechanism 1GE is in a neutral state. From this state, when the movable ring 50 moves to the in-gear position in the direction of arrow A and the dog teeth D1 mesh with the dog teeth D3, the second gear 22 is coupled to the input shaft 11, and the first gear coupling mechanism 1GE is in the gear coupled state. It becomes. When the movable ring 50 moves to the in-gear position in the direction of arrow B and the dog teeth D2 mesh with the dog teeth D4, the fifth gear 25 is coupled to the input shaft 11, and the first gear coupling mechanism 1GE is in the gear coupled state. Become.

  The movable ring 50 is operated from the neutral position to the in-gear position or from the in-gear position to the neutral position by a dog operating device (not shown). The dog operating device has an actuator (such as an electric motor) that drives the movable ring 50 in the axial direction. A control signal is output from the controller to the actuator in accordance with a shift command, and the actuator is driven and controlled by the controller.

  In FIG. 1, when the second speed gear 22 is coupled to the input shaft 11 via the first gear coupling mechanism 1GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the second speed gear 22 and the second speed driven gear 32. Second gear is established. When the fifth speed gear 25 is coupled to the input shaft 11 via the first gear coupling mechanism 1GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the fifth speed gear 25 and the fifth speed driven gear 35. Established.

  Although detailed illustration is omitted, the second gear coupling mechanism 2GE and the third gear coupling mechanism 3GE are also configured similarly to the first gear coupling mechanism 1GE. Accordingly, when the third speed gear 23 is coupled to the input shaft 11 via the second gear coupling mechanism 2GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the third speed gear 23 and the third speed driven gear 33. The speed is established. When the 6th speed gear 26 is coupled to the input shaft 11 via the second gear coupling mechanism 2GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the 6th speed gear 26 and the 6th speed driven gear 36, and the 6th speed stage. Established.

  When the first speed gear 21 is coupled to the output shaft 12 via the third gear coupling mechanism 3GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the drive gear 29 and the first speed gear 21. Established. When the fourth speed gear 24 is coupled to the output shaft 12 via the third gear coupling mechanism 3GE, the rotation of the input shaft 11 is transmitted to the output shaft 12 via the drive gear 27, the fourth speed gear 24, and the fourth speed stage is established. To do.

  As described above, in the present embodiment, the hub 40 and the movable ring 50 of the gear coupling mechanisms 1GE to 3GE are connected to each other so as to be able to transmit torque via the guide pins 51 engaged with the guide grooves 41 ( Figures 2 and 3). Hereinafter, this point will be described in detail.

  FIG. 4 is an enlarged view (a cross-sectional view taken along line IV-IV in FIG. 3) showing the main configuration of the hub 40 and the movable ring 50 cut along a cross section perpendicular to the axis CL0. It is a figure which expands the principal part of hub 40 and movable ring 50 on a plane, and shows the positional relationship between guide groove 41 and guide pin 51 in the neutral state of gear coupling mechanisms 1GE-3GE. In FIG. 5, the rotation direction of the hub 40 during forward traveling and reverse traveling of the vehicle is indicated by arrows F and R, respectively, and the moving direction of the movable ring 50 along the axial direction is indicated by the arrow as in FIG. 3. Indicated by AB.

  As shown in FIG. 4, the outer peripheral surface 40a of the hub 40 faces the inner peripheral surface 50a of the movable ring 50, and the movable ring 50 can move relative to the hub 40 in the axial direction via the support mechanism SM and can be moved. And is supported rotatably. The support mechanism SM includes a guide pin 51 projecting from the inner peripheral surface 50a of the movable ring 50 toward the radially inner rotation center (axis line CL0), and a guide provided on the hub 40 and engaged with the guide pin 51. Groove 41.

  When the hub 40 rotates in the direction of arrow A in FIG. 4, torque acts on the movable ring 50 via the guide pins 51, and the movable ring 50 rotates together with the hub 40. At this time, a pressing force F1 acts on the guide pin 51 from the side surface of the guide groove 41 at a position (radius) R1 from the axis line CL0. FIG. 4 shows the direction of the pressing force F1 during acceleration traveling, and torque acts on the hub 40 from the movable ring 50 during deceleration traveling, and the direction of the pressing force is opposite.

