JP2017211054A - transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission capable of upshifting for every stage and downshifting so as to skip a plurality of stages, with seamless transmission.SOLUTION: A transmission includes a gear connection mechanism that restores a movable ring having dog teeth in a lower stage from an inner gear position to a neutral position when the dog teeth in the lower stage are engaged with each other and dog teeth in an upper stage are engaged with each other simultaneously by an operation of a dog operation device 5. The dog operation device 5 includes: a shaft member 50 having an engagement piece 52 projecting from an outer peripheral surface; a driving unit 60 configured to move the shaft member 50 along an axial line CLa, and rotate the shaft member 50 around the axial line CLa; a plurality of plate members 70 arranged side by side along the axial line CLa, and moving in a direction vertical to the axial line CLa according to an engagement operation with the engagement piece 52; and an operation transmission unit 80 configured to transmit the movement of the plate members 70 to the movable ring.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a transmission mounted on a vehicle.

  2. Description of the Related Art Conventionally, in a vehicle transmission using a single clutch, a transmission that enables an upshift from a lower stage to an upper stage without interrupting driving force is known (see, for example, Patent Document 1). In the transmission described in Patent Document 1, when the lower and upper meshing clutches are simultaneously meshed between the clutch ring and the driving force transmission shaft of each gear of the transmission by the operation of the gear shifting operation unit, the meshing is performed. Guide portions for generating axial forces in the release direction and the meshing direction are provided. The speed change operation unit rotationally drives the shift drum formed with the shift groove, thereby moving the shift arm engaged with the shift groove in the axial direction, thereby moving the clutch ring of the meshing clutch in the axial direction.

International Publication No. 2012/066740

  However, in the apparatus described in Patent Document 1, since the clutch ring is moved in the axial direction by moving the shift arm along the shift groove by the rotation of the shift drum, not only the upshift from the lower stage to the upper stage but also the upper stage Downshift from 1 to the lower stage is also performed one stage at a time. For this reason, for example, it is not possible to perform a shift operation that suddenly depresses the accelerator pedal and lowers the shift stage a plurality of steps at a time, and the drivability of the vehicle is reduced.

  A transmission according to one aspect of the present invention is supported by a plurality of hubs that rotate about a first axis and each of the plurality of hubs so as to be movable in an axial direction and integrally rotatable. A plurality of movable rings having first dog teeth, a plurality of speed change gears rotating about the first axis and having second dog teeth corresponding to the gear position opposite to the first dog teeth; A support mechanism that supports one of the hub and the plurality of transmission gears so as to be rotatable integrally with the rotation shaft, and supports the other of the gears so as to be rotatable relative to the rotation shaft, and the first dog teeth are the second dog teeth. A dog operating device that operates a plurality of movable rings so as to be movable between a neutral position that is separated from the teeth and an in-gear position where the first dog teeth mesh with the second dog teeth; The dog teeth and the second dog teeth and the upper first dog teeth and A co-biting prevention mechanism for returning the movable ring having the lower first dog tooth from the in-gear position to the neutral position among the plurality of movable rings when the two dog teeth are engaged at the same time. A shaft member having an engagement piece extending along two axes and projecting from the outer peripheral surface, and the shaft member is moved along the second axis, and the shaft member is rotated about the second axis. A drive unit and a plurality of plate members arranged side by side along the second axis, the engagement unit having an engaged portion with which the engagement piece can be engaged, and the engagement piece and the engaged portion by the drive unit, The plurality of plate members that move in a direction substantially perpendicular to the second axis in accordance with the engagement operation of the plurality of plate members, and the respective movements of the plurality of plate members are transmitted to the plurality of movable rings corresponding to the plate members. From the neutral position to the in-gear position or from the in-gear position to the neutral position. A motion transmission unit for moving Te comprises a.

  According to the present invention, the engagement pieces projecting from the outer peripheral surface of the shaft member movable in the axial direction are engaged with the engaged portions of the plurality of plate members, and the movement of the plate members is transmitted to the movable ring. As a result, it is possible not only to upshift the gears one step at a time by seamless gear shifting, but also to allow jump gear shifting, which improves the drivability of the vehicle.

The skeleton figure which shows the principal part structure of the transmission which concerns on embodiment of this invention. The disassembled perspective view which shows the structure of the 1st gear coupling mechanism which comprises the transmission of FIG. Sectional drawing which shows the assembly state of the 1st gear coupling mechanism which comprises the transmission of FIG. FIG. 4 is a diagram illustrating a direction of a force acting on a guide pin from a guide groove during acceleration of the vehicle in the first gear coupling mechanism of FIGS. FIG. 4 is a diagram illustrating a direction of a force acting on a guide pin from a guide groove when the vehicle is decelerated in the first gear coupling mechanism of FIGS. The perspective view which shows the principal part structure inside the transmission which concerns on embodiment of this invention. The side view which shows the principal part structure inside the transmission which concerns on embodiment of this invention. The perspective view of the finger which comprises the dog operation apparatus of FIG. The side view of the finger which comprises the dog operation apparatus of FIG. Sectional drawing of the finger cut | disconnected along the AA line of FIG. Sectional drawing of the finger cut | disconnected along the BB line of FIG. Sectional drawing of the finger cut | disconnected along CC line of FIG. Sectional drawing of the finger cut | disconnected along the DD line | wire of FIG. Sectional drawing of the finger cut | disconnected along the EE line | wire of FIG. The figure which models and shows the structure of the finger of FIG. The top view of the shift rail which comprises the dog operation apparatus of FIG. The figure which shows the structure of the shift rail of FIG. 11 matched with the movable ring of FIG. The figure which shows the positional relationship of the finger with respect to a shift rail when shifting to the target gear stage from the present gear stage. The figure which shows an example of the engagement operation | movement of a finger and a shift rail at the time of upshift from 4th speed to 5th speed. The figure which shows an example of the engagement operation | movement of a finger and a shift rail at the time of upshift from 2nd speed to 5th speed. The figure which shows an example of the engagement operation | movement of a finger and a shift rail at the time of downshift from 5th speed to 2nd speed.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. FIG. 1 is a skeleton diagram showing a main configuration of a transmission according to an embodiment of the present invention. The transmission 1 is mounted on, for example, a hybrid vehicle. The hybrid vehicle includes an engine 2 and an electric motor 3.

  The transmission 1 includes a gear mechanism 10 that changes the rotation of at least one of the engine 2 and the electric motor 3 at a speed ratio corresponding to the speed stage, and a clutch mechanism C that transmits or does not transmit the torque of the engine 2 to the gear mechanism 10. Have. 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 is arranged substantially parallel to each other, and each of the plurality of rotation shafts is rotatably supported, that is, the first main input shaft 11, the second main input shaft 12, the sub input shaft 13, the output shaft 14, and the reverse. And a shaft 15. The second main input shaft 12 is formed so as to be coaxial with the first main input shaft 11 and so as to surround the first main input shaft 11. The transmission 1 is, for example, an automatic transmission with 8 forward speeds and 1 reverse speed. The clutch mechanism C includes a first clutch C1 and a second clutch C2 that are configured by a dry clutch. A wet clutch (for example, a wet multi-plate clutch) can be used instead of the dry clutch.

  The electric motor 3 is composed of, for example, a three-phase DC brushless motor, and includes a rotor 3a rotatably supported in a housing of the electric motor 3 (not shown), and a stator 3b disposed around the rotor 3a and fixed to the housing. Have. One end of the first main input shaft 11 is connected to the rotor 3a of the electric motor 3, and the first main input shaft 11 can rotate integrally with the rotor 3a. The stator 3b has a coil wound around the stator core, and the coil is electrically connected to the battery via the power drive unit. The operation of the power drive unit is controlled by a controller (FIG. 8) as an electronic control unit (ECU). Thereby, the torque generated in the electric motor 3 can be controlled, and the torque of the electric motor 3 can be input to the first main input shaft 11. When the vehicle is braked, regenerative energy can be input to the electric motor 3.

  The other end of the first main input shaft 11 is connected to the output shaft 2a of the engine 2 via the first clutch C1, and the first main input shaft 11 and the output shaft 2a are connected according to the connection / disconnection of the first clutch C1. Are bound or blocked. That is, when the first clutch C1 is connected, the first main input shaft 11 and the output shaft 2a are coupled, and the torque from the engine 2 can be input to the first main input shaft 11. On the other hand, when the first clutch C1 is disconnected, the first main input shaft 11 and the output shaft 2a are disconnected, and torque input from the engine 2 becomes impossible.

  Further, the other end portion of the first main input shaft 11 is connected to one end portion of the second main input shaft 12 via the second clutch C2, and the first main input shaft 11 is connected according to the connection / disconnection of the second clutch C2. And the second main input shaft 12 are coupled or disconnected. That is, when the second clutch C2 is connected, the first main input shaft 11 and the second main input shaft 12 are coupled, and when the second clutch C2 is disconnected, the first main input shaft 11 and the second main input shaft 12 are connected. Is cut off. For example, when both the first clutch C 1 and the second clutch C 2 are connected, torque from the engine 2 can be input to the second main input shaft 12. When only the second clutch C <b> 2 is connected, the torque of the electric motor 3 can be input to the second main input shaft 12.

  The clutch mechanism C of the transmission 1 according to the present embodiment includes a pair of clutches C1 and C2 for switching the connection between the input shafts 11 and 12 and the engine 2 and the electric motor 3. Therefore, the clutch mechanism C has a function similar to that of a single clutch that connects and disconnects the engine 2 and the gear mechanism 10 or the electric motor 3 and the gear mechanism 10, and has a clutch for odd-numbered gears and a clutch for even-numbered gears. The configuration is different from the clutch (twin clutch).

  Around the second main input shaft 12, a 2-speed drive gear 22, an 8-speed drive gear 28, a 4-speed drive gear 24, and a 7-speed drive gear 27 are arranged in this order from the electric motor 3 side. The These drive gears 22, 24, 27, and 28 are supported so as to be rotatable relative to the first main input shaft 11 via bearings. A gear 31 is fixed to the second main input shaft 12 on the side (clutch mechanism C side) of the seventh speed drive gear 27. The gear 31 meshes with a gear 32 fixed to the reverse shaft 15. A reverse drive gear 29 and a parking gear 30 are supported around the reverse shaft 15 so as to be rotatable relative to the reverse shaft 15.