  As shown in FIG. 5, the guide groove 41 of the outer peripheral surface 40a of the hub 40 has a pair of side surfaces facing each other from one axial side end surface 40b to the other axial side end surface 40c, that is, a first on the arrow F direction side. It has a side surface 42 and a second side surface 43 on the arrow R direction side. The guide groove 41 is formed symmetrically with respect to a center line CL1 passing through the center between the side end faces 40b and 40c of the hub 40.

  The guide groove 41 extending from the side end face 40b to the side end face 40c is divided into a first area AR1 and a first area AR1 including the center line CL1 by a pair of virtual lines CL2 parallel to the center line CL1 and separated from the center line CL1 by a predetermined length. Dividing into two regions AR2 on both sides of the region AR1 in the groove length direction. At this time, the first side surface 42 is configured by a side surface portion 42a at the axial center portion and a side surface portion 42b at the axial direction end portion, and the second side surface 43 is configured by the side surface portion 43a at the axial center portion and the axial end portion. Side surface portion 43b.

  In the first region AR1, the length (groove width L1) from the first side surface 42 to the second side surface 43 of the guide groove 41 is constant over the groove length direction. The side surface portion 42a in the first region AR1 is inclined by a predetermined angle θa with respect to the virtual line CL3 parallel to the axis line CL0 (FIG. 3), and the angle θ formed by the pair of side surface portions 42a on both sides of the center line CL1 is Less than 180 °. Therefore, the axial center portion 41a of the guide groove 41 in the first region AR1 is formed in a substantially V shape so as to protrude to the arrow F side. When the gear coupling mechanisms 1GE to 3GE are in the neutral state, the guide pin 51 is held at the neutral position in the central portion 41a of the guide groove 41 as shown in FIG.

  The side surface portion 43a and the side surface portion 43b of the second side surface 43 are connected without a step at the same inclination angle θa as the side surface portion 42a of the first side surface 42, respectively. On the other hand, the side surface portion 42b of the first side surface 42 is inclined to the side opposite to the adjacent side surface portion 42a, and a stepped portion 42c is provided at the boundary between the side surface portion 42a and the side surface portion 42b. More specifically, the side surface portion 42a is formed to be inclined in the direction of arrow R from the axial center (center line CL1) to the stepped portion 42c, whereas the side surface portion 42b is formed from the stepped portion 42c to the axial end surface. Inclined in the direction of arrow F over 40b and 40c. Accordingly, the distance between the first side surface 42 (side surface portion 42b) and the second side surface 43 (side surface portion 43b) in the second region AR2 increases toward the axial end surfaces 40b and 40c.

  The main operation of the dog clutch device according to the embodiment of the present invention will be described. 6A and 6B are diagrams showing directions of forces acting on the guide pin 51 during acceleration traveling and deceleration traveling in a state where the movable ring 50 is moved in the direction of arrow A, respectively. 6A and 6B, the guide pin 51 is located in the second area AR2 of the guide groove 41. 7A and 7B are diagrams showing comparative examples of FIGS. 6A and 6B.

During acceleration traveling, the rotation of the hub 40 is faster than the rotation of the movable ring 50. For this reason, as shown in FIG. 6A, the second side surface 43 (for example, the side surface portion 43 b) of the guide groove 41 of the hub 40 contacts the outer peripheral surface of the guide pin 51. As a result, a pressing force F1 in the acceleration direction (arrow F direction) acts on the guide pin 51, and the pressing force F1 causes the torque T1 (= F1 ×) to be applied to any of the transmission gears 21 to 26 via the dog teeth D1 and D3. Radius R1) acts. At this time, since the second side surface 43 of the guide groove 41 is inclined at an angle θa with respect to the axial direction, a force Fa in the direction of arrow A perpendicular to the pressing force F1 acts on the guide pin 51. That is, a force Fa (referred to as engagement promoting force) that promotes the engagement between the dog teeth D1 and the dog teeth D3 acts. The engagement promoting force Fa at this time is represented by the following formula (I).
Fa = T1 / R1 · tanθa (I)

On the other hand, during deceleration traveling, the rotation of the hub 40 is slower than the rotation of the movable ring 50, and torque T2 acts on the movable ring 50 from the dog teeth D3 as shown in FIG. 6B. Therefore, the first side surface 42 of the guide groove 41 of the hub 40, particularly the side surface portion 42b of the second region AR2, abuts the outer peripheral surface of the guide pin 51, and the pressing force F2 in the deceleration direction (arrow R direction) is applied to the guide pin 51. Works. At this time, since the side surface portion 42b of the guide groove 41 is inclined at an angle θb with respect to the axial direction, the force Fb in the direction of the arrow A perpendicular to the pressing force F2 is applied to the guide pin 51, that is, the dog tooth D1 and the dog A force Fb (meshing promoting force) that promotes the meshing with the tooth D3 is applied. The engagement promoting force Fb at this time is represented by the following formula (II).
Fb = T2 / R1 / tan θb (II)

  As described above, in the present embodiment, the side surface portions 42b and 43b that are inclined with respect to the virtual line CL3 are provided at the end portion of the guide groove 41 in the axial direction. For this reason, forces Fa and Fb that promote the meshing of the dog teeth D1 and D3 act on the guide pin 51 when the vehicle is accelerating and decelerating. Therefore, there is no need to machine inclined portions on the meshing surfaces of the dog teeth D1 and D3, and the axial coupling force between the dog teeth D1 and D3 can be increased with a simple configuration, thereby realizing a stable shifting operation. it can.

  On the other hand, as shown in FIGS. 7A and 7B, when the axial end portion of the guide groove 41 is formed along the axial direction without being inclined, the axial engagement promoting forces Fc and Fd are generated. Therefore, it is necessary to process the inclined portions on the meshing surfaces D1a, D3a and D1b, D3b of the dog teeth D1, D3. For this reason, it is necessary to perform back taper processing on the meshing surface, which complicates the processing and increases the processing cost.

In this case, the meshing acceleration force Fc during acceleration traveling and the meshing acceleration force Fd during deceleration traveling are expressed by the following formulas (III) and (IV) using the radius R2 of the meshing surfaces D1a, D3a and D1b, D3b, respectively. It is represented by
Fc = T1 / R2 · tanθc (III)
Fd = T2 / R2 / tanθd (IV)
Therefore, in order to add the meshing acceleration forces Fa and Fb equivalent to those obtained when back taper processing is performed on the guide pins 51 of FIGS. 6A and 6B (FIGS. 7A and 7B), the above formulas (I) and (III ) And the above equations (II) and (IV), the angle θa in FIG. 6A may be set to atan (R1 / R2 · tanθc), and the angle θb in FIG. 6B may be set to atan (R1 / R2 · tanθc).

  In the present embodiment, the movable ring 50 is operated so that the upper gear meshes before the lower gear becomes neutral during upshifting, that is, the lower gear and the upper gear mesh simultaneously. For example, when upshifting from the second gear to the third gear, the third gear 23 is input via the second gear coupling mechanism 2GE before the second gear 22 is neutralized via the first gear coupling mechanism 1GE. Coupled to the shaft 11. At this time, the movable ring 50 moves to the first area AR1 of the guide groove 41 as shown in FIG.

  The rotation of the hub 40 of the first gear coupling mechanism 1GE during the upshift is slower than the 53 rotations of the movable ring 50 (second gear 22). On the other hand, the rotation of the hub H40 of the second gear coupling mechanism 2GE is faster than the rotation of the movable ring 50 (third gear 23). For this reason, a part of the output torque acts as a circulating torque on the second speed gear 22 via the output shaft 12, and the side surface portion 42 a of the first side surface 42 contacts the outer peripheral surface of the guide pin 51.

  Due to this circulation torque, the axial force Fe toward the center line CL1 of the guide groove 41 on the guide pin 51 of the first gear coupling mechanism 1GE, that is, a force (meshing) that separates the dog tooth D1 from the dog tooth D3. Called the release force). As a result, the meshing between the dog tooth D1 of the movable ring 50 and the dog tooth D3 of the second gear 22 is released, and the first gear coupling mechanism 1GE is in a neutral state. In this way, by configuring the upshift while simultaneously engaging a part of the transmission gears (for example, the second speed gear 22 and the third speed gear 23), it is possible to perform a smooth upshift without torque loss.