  In this specification, the gear is fixed to the rotating shaft (the second main input shaft 12, the output shaft 14, the reverse shaft 15 and the like) when processing the gear on the outer peripheral surface of the rotating shaft, The case where a separate gear is supported on the rotating shaft by spline coupling or the like, that is, the case where the gear is provided on the rotating shaft so as not to be relatively rotatable.

  Although not shown, the gear 32 meshes with a gear 33 fixed to the sub input shaft 13. Thereby, the rotation of the second main input shaft 12 is transmitted to the sub input shaft 13 via the gears 31 to 33, and the sub input shaft 13 rotates together with the second main input shaft 12 and the reverse shaft 15. Around the auxiliary input shaft 13, a first speed drive gear 21, a sixth speed drive gear 26, a third speed drive gear 23, and a fifth speed drive gear 25 are arranged in this order from the electric motor 3 side. These drive gears 21, 23, 25, and 26 are supported so as to be relatively rotatable with respect to the auxiliary input shaft 13 through bearings.

  The output shaft 14 includes a 1-2 speed driven gear 41, a 6-8 speed driven gear 42, a 3-4 speed driven gear 43, a 5-7 speed driven gear 44, and a final gear 45. It is fixed in this order from the side. The first-second driven gear 41 meshes with the first-speed drive gear 21 and the second-speed drive gear 22, respectively. Although illustration is omitted, the 1-2 speed driven gear 41 also meshes with the reverse drive gear 29. The 6-8 speed driven gear 42 meshes with the 6 speed drive gear 26 and the 8 speed drive gear 28, respectively. The 3-4 speed driven gear 43 meshes with the 3rd speed drive gear 23 and the 4th speed drive gear 24, respectively. The 5-7 speed driven gear 44 meshes with the 5th speed drive gear 25 and the 7th speed drive gear 27, respectively.

  The parking gear 30 is configured to engage with an engaging claw of a parking gear mechanism (not shown). When the engagement claw is engaged with the parking gear 30 according to the operation of the parking gear mechanism, the gear mechanism 10 is locked, and when the engagement of the engagement claw is released, the gear mechanism 10 is unlocked. The torque of the transmission 1 is output to an operating gear mechanism (not shown) via the final gear 45.

  The transmission 1 includes a plurality of gear coupling mechanisms that couple the drive gears 21 to 29 to a torque transmission rotary shaft. That is, the first gear coupling mechanism 1GE that couples the second speed drive gear 22 or the eighth speed drive gear 28 to the second main input shaft 12, and the fourth speed drive gear 24 or the seventh speed drive gear 27 to the second main input shaft 12. The second gear coupling mechanism 2GE to be coupled, the third gear coupling mechanism 3GE for coupling the first speed driving gear 21 or the sixth speed driving gear 26 to the sub input shaft 13, and the third speed driving gear 23 or the fifth speed driving gear 25 to the sub A fourth gear coupling mechanism 4GE coupled to the input shaft 13 and a fifth gear coupling mechanism 5GE coupling the reverse drive gear 29 to the reverse shaft 15 are provided.

  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 drive gear 22 and the eighth speed drive gear 28, and is fixed to the second main input shaft 12, and the hub HB1. The movable ring DR1 is 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 HB1. More specifically, the hub HB1 is fixed to the outer peripheral surface of the second main input shaft 12 through the spline 12a so as to be integrally rotatable, and the second speed drive gear 22 and the eighth speed drive gear 28 are connected to the bearing 12b, It is provided on the outer peripheral surface of the second main input shaft 12 via 12c so as to be relatively rotatable. The spline 12a and the bearings 12b and 12c constitute a support mechanism 120 that supports the hub HB1 so as to be rotatable with respect to the second main input shaft 11 and supports the drive gears 22 and 28 so as to be relatively rotatable.

  On the inner peripheral surface of the movable ring DR1 centered on the axis CL0, a plurality of substantially cylindrical guide pins DRa projecting radially inward, projecting from the outer peripheral surface of the hub HB1 centering on the axis CL0. Is provided with a substantially V-shaped guide groove HBa corresponding to the guide pin DRa from one axial end surface to the other end surface. The guide pin DRa is fitted in the guide groove HBa, and the movable ring DR1 moves in the axial direction while the guide pin DRa is guided by the guide groove HBa. Dog teeth D2a project from the one end surface in the axial direction of the movable ring DR1 (on the second speed drive gear 22 side) at equal intervals in the circumferential direction, and the other end surface in the axial direction (on the eighth speed drive gear 28 side). Dog teeth D8a are projected at intervals.

  The second-speed drive gear 22 has a transmission gear portion 22a formed on the outer peripheral surface and dog teeth D2b provided at the end in the axial direction facing the dog teeth D2a. More specifically, the second speed drive gear 22 includes a gear main body 221 having a transmission gear portion 22a formed on the outer peripheral surface, and a meshing ring 222 attached to the end of the gear main body 221 on the movable ring DR1 side by spline coupling. And integrally. The meshing ring 222 is provided with a plurality of openings 22b in the circumferential direction corresponding to the dog teeth D2a of the movable ring DR1. For this reason, the axial end surface of the second speed driving gear 22 (meshing ring 222) is formed in a concavo-convex shape in the circumferential direction, whereby the dog tooth facing the dog teeth D2a is formed at the axial end of the second speed driving gear 22. D2b is provided.

  The 8-speed drive gear 28 has a transmission gear portion 28a formed on the outer peripheral surface, and dog teeth D8b provided at the end in the axial direction facing the dog teeth D8a. More specifically, the 8-speed drive gear 28 is provided with a plurality of circumferential openings 28b corresponding to the dog teeth D8a of the movable ring DR1, and the axial end surface of the 8-speed drive gear 28 is uneven in the circumferential direction. It is formed in a shape. As a result, dog teeth D8b are provided at the axial ends of the 8-speed drive gear 28 so as to face the dog teeth D8a.

  In FIG. 3, the dog teeth D2a and D8a of the movable ring DR1 are not meshed with any of the dog teeth D2b and D8b of the second speed drive gear 22 and the eighth speed drive gear 28, and the movable ring DR1 is located in the neutral position. The first gear coupling mechanism 1GE is in a neutral state. From this state, when the movable ring DR1 moves to the in-gear position in the direction of arrow A and the dog teeth D2a mesh with the dog teeth D2b, the second-speed drive gear 22 is coupled to the second main input shaft 12, and the first gear coupling mechanism 1GE. Is in a gear-coupled state. Further, when the movable ring DR1 moves to the in-gear position in the arrow B direction and the dog teeth D8a mesh with the dog teeth D8b, the 8-speed drive gear 28 is coupled to the second main input shaft 12, and the first gear coupling mechanism 1GE is The gear is connected.

  In FIG. 1, when the second speed drive gear 22 is coupled to the second main input shaft 12 via the first gear coupling mechanism 1GE, the rotation of the second main input shaft 12 is changed to the second speed drive gear 22, 1-2 speed driven gear. Is transmitted to the output shaft 14 via 41, and the second gear is established. When the 8-speed drive gear 28 is coupled to the second main input shaft 12 via the first gear coupling mechanism 1GE, the rotation of the second main input shaft 12 is transmitted via the 8-speed drive gear 28 and the 6-8-speed driven gear 42. Transmission to the output shaft 14 establishes the eighth gear.

  Although not shown in detail, the other gear coupling mechanisms 2GE to 5GE are configured in the same manner as the first gear coupling mechanism 1GE.

  In other words, the second gear coupling mechanism 2GE is disposed between the fourth speed drive gear 24 and the seventh speed drive gear 27, and the hub HB2 fixed to the second main input shaft 12 and the outer peripheral surface of the hub HB2. And a movable ring DR2 supported so as to be movable in the axial direction. The movable ring DR2 has dog teeth D4a on one axial end surface and dog teeth D7a on the other axial end surface. The 4-speed drive gear 24 has a gear shift gear portion at one end in the axial direction and dog teeth D4b opposite to the dog teeth D4a at the other end in the axial direction. The seventh-speed drive gear 27 has a transmission gear portion at one end in the axial direction and dog teeth D7b opposite the dog teeth D7a at the other end in the axial direction.

  When the movable ring DR2 moves to one in-gear position in the axial direction and the dog tooth D4a meshes with the dog tooth D4b, the fourth speed drive gear 24 is coupled to the second main input shaft 12. As a result, the rotation of the second main input shaft 12 is transmitted to the output shaft 14 via the fourth speed drive gear 24 and the third and fourth speed driven gear 43, and the fourth speed stage is established. When the movable ring DR2 moves to the other in-gear position in the axial direction and the dog teeth D7a mesh with the dog teeth D7b, the seventh speed drive gear 27 is coupled to the second main input shaft 12. As a result, the rotation of the second main input shaft 12 is transmitted to the output shaft 14 via the seventh speed drive gear 27 and the fifth to seventh speed driven gear 44, and the seventh speed stage is established.

  The third gear coupling mechanism 3GE is disposed between the first speed drive gear 21 and the sixth speed drive gear 26, and moves in the axial direction along the outer peripheral surface of the hub HB3 fixed to the sub input shaft 13 and the hub HB3. The movable ring DR3 is supported in a possible manner. The movable ring DR3 has dog teeth D1a on one end surface in the axial direction and dog teeth D6a on the other end surface in the axial direction. The first-speed drive gear 21 has a transmission gear portion at one end in the axial direction, and has dog teeth D1b opposite the dog teeth D1a at the other end in the axial direction. The sixth speed drive gear 26 has a gear shift gear portion at one end in the axial direction and dog teeth D6b opposite the dog teeth D6a at the other end in the axial direction.