According to the embodiment of the present invention, the following effects can be obtained.
(1) The dog clutch device is configured to couple a hub 40 that rotates about an axis line CL0 and transmission gears 21 to 26 that are provided to be rotatable relative to the hub 40 about an axis line CL0. The movable ring 50 has an inner peripheral surface 50a opposite to the surface 40a, has a dog tooth D1, D2, and is movable relative to the hub 40 in the axial direction and rotatable integrally with the hub 40. The transmission gears 21 to 26 have dog teeth D3 and D4 facing the dog teeth D1 and D2 (FIGS. 1 to 4). The support mechanism SM protrudes from the guide groove 41 extending in the axial direction on the outer peripheral surface 40a of the hub 40 and the inner peripheral surface 50a of the movable ring 50, engages with the guide groove 41, and has dog teeth D1, D1. A guide pin 51 that regulates the moving direction of the movable ring 50 that is movable from a neutral position where D2 is separated from the dog teeth D3, D4 to an in-gear position where the dog teeth D1, D2 mesh with the dog teeth D3, D4. The side surfaces 42 and 43 of the guide groove 41 that are in contact with the outer peripheral surface of the guide pin 51 have side surface portions 42b and 43b that are inclined with respect to a virtual line CL3 parallel to the axis line CL0 and extend toward the axial end (see FIG. 5).

  In this way, by providing the side surfaces 42b and 43b inclined toward the axial ends on the side surfaces 42 and 43 of the guide groove 41, when the guide pin 51 moves to the second area AR2 of the guide groove 41, it is movable with the hub 40. Axial forces Fa and Fb that engage the dog teeth D1 and D2 and the dog teeth D3 and D4 act on the guide pin 51 by the torques T1 and T2 acting between the rings 50. For this reason, it is not necessary to incline the meshing surfaces of the dog teeth D1 to D4, the back taper processing becomes unnecessary, and the processing cost can be reduced. That is, according to the dog clutch device of the present embodiment, the meshing surfaces of the dog teeth D1 to D4 are inclined with a simple configuration in which the inclined side surface portions 42b and 43b are provided at the axial end portion of the guide groove 41. The same meshing facilitating forces Fa and Fb (FIGS. 6A and 6B) can be added to the movable ring 50 (guide pin 51), and the coupling force between the dog teeth D1 and D2 and the dog teeth D3 and D4 is easy. Can be increased.

(2) The guide groove 41 has a first side surface 42 on the rotational direction side and a second side surface 43 opposite to the rotational direction that face each other. The second side surface 43 has a side surface portion 43b inclined toward the opposite side of the rotation direction toward the axial end portion with respect to the virtual line CL3 (FIG. 6A, 6B). As a result, the meshing force Fa, Fb can be applied to the movable ring 50 during both acceleration and deceleration, and the transmission gears 21 to 26 (dog teeth D3, D4) and the movable ring 50 (dog) The teeth D1, D2) can be stably connected.

(3) The first side surface 42 includes a side surface portion 42a that is continuous with the side surface portion 42b and is inclined to the opposite side of the side surface portion 42b with respect to the virtual line CL3 (FIG. 8). As a result, when the lower transmission gear and the upper transmission gear are simultaneously meshed during upshifting, the output shaft is connected to the guide pin 51 of the movable ring 50 of the gear coupling mechanism corresponding to the lower transmission gears 21 to 26. The meshing release force Fe in the axial direction acts by the circulating torque via 12, and the movable ring 50 can be moved to the neutral position at an optimal timing without torque loss.

  In the above embodiment, the guide groove 41 is divided into three regions AR1 and AR2 in the length direction, and the central portion 41a of the guide groove 41 in the first region AR1 is substantially V-shaped so as to protrude in the rotation direction. However, the shape of the guide groove 41 is not limited to this. For example, as shown in FIG. 9A, the side surface portions 42a and 43a at the center in the axial direction of the guide groove 41 extend in parallel to the virtual line CL3 in the axial direction, and the side surface portions 42b and 43b at the end portions in the axial direction. You may make it incline at a predetermined angle with respect to virtual line CL3. Thus, as described above, the engagement fading force Fa in the axial direction can be applied to the guide pin 51 with a simple configuration. On the other hand, as shown in FIG. 9B, the movable ring 50 is provided with dog teeth 51A (spline teeth) that engage with the guide grooves 41, and the meshing surfaces of the dog teeth D1 and D3 are inclined. The dog teeth D1 and D3 require back taper processing, which increases the processing cost.