  When the movable ring DR3 moves to one in-gear position in the axial direction and the dog tooth D1a meshes with the dog tooth D1b, the first speed drive gear 21 is coupled to the auxiliary input shaft 13. As a result, the rotation of the auxiliary input shaft 13 is transmitted to the output shaft 14 via the first-speed drive gear 21 and the first-second driven gear 41, and the first-speed stage is established. When the movable ring DR3 moves to the other in-gear position in the axial direction and the dog tooth D6a meshes with the dog tooth D6b, the sixth speed drive gear 26 is coupled to the auxiliary input shaft 13. As a result, the rotation of the auxiliary input shaft 13 is transmitted to the output shaft 14 via the 6-speed drive gear 26 and the 6-8 speed driven gear 42, and the 6th speed stage is established.

  4th gear coupling mechanism 4GE is arrange | positioned between the 3rd speed drive gear 23 and the 5th speed drive gear 25, and moves to an axial direction along the outer peripheral surface of hub HB4 fixed to the sub input shaft 13, and hub HB4. It has a movable ring DR4 supported in a possible manner. The movable ring DR4 has dog teeth D3a on one axial end surface and dog teeth D5a on the other axial end surface. The third-speed drive gear 23 has a gear shift gear at one axial end and a dog tooth D3b opposite the dog tooth D3a at the other axial end. The fifth-speed drive gear 25 has a transmission gear portion at one end in the axial direction and dog teeth D5b opposite the dog teeth D5a at the other end in the axial direction.

  When the movable ring DR4 moves to one in-gear position in the axial direction and the dog teeth D3a mesh with the dog teeth D3b, the third-speed drive gear 23 is coupled to the sub input shaft 13. As a result, the rotation of the auxiliary input shaft 13 is transmitted to the output shaft 14 via the third speed drive gear 23 and the third and fourth speed driven gear 43, and the third speed stage is established. When the movable ring DR4 moves to the other in-gear position in the axial direction and the dog tooth D5a meshes with the dog tooth D5b, the fifth speed drive gear 25 is coupled to the auxiliary input shaft 13. As a result, the rotation of the auxiliary input shaft 13 is transmitted to the output shaft 14 via the fifth speed drive gear 25 and the 5-7 speed driven gear 44, and the fifth speed stage is established.

  The fifth gear coupling mechanism 5GE includes a hub HB5 fixed to the reverse shaft 15 and a movable ring DR5 supported so as to be movable in the axial direction along the outer peripheral surface of the hub HB5. The movable ring DR5 has dog teeth D9a on one end surface in the axial direction. The reverse drive gear 29 has a transmission gear portion at one end in the axial direction and dog teeth D9b at the other end in the axial direction.

  When the movable ring DR5 moves to one in-gear position in the axial direction and the dog tooth D9a meshes with the dog tooth D9b, the reverse drive gear 29 is coupled to the reverse shaft 15. Thereby, the rotation of the reverse shaft 15 is transmitted to the output shaft 14 via the reverse drive gear 29 and the first-second driven gear 41, and the reverse gear is established. Although illustration is omitted, when the movable ring DR5 moves to the other parking operation position in the axial direction, the parking gear mechanism is operated, the engaging claw of the parking gear mechanism is engaged with the parking gear 30, and the gear mechanism 10 is Locked.

  As described above, V-shaped guide grooves HBa are provided on the outer peripheral surfaces of the hubs HB1 to HB5 of the gear coupling mechanisms 1GE to 5GE, and the guide pins DRa of the movable rings DR1 to DR5 are respectively provided in the guide grooves HBa. Engage. 4A and 4B are diagrams showing the directions of forces acting on the guide pin DRa from the guide groove HBa during acceleration and deceleration, respectively. Here, as an example, the direction of the force acting on the guide pin DRa from the guide groove HBa of the first gear coupling mechanism 1GE in the gear coupled state, that is, the dog tooth D2b of the second-speed drive gear 22 becomes the dog tooth D2a of the movable ring DR1. The direction of the force acting on the guide pin DRa in the engaged state is shown. Although illustration is omitted, even when the other gear coupling mechanisms GE2 to GE5 are in the gear coupling state, the same force as shown in FIGS. 4A and 4B is applied to the guide pins DRa of the gear coupling mechanisms GE2 to GE5. It acts from the guide groove HBa.

  The hub HB1 rotates in the direction of arrow F in FIGS. 4A and 4B when the vehicle travels forward, and rotates in the direction of arrow R when traveling backward. The guide groove HBa has a pair of opposite side surfaces, that is, a side surface HBa1 on the forward rotation side and a side surface HBa2 on the reverse rotation side. The guide groove HBa is formed so as to be symmetric with respect to the center line CL1 passing through the middle of the axial length (AB direction) of the hub HB1 and to have a constant groove width over the entire length. It has a substantially V shape so as to protrude in the F direction. Therefore, the side surfaces HBa1 and HBa2 are inclined at a predetermined angle θ1 with respect to the virtual line CL2 parallel to the axis CL0 (FIG. 3), and the angle θ0 formed by the pair of side surfaces HBa1 on both sides of the center line CL1 is 180 °. Smaller than.

  As shown in FIG. 4A, at the time of acceleration in the second speed traveling, the rotation of the hub HB1 is faster than the rotation of the movable ring DR1. Therefore, the side surface HBa2 of the guide groove HBa of the hub HB1 contacts the outer peripheral surface of the guide pin DRa, and the pressing force FA in the direction of arrow F corresponding to the torque in the acceleration direction acts on the guide pin DRa. At this time, since the side surface HBa2 of the guide groove HBa is inclined at an angle θ1 with respect to the virtual line CL2 in the axial direction, the axial force Fa in the arrow A direction perpendicular to the pressing force FA is applied to the guide pin DRa, that is, 2 A force that promotes meshing between the fast drive gear 22 and the movable ring DR1 (referred to as meshing promoting force) also acts.

  On the other hand, as shown in FIG. 4B, at the time of deceleration in the second speed traveling, the rotation of the hub HB1 is slower than the rotation of the movable ring DR1. For this reason, the side surface HBa1 of the guide groove HBa of the hub HB1 contacts the guide pin DRa, and the pressing force FB in the arrow R direction corresponding to the torque in the deceleration direction acts on the guide pin DRa. At this time, since the side surface HBa1 of the guide groove HBa is inclined at an angle θ1 with respect to the virtual line CL2 in the axial direction, the guide pin DRa has an axial force Fb in the direction of the arrow B perpendicular to the pressing force FB, that is, 2 A force for releasing the meshing between the fast drive gear 22 and the movable ring DR1 (referred to as a meshing release force) also acts.

  In this embodiment, the transmission 1 is configured so that the lower gear and the upper gear are meshed simultaneously when upshifting only one gear from the lower gear to the upper gear. Therefore, for example, when upshifting from the fourth speed to the fifth speed, the fourth gear coupling mechanism is further connected with the fourth speed driving gear 24 coupled to the second main input shaft 12 via the second gear coupling mechanism 2GE. A 5-speed drive gear 25 is coupled to the sub input shaft 13 via 4GE.

  At this time, the rotation of the hub HB2 of the second gear coupling mechanism 2GE is slower than the rotation of the movable ring DR2 (fourth speed drive gear 24). On the other hand, the rotation of the hub HB4 of the fourth gear coupling mechanism 4GE is faster than the rotation of the movable ring DR4 (5-speed drive gear 25). For this reason, the 4th speed drive gear 24 will be in the deceleration state of FIG. 4B, and the 5th speed drive gear 25 will be in the acceleration state of FIG. 4A. That is, when the 4-speed drive gear 24 and the 5-speed drive gear 25 are simultaneously meshed with the movable rings DR2, DR4, respectively, the 5-speed drive gear 25 rotates faster than the 4-speed drive gear 24. A part of the output torque acts as a circulating torque via the output shaft 14.

  Due to this circulating torque, the mesh release force Fb (FIG. 4B) acts on the guide pin DRa of the second gear coupling mechanism 2GE, and the movable ring DR2 moves in the direction of arrow B (mesh release direction) in FIG. 4B. As a result, the meshing between the dog tooth D4a of the movable ring DR2 and the dog tooth D4b of the fourth-speed drive gear 24 is released, and the second gear coupling mechanism 2GE becomes neutral. On the other hand, the meshing promoting force Fa (FIG. 4A) acts on the guide pin DRa of the fourth gear coupling mechanism 4GE, and the movable ring DR4 is pressed in the direction of arrow A (meshing promoting direction) in FIG. 4A. As a result, the meshing state between the dog teeth D5a of the movable ring DR4 and the dog teeth D5b of the fifth speed drive gear 25 is maintained, and the fourth gear coupling mechanism 4GE is in the gear coupling state.

  Such a mode of shifting while simultaneously engaging a pair of drive gears is called seamless shifting. By upshifting with seamless gear shifting, smooth gear shifting without torque loss becomes possible. On the other hand, a mode in which all gear coupling mechanisms 1GE to 5GE are once returned to the neutral state without shifting the pair of drive gears at the same time is referred to as a normal shift (non-seamless shift). In the present embodiment, as described later, the transmission 1 is configured such that not only a seamless shift but also a normal shift can be realized.

  The movable rings DR1 to DR5 are respectively moved from the neutral position to the in-gear position or from the in-gear position to the neutral position by the dog operating device, and the seamless gear shift or the normal gear shifting is performed by the dog operating device. Hereinafter, the configuration of the dog operating device according to the present embodiment will be described.

  FIGS. 5 and 6 are a perspective view and a side view, respectively, showing the main configuration of the gear mechanism 10 and the dog operating device 5 in the transmission 1. In the following, for convenience, three directions orthogonal to each other are defined as the front-rear direction, the left-right direction, and the up-down direction, respectively, and the configuration of each part will be described according to this definition. The vertical direction corresponds to, for example, the height direction of the vehicle, and the left-right direction corresponds to, for example, the vehicle width direction or the vehicle length direction.

  As shown in FIGS. 5 and 6, the dog operating device 5 includes a shift shaft 50 extending in the vertical direction along the axis line CLa, an actuator 60 connected to the upper end portion of the shift shaft 50, and a lower end of the shift shaft 50. And a plurality of shift forks 80 that transmit the movement of each shift rail 70 to the corresponding movable rings DR1 to DR5. The actuator 60 includes a first motor 61 that moves the shift shaft 50 in the vertical direction and a second motor 62 that rotates the shift shaft 50 about the axis line CLa. As many shift rails 70 as the movable rings DR1 to DR5 are provided (five).

  The shift shaft 50 includes a substantially cylindrical shaft body 51 extending along the axis CLa, and fingers 52 fixed to the lower portion of the shaft body 51. FIG. 7 is a perspective view of the finger 52, and FIG. 8 is a side view of the finger 52. FIG. 8 also shows a part (cross-sectional view) of the shift rail 70 disposed around the finger 52.

  7 and 8, the finger 52 includes a cylindrical portion 520 extending in the vertical direction along the axis line CLa, and a first direction perpendicular to the axis line CLa from the outer peripheral surface of the cylindrical portion 520 (in FIG. 7). A first protrusion FG1 protruding in the direction of arrow A) and a second protrusion FG2 protruding in the second direction opposite to the first direction (in the direction of arrow B in FIG. 7) from the outer peripheral surface of the cylindrical portion 520. A through hole 520a is opened in the vertical direction in the cylindrical portion 520, the shaft body 51 is inserted into the through hole 520a, and the finger 52 is fixed to the shaft body 51 by, for example, welding.

  The finger 52 has a first finger portion 521 to a ninth finger portion 529 that are continuous in the vertical direction. The lengths (heights) ΔL1 in the vertical direction of the finger portions 521 to 529 are equal to each other, and the cross-sectional shapes of the finger portions 521 to 529 cut by the cutting plane perpendicular to the axis line CLa are almost constant over the height ΔL1 direction. It is.

  9A to 9E show a first finger part 521 cut along the line AA in FIG. 8 perpendicular to the axis CLa, and a second finger part 522 cut along the line BB in FIG. 8, the third finger part 523 cut along the line CC in FIG. 8, the fifth finger part 525 cut along the line DD in FIG. 8, and cut along the line EE in FIG. It is sectional drawing (sectional drawing seen from upper direction) which shows the structure of the 6th finger part 526. FIG. Although illustration is omitted, the configuration of the fourth finger portion 524 and the ninth finger portion 529 is equal to the configuration of the third finger portion 523 (FIG. 9C), and the configuration of the seventh finger portion 527 is the sixth finger portion 526 ( The configuration of the eighth finger portion 528 is equal to the configuration of the first finger portion 521 (FIG. 9A).

  The finger 52 has a cross-sectional shape in FIG. 9C as a reference shape, and is configured by changing the reference shape in a predetermined finger portion. First, the reference shape will be described. As shown in FIG. 9C, the third finger portion 523, the fourth finger portion 524, and the ninth finger portion 529 are first protrusions that protrude from the outer peripheral surface of the cylindrical portion 520 along the axis CLb perpendicular to the axis CLa. It has part FG1 and 2nd protrusion part FG2.

  The first protrusion FG1 and the second protrusion FG2 have the same shape, and the first protrusion FG1 and the second protrusion FG2 are configured symmetrically with respect to the axis CLb. That is, the pair of side surfaces FG11 and FG12 of the first protrusion FG1 and the pair of side surfaces FG21 and FG22 of the second protrusion FG2 are formed symmetrically with respect to the axis CLb. Hereinafter, of the side surfaces FG11, FG12, FG21, and FG22 of the protrusions FG1 and FG2, the side surfaces FG11 and FG21 on the side of the first rotation direction (arrow R1 direction) centered on the axis line CLa are the first side surface and the axis line CLa. Side surfaces FG12 and FG22 on the side of the second rotation direction (arrow R2 direction) opposite to the first rotation direction centering on are referred to as second side surfaces.

  The first side surface FG11 and the second side surface FG12 of the first protrusion FG1 are connected by a first peripheral surface FG13. The first side surface FG21 and the second side surface FG22 of the second protrusion FG2 are connected by the second peripheral surface FG23. The first peripheral surface FG13 and the second peripheral surface FG23 are each formed along an arc having a radius r1 with the axis line CLa as the center.

  As shown in FIG. 9A, the first finger portion 521 and the eighth finger portion 528 are configured such that the first side surface FG11 and the second side surface FG12 of the first protrusion FG1 are symmetrical with respect to the axis line CLb. On the other hand, the first side surface FG21 and the second side surface FG22 of the second protrusion FG2 are asymmetric. That is, the notch CT1 is provided in the first side face FG21 of the second protrusion FG2, and the first side face FG21 is located on the axis CLb side with respect to the reference shape (dotted line).

  As shown in FIG. 9B, the second finger portion 522 is configured such that the first side surface FG21 and the second side surface FG22 of the second protrusion FG2 are symmetrical with respect to the axis line CLb. On the other hand, the first side surface FG11 and the second side surface FG12 of the first protrusion FG1 are asymmetric. That is, the notch CT2 is provided in the second side surface FG12 of the first protrusion FG1, and the second side surface FG12 is positioned on the axis CLb side with respect to the reference shape (dotted line).

  As shown in FIG. 9D, the fifth finger portion 525 at the center in the vertical direction has only the first protrusion portion FG1 without the second protrusion portion FG2, and protrudes only from the cylindrical portion 520 along the axis CLb. To do. A protrusion FG3 is provided at the tip of the first protrusion FG1. Accordingly, the first protrusion FG1 of the fifth finger portion 525 protrudes by a predetermined amount from the reference shape (dotted line), and the length r3 from the axis CLa to the tip of the protrusion FG3 is longer than r1 in FIG. 9C. Note that the first side surface FG11 and the second side surface FG12 of the first protrusion FG1 having the protrusion FG3 are formed symmetrically with respect to the axis CLb.

  As shown in FIG. 9E, the sixth finger portion 526 and the seventh finger portion 527 are configured such that the first side surface FG11 and the second side surface FG12 of the first protrusion FG1 are symmetrical with respect to the axis line CLb. On the other hand, the first side surface FG21 and the second side surface FG22 of the second protrusion FG2 are asymmetric. That is, the notch CT3 is provided in the second side face FG22 of the second protrusion FG2, and the second side face FG22 is located on the axis CLb side with respect to the reference shape (dotted line).

  FIG. 10 is a diagram showing the structure of the finger 52 as a model. In FIG. 10, the first protrusions FG1 of the first finger part 521 to the ninth finger part 529 are F1 to F9, respectively, the first finger part 521 to the fourth finger part 524 and the sixth finger part 526 to the ninth finger. The 2nd protrusion part FG2 of the part 529 is each represented by F10-F17.

  Further, as will be described later, when the transmission 1 is shifted to the electric motor 3 side in FIG. 1, that is, one of the first to fourth speeds, the engaging portion delays the timing of the shift by the notch CT1 (FIG. 9A). That is, the first protrusion F10 of the first finger part 521 and the second protrusion F16 of the eighth finger part 528 are denoted by F10a and F16a with a suffix a. Further, as will be described later, when the transmission 1 is shifted to the clutch mechanism side in FIG. 1, that is, any one of the fifth to eighth gears, the shift timing is delayed by the notches CT2 and C3 (FIGS. 9B and 9E). The engaging portions to be made, that is, the first protruding portion F2 of the second finger portion 522, the second protruding portion F14 of the seventh finger portion 527, and the second protruding portion F15 of the eighth finger portion 528 are each denoted by the symbol b. F2b, F14b, and F15b. The first protruding portion F5 of the fifth finger portion 525 having the protruding portion FG3 is denoted by F5c with a suffix c.

  Around the fingers 52 configured as described above, a plurality of (five) shift rails 70 having the same shape, that is, the first shift rail 71 to the fifth shift rail 75 as shown in FIGS. Are arranged at equal intervals in the vertical direction.

  As shown in FIG. 8, the distance ΔL2 between the shift rails 71 to 75 adjacent in the vertical direction is equal to the vertical length ΔL1 of the finger portions 521 to 529. The vertical position of the finger 52 with respect to the shift rail 70 is changed by the vertical movement of the finger 52 by the actuator 60. Thereby, the 1st finger part 521-the 9th finger part 529 can be arrange | positioned facing the internal peripheral surface of the desired shift rails 71-75. The direction in which the finger 52 can move (vertical direction) is called a select direction. By rotating the finger 52, the protrusions FG1 and FG2 of the finger 52 can be engaged with the inner peripheral surfaces of the shift rails 71 to 75.

  FIG. 11 is a plan view (viewed from above) of the shift rail 70 (first shift rail 71 to fifth shift rail 75). In FIG. 11, the reference shape (FIG. 9C) of the finger 52 in the neutral posture is indicated by a solid line, and the cutouts CT1 to CT3 (FIGS. 9A, 9B, and 9E) and the protrusion FG3 (FIG. 9D) are indicated by a dotted line. The neutral posture refers to a case where the angle (finger rotation angle) θa formed between the reference line CLd extending in the front-rear direction through the axis CLa and the axis CLb is 0 ° (see FIG. 14).

  As shown in FIG. 11, the shift rail 70 is formed in a substantially rectangular plate shape extending in the direction perpendicular to the axis CLa (front-back and left-right directions). The shift rail 70 has an opening 700 penetrating in the vertical direction, and the finger 52 is disposed in the opening 700 so as to be movable in the vertical direction and rotatable about the axis line CLa. Assuming that a center line extending in the vertical direction through the center of the opening 700 is CLc, the center line CLc indicates that when the shift rail 70 is positioned at a neutral position in the middle in the left-right direction as shown in FIG. It coincides with the axis line CLa.

  The opening 700 has a pair of left and right peripheral surfaces 701 formed along a virtual circle with a radius r2 around the center line CLc, and is cut out in a substantially U shape in the front-rear direction from the peripheral surface 701 along the axis CLb. And a pair of front and rear cutout portions 702 and 703. The radius r2 of the peripheral surface 701 is equal to or longer than the length from the axis CLa to the first peripheral surface FG13 and the second peripheral surface FG23 of the finger 52 (radius r1 in FIG. 9C), and the protruding portion of the finger 52 from the axis CLa. It is shorter than the length to the tip of FG3 (radius r3 in FIG. 9D).