  In the above embodiment, the side surface portion 42b inclined at the predetermined angle θb with respect to the virtual line CL3 at the axial direction end portion of the first side surface 42 in the second region AR2 of the guide groove 41, that is, the axial direction end portion with respect to the virtual line CL3. And a side surface portion 43b inclined at a predetermined angle θa with respect to the imaginary line CL3 at the axial end portion of the second side surface 43 in the second region AR2 of the guide groove 41. In other words, the second inclined portion inclined toward the opposite side of the rotation direction from the imaginary line CL3 toward the axial end portion is provided. In this case, the angles θa and θb may be equal to or different from each other. As the inclined portions of the side surfaces 42 and 43 of the guide groove 41, only one of the first inclined portion (side surface portion 42b) and the second inclined portion (side surface portion 43b) (for example, the second inclined portion) may be provided. Good. In the above embodiment, the first side surface 42 is provided with the side surface portion 42a (third inclined portion) that is inclined to the opposite side of the side surface portion 42b with respect to the virtual line CL3 and guides the guide pin 51 to the neutral position. The third inclined portion may be omitted as shown in FIG.

  In the above embodiment, the guide groove 41 is provided on the outer peripheral surface 40a of the hub 40 as the first rotating body, and the guide pin 51 is projected from the inner peripheral surface 50a of the movable ring 50. However, the configuration of the support mechanism that supports the movable ring so as to be relatively movable in the axial direction and to be rotatable integrally with the first rotating body is not limited thereto. For example, a guide groove may be provided on the inner peripheral surface 50 a of the movable ring 50 and a guide pin may be provided so as to protrude from the outer peripheral surface 40 a of the hub 40. That is, a guide groove extending in the axial direction on one of the outer peripheral surface of the first rotating body and the inner peripheral surface of the movable ring, and the other of the outer peripheral surface of the first rotating body and the inner peripheral surface of the movable ring The dog teeth D1, D2 are engaged from the neutral position where the dog teeth D1, D2 (first dog teeth) are separated from the dog teeth D3, D4 (second dog teeth). The support mechanism may have any configuration as long as it has a guide pin that regulates the moving direction of the movable ring that can move to the in-gear position meshing with D3 and D4.

  In the embodiment described above, a dog clutch device that couples the hub 40 as the first rotating body that rotates about the axis CL0 and the transmission gears 21 to 26 as the second rotating bodies that are rotatably provided to the hub 40 will be described. However, the dog clutch device of the present invention can be applied to devices other than the transmission 1. Therefore, the configurations of the first rotating body and the second rotating body are not limited to those described above.

  The above description is merely an example, and the present invention is not limited to the above-described embodiments and modifications unless the features of the present invention are impaired. It is also possible to arbitrarily combine one or more of the above-described embodiments and modified examples. Variations can be combined.

DESCRIPTION OF SYMBOLS 1 Transmission, 21-26 Transmission gear, 40 Hub, 41 Guide groove, 42 1st side surface, 42a, 42b Side surface part, 43 2nd side surface, 43b Side surface part, 50 Movable ring, 51 Guide pin, SM support mechanism, D1 ~ D4 dog teeth

Claims (3)

A dog clutch device that couples a first rotating body that rotates about an axis and a second rotating body that is provided to be rotatable relative to the first rotating body about the axis,
A movable ring having an inner peripheral surface facing the outer peripheral surface of the first rotating body and having a first dog tooth;
A support mechanism that supports the movable ring so as to be relatively movable in the axial direction with respect to the first rotating body and to be able to rotate integrally with the first rotating body;
The second rotating body has second dog teeth facing the first dog teeth,
The support mechanism is
A guide groove extending in the axial direction on either the outer peripheral surface of the first rotating body or the inner peripheral surface of the movable ring;
A neutral position that protrudes from either the outer peripheral surface of the first rotating body or the inner peripheral surface of the movable ring, engages with the guide groove, and separates the first dog teeth from the second dog teeth. A guide pin that regulates a moving direction of the movable ring that is movable from an in-gear position where the first dog teeth mesh with the second dog teeth,
The dog clutch device according to claim 1, wherein a side surface of the guide groove that contacts the outer peripheral surface of the guide pin has an inclined portion that is inclined with respect to an imaginary line parallel to the axis and extends toward an axial end portion. The dog clutch device according to claim 1,
The guide groove has a first side surface on the rotation direction side and a second side surface opposite to the rotation direction, which are opposed to each other.
The inclined portion has a first inclined portion that is inclined to the rotational direction side with respect to the imaginary line on the first side surface, and an axial end portion with respect to the imaginary line on the second side surface. A dog clutch device having a second inclined portion inclined to the opposite side of the rotation direction. The dog clutch device according to claim 2,
The dog clutch device according to claim 1, wherein the first side surface includes a third inclined portion that is continuous with the first inclined portion and is inclined to the opposite side of the first inclined portion with respect to the virtual line.

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