  The notch 702 has a pair of left and right side surfaces 702a and 702b extending in the front-rear direction, and a front end surface 702c connecting the side surfaces 702a and 702b. The notch 703 has a pair of left and right side surfaces 703a and 703b extending in the front-rear direction, and a rear end surface 703c connecting the side surfaces 703a and 703b. The length from the center line CLc to the rear end surface 703c of the notch 703 is longer than the length from the center line CLc to the front end surface 702c of the notch 702, and is larger than the radius r3 of the protrusion FG3 of the finger 52. long. In the neutral posture, the finger 52 is disposed such that the first protrusion FG1 is disposed in the notch 703 and the second protrusion FG2 is disposed in the notch 702.

  One end portion of the corresponding shift fork 80 is fixed to the end portion 70 a of each shift rail 71 to 75. Note that the position and shape of the end portion 70a to which the shift fork 80 is fixed differ for each of the shift rails 71 to 75. As shown in FIGS. 5 and 6, the other end of each shift fork 80 is connected to movable rings DR1 to DR5 of gear coupling mechanisms 1GE to 5GE, respectively.

  Each shift fork 80 is supported so as to be movable in the left-right direction along a guide 81 extending in the left-right direction, and each shift rail 71 to 75 is integrated with the shift fork 80 according to the engaging operation with the finger 52. Move left and right. That is, the shift rails 71 to 75 move from the neutral position in FIG. 11 to the right shift position shifted to the right or the left shift position shifted to the left, or from the right shift position or the left shift position to the neutral position. The direction (left-right direction) in which the shift rails 71 to 75 can move is referred to as a shift direction. As the shift rails 71 to 75 move in the left-right direction, the movable rings DR1 to DR5 move in the left-right direction via the shift fork 80.

  FIG. 12 is a diagram showing the configuration of the shift rail 70 in association with the movable rings DR1 to DR5. As shown in FIG. 12, the first shift rail 71 is connected to the movable ring DR1 of the first gear coupling mechanism 1GE via a shift fork 80, and the second shift rail 72 is coupled to the second gear coupling mechanism via the shift fork 80. The third shift rail 73 is connected to the movable ring DR5 of the fifth gear coupling mechanism 5GE via the shift fork 80, and the fourth shift rail 74 is connected to the third gear via the shift fork 80. The fifth shift rail 75 is coupled to the movable ring DR4 of the fourth gear coupling mechanism 4GE via the shift fork 80. The fifth shift rail 75 is coupled to the movable ring DR3 of the coupling mechanism 3GE.

  When the first shift rail 71 moves from the neutral position to the left shift position or the right shift position by the engagement operation of the shift rail 70 and the finger 52 due to the rotation of the finger 52, the movable ring DR1 moves to the second speed drive gear side or the eighth speed. The second gear or the eighth gear is established by moving to the in-gear position on the drive gear side. When the second shift rail 72 moves from the neutral position to the left shift position or the right shift position, the movable ring DR2 moves to the in-gear position on the 4th speed drive gear side or 7th speed drive gear side, and the 4th speed stage or 7th speed stage changes. Establish.

  When the third shift rail 73 moves from the neutral position to the left shift position or the right shift position, the movable ring DR5 moves to the in-gear position or the parking operation position on the reverse drive gear side, and the reverse gear is established or the parking mechanism is operated. When the fourth shift rail 74 moves from the neutral position to the left shift position or the right shift position, the movable ring DR3 moves to the in-gear position on the first speed drive gear side or the sixth speed drive gear side, and the first speed stage or the sixth speed stage changes. Establish. When the fifth shift rail 75 moves from the neutral position to the left shift position or the right shift position, the movable ring DR4 moves to the in-gear position on the third speed drive gear side or the fifth speed drive gear side, so that the third speed stage or the fifth speed stage is set. Establish.

  The finger driving actuator 60 is controlled by the controller 63 of FIG. 8 which constitutes a part of the electronic control unit. The controller 63 selects a gear position according to an operation of a range selector that can be operated in a range such as L, S, D, N, R, and P. When the D range is selected by operating the range selector, the automatic shift mode is set, and the controller 63 selects the target shift stage based on the depression amount of the accelerator pedal and the vehicle speed. Further, the controller 63 controls the movement and rotation of the finger 52 in the select direction so that the transmission 1 reaches the target shift stage, and moves the desired shift rail 70 in the shift direction.

  FIG. 13 is a diagram showing the positional relationship of the finger 52 with respect to the shift rail 70 when shifting from the current shift speed (current speed) to the target shift speed (next speed). More specifically, the protrusions F1 to F17 (FIG. 12) of the finger 52 corresponding to the first shift rail 71 to the fifth shift rail 75 (FIG. 12) after the finger 52 is moved in the select direction according to the target shift speed. It is a figure which shows the positional relationship of 10). In FIG. 13, the reference numerals in parentheses in FIG. 10 are used for the protrusions F2, F5, F10, and F14 to F16.

  In the following, the position where the protrusion F5c of the fifth finger portion 525 at the center in the vertical direction faces the first shift rail 71 for 2-8 speed is the 2-8 speed select position, and the second shift for 4-7 speed. The position facing the rail 72 is the 4-7 speed select position, the position facing the reverse and parking third shift rail 73 is the RP select position, and the position facing the 4th shift rail 74 for 1-6 speed. Is referred to as the 1-6th speed select position, and the position facing the fifth shift rail 75 for 3-5th speed is referred to as the 3-5th speed select position. The finger 52 moves to any one of the select positions described above according to the target gear position.

  For example, when the target shift speed is 5th gear, the finger 52 moves to the 3-5th gear select position in a neutral posture. At this time, as shown in part A of FIG. 13, the protruding portion F5 of the fifth finger portion 525 is disposed so as to face the inner peripheral surface of the fifth shift rail 75 for 3-5 speed. The protrusions F1 and F10a of the first finger portion 521 are arranged so as to face the inner peripheral surface of the first shift rail 71 for 2-8 speed. The protrusions F2b and F11 of the second finger portion 522 are disposed so as to face the inner peripheral surface of the second shift rail 72 for 4-7 speed. The protrusions F3 and F12 of the third finger part 523 are arranged so as to face the inner peripheral surface of the third shift rail 73 for RP. The protrusions F4 and F13 of the fourth finger portion 524 are disposed so as to face the inner peripheral surface of the fourth shift rail 74 for 1-6 speed.

  For example, when the target shift speed is the second speed, the finger 52 moves to the 2-8 speed select position with the neutral posture. At this time, as shown in part B of FIG. 13, the protruding part F5c of the fifth finger part 525 is arranged to face the inner peripheral surface of the first shift rail 71 for 2-8 speed. The protruding portions F6 and F14b of the sixth finger portion 526 are arranged so as to face the inner peripheral surface of the second shift rail 72 for 4-7 speed. The protrusions F7 and F15b of the seventh finger portion 527 are arranged to face the inner peripheral surface of the third shift rail 73 for RP. The protruding portions F8 and F16a of the eighth finger portion 528 are disposed so as to face the inner peripheral surface of the fourth shift rail 74 for 1-6 speed. The protrusions F9 and F17 of the ninth finger portion 529 are disposed so as to face the inner peripheral surface of the third shift rail 75 for 3-5 speed.

  Thus, after the finger 52 is moved in the select direction according to the target shift stage by driving the actuator 60, the finger 52 is rotated about the axis line CLa (FIG. 8) and engaged with the shift rail 70. Operation is performed. FIG. 14 is a diagram showing an example of an engaging operation at the time of upshift from the fourth speed to the fifth speed along a time series. 14 shows the positional relationship of the second finger part 522 with respect to the second shift rail 72 for 4-7 speed (only the opening 700 is shown), and the lower part shows the fifth shift rail 75 for 3-5 speed ( The positional relationship of the 5th finger part 525 with respect to the opening part 700 is shown. In FIG. 14, the states of the shift rails 72 and 75 at the start of shifting (time point a) are indicated by dotted lines.

  When shifting from the fourth speed to the fifth speed, the finger 52 moves from the 4-7 speed select position to the 3-5 speed select position in a neutral posture. When the transmission 1 is shifted to the fourth speed, the second shift rail 72 moves to the left shift position (FIG. 12). Therefore, as shown in FIG. 14, at the start of the shift immediately after the finger 52 moves in the 3-5 speed select direction (time point t1), the second shift rail 72 is shifted from the neutral position to the left and moved to the left shift position. The center line CLc of the second shift rail 72 is shifted to the left by a predetermined distance ΔLa0 from the axis line CLa of the finger 52. At this time, the fifth shift rail 75 is in the neutral position, and the center line CLc coincides with the axis line CLa.

  In this state, when the finger 52 rotates about the axis CLa in the direction of the arrow R1 and the finger rotation angle θa reaches the predetermined angle θa2 (time point t2), the first protrusion FG1 (F2b) of the second finger 522 The second side surface FG12 contacts the side surface 703b of the notch 703 of the second shift rail 72. As a result, a rightward pressing force acts on the second shift rail 72 from the first projecting portion FG1 of the second finger portion 522. Since the notch CT2 is provided in the second side surface FG12 of the second finger part 252, the finger rotation angle θa at the time of contact is larger than when the reference-shaped finger part (third finger part 523, etc.) is in contact. The timing at which the side surface FG12 contacts the side surface 703b is late.

  When the finger rotation angle θa reaches a predetermined angle θa3 (> θa2) (time point t3), the side surface FG12 of the projection FG3 (F5c) of the fifth finger portion 525 is changed to the side surface 703b of the cutout portion 703 of the fifth shift rail 75. To touch. When the finger rotation angle θa reaches a predetermined angle θa4 (> θa3) (time point t4), the fifth shift rail 75 is moved a predetermined distance from the neutral position to the right side by the pressing force from the first protrusion FG1 of the fifth finger portion 525. Shift by ΔLa1. Thereby, the dog tooth D5a of the movable ring DR4 shown in FIG. 1 starts to contact the dog tooth D5b of the fifth speed drive gear 25.

  When the finger rotation angle θa reaches a predetermined angle θa5 (> θa4) (time point t5), the fifth shift rail 75 shifts to the right side by a predetermined distance ΔLa2. As a result, the movable ring DR4 moves to the in-gear position, and the dog teeth D5a and D5b mesh with each other to establish the fifth gear. When the finger rotation angle θa reaches the predetermined angle θa6 (> θa5) (time point t6), the second shift rail 72 approaches the neutral position, and the distance from the center line CLc to the axis line CLa of the second shift rail 72 is the predetermined distance ΔLa3. It becomes. Thereby, movable ring DR2 (FIG. 1) moves to a neutral position, and mesh | engagement of dog teeth D2a and D2b is cancelled | released.

  From time t5 to time t6, the dog tooth D4b of the fourth speed drive gear 24 is engaged with the dog tooth D4a of the movable ring DR2, and at the same time, the dog tooth D5a of the fifth speed drive gear 25 is the dog tooth of the movable ring DR4. Engage with D5b. At this time, as described above, the circulating torque via the output shaft 14 acts on the lower movable ring DR2, and the mesh release force Fb (FIG. 4B) acts on the lower movable ring DR2. Thereby, it is possible to prevent the movable ring DR2 from moving to the neutral position side and the dog teeth D4a and D4b for the fourth speed and the D5a and D5b for the fifth speed to be engaged with each other.

  When the finger rotation angle θa reaches the predetermined angle θa7 (> θa6) (time t7), the fifth shift rail 75 shifts to the right side by a predetermined distance ΔLa4. Thereby, the fifth shift rail 75 moves to the right shift position, and the shift from the fourth speed to the fifth speed is completed. At this time, the second shift rail 72 moves to the neutral position. After the shift is completed, the finger 52 rotates by a predetermined angle θa7 in the arrow R2 direction and returns to the neutral posture of θa = 0 °. When the target gear position is changed, the finger 52 moves in the select direction while maintaining the neutral posture, and the same operation is repeated.

  As described above, in the present embodiment, the notch CT2 is provided on the side surface FG12 of the second finger portion 522, and when the upshift from the fourth speed to the fifth speed is performed, the timing of the movement to the neutral position of the second shift rail 72 is delayed. I made it. As a result, a seamless speed change can be realized, a smooth upshift without torque loss is possible, and the drivability of the vehicle is improved.

  As shown by hatching in FIG. 13, when the next shift stage that is one greater than the current shift stage is used as the target shift stage, not only the upshift from the fourth speed but also the upshift from other shift stages, The protruding portion of the finger 52 having the cutouts CT1 to C3 is disposed to face the inner peripheral surface of the shift rail 70 corresponding to the target shift speed. For example, when upshifting from the first speed to the second speed, the protruding portion F16a of the eighth finger portion 528 having the notch CT1 is arranged to face the first shift rail 71 for 2-8 speed, and from the second speed When upshifting to the third speed, the protruding portion F10a of the first finger portion 521 having the notch CT1 is disposed to face the first shift rail 71 for 2-8 speed. As a result, even at the time of upshifting from another shift stage, the timing of movement to the neutral position of the shift rail can be delayed, and seamless shifting can be performed as described above.

  That is, when shifting from the current stage to the next stage, as shown in FIG. 13, when the movable rings DR1 to DR4 move to the electric motor 3 side in FIG. Projecting portions F10a and F16a with a suffix a are arranged opposite to the shift rail. On the other hand, when the gears DR1 to DR4 move to the clutch mechanism C side in FIG. 1 and shift to the fifth to eighth gears, when the upshift is performed by one step from the current step to the next step, the shift ring faces the current step. The protrusions F2b, F14b, and F15b to which the subscript b is attached are arranged. Therefore, the return operation to the neutral position of the current stage shift rail is delayed, and seamless shifting is possible.

  In the transmission 1 of the present embodiment, not only upshifting by one stage but also upshifting and downshifting over a plurality of stages (referred to as jumping shift) is possible. FIG. 15 is a diagram showing an example of an engaging operation at the time of upshift from the second speed to the fifth speed along a time series. 15 shows the positional relationship of the first finger portion 521 with respect to the first shift rail 71 for 2-8 speed, and the lower portion shows the fifth finger portion 525 with respect to the fifth shift rail 75 for 3-5 speed. The positional relationship of is shown.

  When shifting from the 2nd speed to the 5th speed, the finger 52 moves from the 2-8 speed select position to the 3-5 speed select position. As shown in FIG. 15, the second shift rail 72 remains moved to the left shift position (second speed side) at the start of shifting immediately after the finger 52 moves in the 3-5 speed select direction (time point t11). The center line CLc of the second shift rail 72 is shifted to the left side with respect to the axis line CLa of the finger 52. At this time, the fifth shift rail 75 is in a neutral position, similar to the time point t1 in FIG. 14, and the center line CLc coincides with the axis line CLa.

  In this state, when the finger 52 rotates around the axis CLa in the direction of the arrow R1 and the finger rotation angle θa reaches a predetermined finger rotation angle θa12 (time point t12), the first protrusion FG1 of the first finger portion 521 is reached. The side surface FG12 contacts the side surface 703b of the notch 703 of the first shift rail 71, and a rightward pressing force acts on the first shift rail 71. In this case, the finger rotation angle θa12 is smaller than the finger rotation angle θ2 of FIG. 14, and the contact timing of the first finger portion 521 is earlier than the contact timing of the second finger portion 522 of FIG.

  When the finger rotation angle θa reaches a predetermined angle θa13 (> θa12) (time point t13), the meshing between the dog tooth D2b of the second speed drive gear 22 and the dog tooth D2a of the movable ring DR1 is released. As a result, the transmission 1 is in a neutral state. When the finger rotation angle θa reaches a predetermined angle θa14 (> θa13) (time t14), the side surface FG12 of the projection FG3 of the fifth finger portion 525 is notched in the fifth shift rail 75, as at time t3 in FIG. The side surface 703b of the portion 703 is contacted, and a rightward pressing force acts on the fifth finger portion 525. At this time, the first shift rail 71 moves to the neutral position, and thereafter, the first peripheral surface FG13 and the second peripheral surface FG23 of the first finger portion 521 are respectively the peripheral surface 701 of the first shift rail 71 (FIG. 11). ) And the position of the first shift rail 71 is maintained at the neutral position.

  When the finger rotation angle θa reaches a predetermined angle θa15 (> θa14) (time t15), the dog tooth D5a of the movable ring DR4 starts to contact the dog tooth D5b of the fifth speed drive gear 25, as at time t4 in FIG. . At time t14 and time t15, both the first gear coupling mechanism 1GE for the second speed and the fourth gear coupling mechanism 4GE for the fifth speed are in the neutral state, and the transmission 1 is in the neutral state.

  When the finger rotation angle θa reaches a predetermined angle θa16 (> θa15) (time point t16), the movable ring DR4 moves to the in-gear position and the dog teeth D5a and D5b mesh with each other as in the time point t5 of FIG. A stage is established. When the finger rotation angle θa reaches a predetermined angle θa17 (> θa16) (time point t17), the fifth shift rail 75 moves to the right shift position, and the shift from the second speed to the fifth speed is completed. Thereafter, the finger 52 rotates by a predetermined angle θa17 in the direction of the arrow R2 and assumes a neutral posture.

  FIG. 16 is a diagram showing an example of the engaging operation at the time of downshift from the fifth speed to the second speed in time series. 16 shows the positional relationship of the fifth finger portion 525 with respect to the first shift rail 71 for 2-8 speed, and the lower portion shows the ninth finger portion 529 with respect to the fifth shift rail 75 for 3-5 speed. The positional relationship of is shown.

  When shifting from the fifth speed to the second speed, the finger 52 moves from the 3-5 speed select position to the 2-8 speed select position. As shown in FIG. 16, at the start of shifting immediately after the finger 52 moves in the 2-8th speed select direction (time t21), the fifth shift rail 75 remains moved to the right shift position (5th speed side). The center line CLc of the fifth shift rail 75 is shifted to the right side with respect to the axis line CLa of the finger 52. At this time, the first shift rail 71 is in the neutral position, and the center line CLc coincides with the axis line CLa.

  In this state, when the finger 52 rotates around the axis CLa in the direction of the arrow R2 and the finger rotation angle θa reaches a predetermined finger rotation angle θa22 (time point t22), the first protrusion FG1 of the ninth finger portion 529 The side surface FG11 contacts the side surface 703a of the notch 703 of the fifth shift rail 75, and a leftward pressing force acts on the fifth shift rail 75. The finger rotation angle θa22 in this case is smaller than the finger rotation angle θ2 of FIG. 14, and the contact timing of the ninth finger portion 529 is earlier than the contact timing of the second finger portion 522 of FIG.

  When the finger rotation angle θa reaches a predetermined angle θa23 (> θa22) (time point t23), the meshing between the dog teeth D5b of the fifth speed drive gear 25 and the dog teeth D5a of the movable ring DR4 is released. As a result, the transmission 1 is in a neutral state. When the finger rotation angle θa reaches a predetermined angle θa24 (> θa23) (time t24), the side surface FG11 of the projection FG3 of the fifth finger portion 525 contacts the side surface 703a of the cutout portion 703 of the first shift rail 71. . At this time, the fifth shift rail 75 moves to the neutral position, and thereafter, the first peripheral surface FG13 and the second peripheral surface FG23 of the ninth finger portion 529 are connected to the peripheral surface 701 of the fifth shift rail 75 (FIG. 11). And the position of the fifth shift rail 75 is maintained at the neutral position.

  When the finger rotation angle θa reaches a predetermined angle θa25 (> θa24) (time t25), the dog tooth D2a of the movable ring DR1 starts to contact the dog tooth D2b of the second speed drive gear 22. At time t24 and time t25, the first gear coupling mechanism 1GE for the second speed and the fourth gear coupling mechanism 4GE for the fifth speed are both in the neutral state, and the transmission 1 is in the neutral state.

  When the finger rotation angle θa reaches a predetermined angle θa26 (> θa25) (time point t26), the movable ring DR1 moves to the in-gear position, and the dog teeth D2a and D2b mesh with each other to establish the second gear. When the finger rotation angle θa reaches a predetermined angle θa27 (> θa26) (time t27), the first shift rail 71 moves to the left shift position, and the shift from the fifth speed to the second speed is completed. Thereafter, the finger 52 rotates by a predetermined angle θa27 in the direction of the arrow R1 and assumes a neutral posture.

  As described above, in the present embodiment, the normal shift through the neutral state of the transmission 1 enables upshifts and downshifts that jump over a plurality of stages, that is, jump shifts. For this reason, for example, when the kick-down operation is performed by largely depressing the accelerator pedal, the transmission 1 can be immediately changed to a desired gear position, and the drivability of the vehicle is improved.

  For example, as shown in part C of FIG. 13, when shifting from the fourth speed to the second speed, the protruding part F <b> 14 b having the notch CT <b> 3 faces the second shift rail 72. However, in this case, since the second side surface FG22 on the opposite side of the notch CT3 of the protruding portion 14b contacts the second shift rail 72, there is no delay in the return operation to the neutral position of the second shift rail 72. Similarly, there is no delay in the return operation to the neutral position of the shift rail at the time of other gear shifts except for the upshift by one step such as the shift from the 8th gear to the 5th gear shown in the D part of FIG.

According to this embodiment, the following effects can be obtained.
(1) The transmission 1 is movable in the axial direction to each of the plurality of hubs HB1 to HB5 (for example, the hub HB2 rotating about the axis CL0) and the plurality of hubs HB1 to HB5. A plurality of movable rings DR1 to DR5 that are rotatably supported integrally and have dog teeth D1a to D9a corresponding to the gears, and dog teeth D1b to D9b corresponding to the gears facing the dog teeth D1a to D9a. At the same time, a plurality of speed change drive gears 21 to 30 that rotate about the axis (for example, a second speed drive gear 22 that rotates about the axis CL0) and a plurality of hubs HB1 to HB5 are connected to the rotation shaft (second main input shaft). 12, a sub-input shaft 13 and a reverse shaft 15), and a support mechanism 120 that supports a plurality of drive gears 21 to 30 so as to be rotatable relative to the rotary shafts 12, 13, and 15. The plurality of movable rings DR1 to DR5 are operated to move between a neutral position where the dog teeth D1a to D9a are separated from the dog teeth D1b to D9b and an in-gear position where the dog teeth D1a to D9a mesh with the dog teeth D1b to D9b. The dog operation device 5 to be engaged with the lower dog teeth (for example, the 4th-speed dog teeth D4a and D4b) and the upper dog teeth (for example, the 5th-speed dog teeth D5a and D5b) simultaneously by the operation of the dog operation device 5 Gear coupling mechanisms 1GE to 4GE that return the movable ring having the lower dog teeth (for example, the movable ring DR2 having the fourth-tooth dog teeth D4a) from the in-gear position to the neutral position among the plurality of movable rings DR1 to DR5. (FIGS. 1, 3 and 4B). The dog operating device 5 extends along the axis line CLa, and moves the shift shaft 50 along the axis line CLa with the shift shaft 50 having fingers 52 projecting from the outer peripheral surface. The actuator 60 that rotates the shift shaft 50 and the notches 702 and 703 that are juxtaposed along the axis CLa and with which the fingers 52 can be engaged. The fingers 52 and the notches 702 and 703 of the actuator 60 In accordance with the engagement operation, the movement of each of the plurality of shift rails 71 to 75 moving in the direction substantially perpendicular to the axis CLa and the plurality of plate shift rails 71 to 75 is changed to a plurality of shift rails 71 to 75. Is transmitted to the movable rings DR1 to DR5, and the movable rings DR1 to DR5 are also moved from the neutral position to the in-gear position. It includes a shift fork 80 to move toward the neutral position from the in-gear position.

  Thereby, the finger 52 of the shift shaft 50 can be engaged with any shift rails 71 to 75 corresponding to the target shift speed. Therefore, it is possible to perform not only a shift (seamless shift) that increases by one step from the lower step to the upper step, but also a shift (jump shift) that increases and decreases a plurality of steps at once from the lower step to the upper step and from the upper step to the lower step. As a result, a smooth upshift without torque loss is possible, and a speed change operation is possible in which the accelerator pedal is suddenly depressed and the gear speed is lowered a plurality of speeds at a stroke, thereby improving the drivability of the vehicle.

(2) The dog operating device 5 sets the target shift speed, and after moving the shift shaft 50 along the axis line CLa according to the target shift speed, the dog operating device 5 rotates the shift shaft 50 about the axis line CLa. A controller 63 for controlling 60 is further provided (FIG. 8). As a result, the engagement operation between the shift rail 70 and the finger 52 corresponding to the target shift stage can be easily realized, and the transmission 1 can realize both the seamless shift and the jump shift.

(3) The plurality of movable rings DR1 to DR5 are provided corresponding to the gear position, and the plurality of shift rails 71 to 75 are provided corresponding to the movable rings DR1 to DR5 (FIGS. 1 and 12). The finger 52 has a plurality of finger portions 521 to 529 provided corresponding to the plurality of shift rails 71 to 75 (FIG. 10). Accordingly, the protrusions F1 to F17 of any of the plurality of finger portions 521 to 529 can be engaged with any of the plurality of different shift rails 71 to 75, respectively, and the plurality of shift rails 71 to 75 can be engaged with good timing. It can move in the shift direction.

(4) The plurality of finger portions 521 to 529 is a number obtained by subtracting 1 from twice the number of shift rails 71 to 75, that is, nine finger portions 521 to 529, and among the plurality of finger portions 521 to 529 The central finger portion 525 constitutes an in-gear protrusion F5c for moving the movable ring from the neutral position to the in-gear position, while the other finger portions excluding the central finger portion 525 (for example, the first finger portion 521, The second finger part 522 and the ninth finger part 529) constitute off-gear protrusions (for example, F1, F2b, F9) for moving the movable ring from the in-gear position to the neutral position (FIGS. 14 to 16). . Thereby, the number of the finger parts 521-529 can be suppressed to the necessary minimum, and the finger 52 can be comprised compactly.

(5) The plurality of movable rings include, for example, a fourth-speed movable ring DR2 and a fifth-speed movable ring DR4, and the plurality of shift rails 70 include the second shift rail 72 and the movable ring corresponding to the movable ring DR2. And a fifth shift rail 75 corresponding to DR4 (FIGS. 1 and 12). The finger 52 establishes the fifth speed stage by operating the dog operating device 5 from the state where the movable ring DR4 is located at the neutral position and the movable ring DR2 is located at the in-gear position and the fourth speed stage is established. A second finger portion 522 that engages with the second shift rail 72 and moves the movable ring DR2 to the neutral position, and a fifth finger that engages with the fifth shift rail 75 and moves the movable ring DR4 to the in-gear position. The second finger portion 522 and the fifth finger portion 525 are protrusions F2b configured such that the movable ring DR4 moves to the in-gear position before the movable ring DR2 moves to the neutral position. F5c (FIG. 14). As a result, when upshifting from the lower stage to the upper stage one step at a time, it is possible to perform a shift in which the lower dog teeth D4a and D4b and the upper dog teeth D5a and D5b are simultaneously meshed, that is, a seamless shift.

(6) The plurality of movable rings include, for example, a second-speed movable ring DR1 and a fifth-speed movable ring DR4 having two or more stages higher than the second speed, and the plurality of shift rails 70 correspond to the movable ring DR1. A first shift rail 71 and a fifth shift rail 75 corresponding to the movable ring DR4 are included (FIGS. 1 and 12). The finger 52 establishes the second gear stage by operating the dog operating device 5 from the state where the movable ring DR1 is located at the neutral position and the movable ring DR4 is located at the in-gear position and the fifth gear stage is established. When the movable ring DR1 moves to the in-gear position, it has a ninth finger portion 529 that engages with the shift rail 75 and moves the movable ring DR4 to the neutral position (FIG. 16). Thus, unlike the case of upshifting one step at a time, it is possible to realize a jump shift from the upper stage to the lower stage without simultaneously meshing the upper dog teeth D5a, D5b and the lower dog teeth D2a, D2b.

(7) The second finger portion 522 is changed from the fourth speed to the fifth speed rather than the timing at which the ninth finger portion 529 engages the notch portion 703 of the fifth shift rail 75 at the time of shifting from the fifth speed to the second speed. A notch CT2 is provided so as to delay the timing at which the second finger portion 522 engages with the notch 703 of the second shift rail 72 at the time of shifting (FIG. 7). Similarly, the first finger portion 521 and the eighth finger portion 528 and the sixth finger portion 526 and the seventh finger portion 527 have notches CT1 and CT3 (FIGS. 9A and 9E). As a result, a seamless shift can be realized with a simple configuration while allowing a normal shift.

  In the above embodiment (FIGS. 2 and 3), the dog teeth D2a and D8a (first dog teeth) D1 are formed in a convex shape on the movable ring DR1, and the drive gear (transmission gear) 22 is opposed to the teeth. Although dog teeth D2b and D8b (second dog teeth) are formed in a concave shape in 28, the configuration of the first dog teeth and the second dog teeth is not limited to this. In the above embodiment (FIG. 3), the hub HB1 and the drive gears 22 and 28 are rotatably provided about the axis CL0 (first axis), and the hub HB1 is connected to the second main input shaft via the support mechanism 120. 12 (rotating shaft) is supported so as to be rotatable integrally, and the gears 22 and 28 are supported so as to be relatively rotatable. For example, the gears for shifting are supported so as to be rotatable integrally with the rotating shaft, and The hub may be rotatably supported integrally with the rotation shaft, and the configuration of the support mechanism is not limited to that described above.

  In the above embodiment (FIGS. 2 and 4B), the gear coupling mechanism is configured by engaging the guide pin DRa projecting from the inner peripheral surface of the movable ring DR1 with the substantially V-shaped guide groove HBa on the outer peripheral surface of the hub HB1. 1GE is configured to prevent co-biting between the lower dog teeth and the upper dog teeth, but when the lower dog teeth and the upper dog teeth mesh at the same time by the operation of the dog operating device, As long as the movable ring having the lower dog teeth is returned from the in-gear position to the neutral position, any configuration of the co-biting prevention mechanism may be used. In the above embodiment (FIGS. 7 and 8), the shaft body 51 extending along the axis line CLa (second axis line) is inserted into the through hole 520a of the finger 52, and the shift shaft 50 as the shaft member is formed. Although it comprised, as long as it has the finger (engagement piece) protruding from an outer peripheral surface, the structure of a shaft member may be what.

  In the above embodiment (FIGS. 5 and 6), the actuator 60 as a drive unit moves the shift shaft 50 along the axis line CLa and rotates the shift shaft 50 about the axis line CLa. The drive unit may have any configuration. In the above embodiment (FIGS. 8 and 11), a plurality of shift rails 71 to 75 (plate members) are arranged side by side along the axis line CLa, and a notch 703 is provided on the inner peripheral surface of the shift rails 71 to 75. The shift rails 71 to 75 are moved in a substantially vertical direction (left-right direction) with respect to the axis line CLa in accordance with the engaging operation between the finger 52 and the notch 703. An engaged portion that can be engaged may be configured, and the configuration of the plate member is not limited to that described above.

  In the above embodiment (FIGS. 5 and 6), the movement of the shift rails 71 to 75 is transmitted to the corresponding movable rings DR1 to DR5 via the shift fork 80, and the movable rings DR1 to DR5 are moved from the neutral position to the in-gear position. Alternatively, the movement fork is moved from the in-gear position to the neutral position, but the configuration of the shift fork as the operation transmitting portion is not limited to the above. In the above-described embodiment, the controller 63 as the control unit sets the target shift speed according to the vehicle speed and the depression amount of the accelerator pedal, and moves the shift shaft 50 along the axis CLa according to the target shift speed. Although the actuator 60 is controlled to rotate around the axis CLa later, for example, a gear manually input by the driver may be set as the target gear, and the configuration of the control unit is not limited to that described above.

  In the said embodiment (FIG. 8), the several finger part 521-529 which comprises the finger 52 as a protrusion part has been arrange | positioned without gap in the up-down direction. More specifically, the finger 52 is constituted by nine finger portions 521 to 529 obtained by subtracting 1 from twice the number (5) of the shift rails 71 to 75, and the central finger portion 525 (projecting portion F5c). Constitutes an in-gear engagement part for moving the movable rings DR1 to DR5 from the neutral position to the in-gear position, and the other finger parts 521 to 524 and 526 to 529 move the movable rings DR1 to DR5 from the in-gear position to the neutral position. Although the off-gear engaging portion for moving is configured, the configuration of the engaging piece is not limited to this. For example, a plurality of finger portions may be arranged with a gap in the vertical direction. The number of finger portions is not limited to that described above, and may be more than twice the number of shift rails, for example.

  In the above-described embodiment (FIG. 14), the second shift rail 72 corresponding to the movable ring DR2 for the fourth speed is used as the first plate member corresponding to the first movable ring for the first gear, and the second gear stage is used. The operation at the time of upshifting from the fourth speed to the fifth speed has been described using the fifth shift rail 75 corresponding to the fifth-speed movable ring DR4 as the second plate member corresponding to the second movable ring. In other words, the second finger portion 522 is used as the first engaging portion that moves the movable ring DR2 to the neutral position, and the fifth finger portion 525 is used as the second engaging portion that moves the movable ring DR4 to the in-gear position. An example of shifting operation has been described. In particular, in the above-described embodiment, before the movable ring DR2 moves to the neutral position by providing the notch CT2 in the protrusion F2b of the protrusion F2b of the second finger part 522 and the protrusion F5c of the fifth finger part 525. Although the movable ring DR4 is moved to the in-gear position, the configuration of the first engaging portion and the second engaging portion is not limited to this.

  In the above-described embodiment (FIG. 16), the first shift rail 71 corresponding to the second-speed movable ring DR1 is used as the first plate member corresponding to the first movable ring for the first gear, and the third gear stage. The fifth shift rail 75 corresponding to the fifth-speed movable ring DR4 is used as the third plate member corresponding to the third movable ring, and the jumping shift operation from the fifth speed to the second speed has been described. That is, the ninth finger portion 529 is used as the third engagement portion that moves the movable ring DR4 to the neutral position, and the fifth finger portion 525 is used as the first engagement portion that moves the movable ring DR1 to the in-gear position. An example of the speed change operation will be described, and the movable ring DR4 is moved to the neutral position before the movable ring DR1 is moved to the in-gear position. However, the configurations of the first engagement portion and the third engagement portion are the same. Not exclusively.

  In the above embodiment (FIGS. 14 and 16), by providing the notch CT2 in the second finger portion 522, for example, the ninth finger portion 529 (the third engagement portion) can be used at the time of jump shift from the fifth speed to the second speed. The second finger portion 522 (first engaging portion) is notched on the second shift rail 72 during the seamless shift from the fourth speed to the fifth speed than the timing at which the notched portion 703 of the fifth shift rail 75 is engaged. Although the timing of engaging with 703 is delayed, the configuration for shifting the timing at the time of seamless shifting is not limited to this.

  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, 5 dog operation device, 21-30 Drive gear, 50 Shift shaft, 52 finger, 60 Actuator, 63 Controller, 70 Shift rail, 80 Shift fork, 120 Support mechanism, 702, 703 Notch part, GE1-GE5 Gear coupling mechanism, HB1 to HB5 hub, DR1 to DR5 movable ring, D1a to D9a dog tooth, D1b to D9b dog tooth, CT1 to CT3 notch, F1 to F9 first protrusion, F10 to F17 second protrusion

Claims (7)

A plurality of hubs rotating about a first axis;
A plurality of movable rings supported by each of the plurality of hubs so as to be movable in an axial direction and integrally rotatable, and having first dog teeth corresponding to gears;
A plurality of speed change gears that rotate about the first axis and that have second dog teeth corresponding to the gear positions facing the first dog teeth;
A support mechanism that supports one of the plurality of hubs and the plurality of transmission gears so as to be rotatable integrally with a rotation shaft, and supports the other of the plurality of gears so as to be rotatable relative to the rotation shaft;
A dog operation for operating the plurality of movable rings so as to be movable between a neutral position where the first dog teeth are separated from the second dog teeth and an in-gear position where the first dog teeth mesh with the second dog teeth. Equipment,
When the first dog teeth and the second dog teeth on the lower stage and the first dog teeth and the second dog teeth on the upper stage are meshed simultaneously by operation of the dog operating device, the lower stage of the plurality of movable rings A co-biting prevention mechanism for returning the movable ring having the first dog teeth from the in-gear position to the neutral position,
The dog operating device is:
A shaft member having an engagement piece extending along the second axis and projecting from the outer peripheral surface;
A drive unit that moves the shaft member along the second axis and rotates the shaft member about the second axis;
A plurality of plate members arranged side by side along the second axis, and having an engaged portion with which the engaging piece can be engaged, and the engaging piece and the engaged portion by the drive portion A plurality of plate members that move in a substantially vertical direction with respect to the second axis,
The movement of each of the plurality of plate members is transmitted to the plurality of movable rings corresponding to the plate members, and the movable ring is moved from the neutral position to the in-gear position or from the in-gear position to the neutral position. And a transmission. The transmission according to claim 1, wherein
The dog operating device sets a target shift speed, and moves the shaft member along the second axis according to the target shift speed, and then rotates the shaft member around the second axis. The transmission further includes a control unit for controlling the driving unit. The transmission according to claim 1 or 2,
The plurality of movable rings are provided corresponding to a gear position, the plurality of plate members are provided corresponding to the plurality of movable rings, and the engagement piece is provided corresponding to the plurality of plate members. A transmission comprising a plurality of engaging portions. The transmission according to claim 3,
The plurality of engaging portions are composed of an engaging portion equal to or more than the number obtained by subtracting 1 from twice the number of the plate members, and a central engaging portion among the plurality of engaging portions attaches the movable ring to the movable ring. An in-gear engaging portion for moving from the neutral position to the in-gear position is configured, while the other engaging portions except the central engaging portion move the movable ring from the in-gear position to the neutral position. An off-gear engagement portion for the transmission is provided. The transmission according to claim 3 or 4,
The plurality of movable rings include a first movable ring for a first gear and a second movable ring for a second gear having a number of steps larger than the first gear,
The plurality of plate members include a first plate member corresponding to the first movable ring and a second plate member corresponding to the second movable ring,
In the engagement piece, the dog operation is performed when the second movable ring is located at the neutral position and the first movable ring is located at the in-gear position and the first gear is established. When the second shift stage is established by operating the device, the first engagement portion that engages with the first plate member and moves the first movable ring to the neutral position, and the second plate member are engaged. And a second engaging portion that moves the second movable ring to the in-gear position,
The first engaging portion and the second engaging portion are configured such that the second movable ring moves to the in-gear position before the first movable ring moves to the neutral position. Gearbox to do. The transmission according to claim 5, wherein
The plurality of movable rings further include a third movable ring for a third shift stage having a number of stages two or more larger than the first shift stage,
The plurality of plate members further include a third plate member corresponding to the third movable ring,
In the engagement piece, the dog operation is performed when the first movable ring is positioned at the neutral position and the third movable ring is positioned at the in-gear position and the third shift stage is established. A third engagement portion that engages with the third plate member to move the third movable ring to the neutral position when establishing the first gear position by operation of the device;
The first engaging portion and the third engaging portion are configured such that the third movable ring moves to the neutral position before the first movable ring moves to the in-gear position. Gearbox to do. The transmission according to claim 6, wherein
The first engagement portion is more than the timing at which the third engagement portion engages with the engaged portion of the third plate member at the time of shifting from the third shift speed to the first shift speed. It has a notch so as to delay the timing at which the first engaging portion engages with the engaged portion of the first plate member at the time of shifting from the first gear to the second gear. Gearbox to do.

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