JP2017207181A - Speed change gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed change gear capable of reducing stress generated at a guide pin engaging a hub and a movable ring with each other.SOLUTION: A speed change gear 1 comprises: a hub HB1 which rotates integrally with a rotary shaft 12; a movable ring DR1 which is provided at a periphery of the hub HB1 movably in an axial direction, and has dog teeth D1; a speed changing gear 22 which is provided relatively rotatably to the rotary shaft 12, and has dog teeth D3 opposed to the dog teeth D1; and a dog operation device which operates the movable ring DR1 from a neutral position to an in-gear position. The hub HB1 has a guide groove extending in an axial direction on an outer peripheral surface, and the movable ring DR1 has a guide pin in a substantially columnar shape which has one end part inserted into a recessed part provided on an inner peripheral surface rotatably through lubricating oil and also has the other end part engaging the guide groove.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a transmission that establishes a gear position via a dog clutch.

  Conventionally, the clutch ring is supported around the clutch cam ring so as to be movable in the axial direction, and the dog teeth provided on the side surface of the clutch ring and the dog teeth provided on the transmission gear are engaged according to the movement of the clutch ring. There is known a transmission that performs or releases meshing (see, for example, Patent Document 1). In the transmission described in Patent Document 1, a cam protrusion projecting from the inner peripheral surface of the clutch ring is engaged with a cam groove on the outer peripheral surface of the clutch cam ring, and torque of the clutch cam ring is generated via the cam protrusion. While transmitting to the clutch ring, the clutch ring is moved in the axial direction while sliding the cam projection along the cam groove at the time of shifting.

Japanese Patent No. 5707119

  However, in the apparatus described in Patent Document 1, since the cam protrusion on which the torque of the clutch cam ring acts is slid along the cam groove at the time of shifting, the sliding resistance is large and the cam protrusion may be damaged.

  A transmission according to an aspect of the present invention includes a rotating body that rotates about an axis, a movable body that is relatively movable in the axial direction with respect to the rotating body, and that can rotate integrally with the rotating body, and has a first dog tooth. A ring, a speed change gear provided with a second dog tooth facing the first dog tooth and capable of rotating relative to the rotating body; and a first dog from a neutral position where the first dog tooth is separated from the second dog tooth. A dog operating device that operates the movable ring over the in-gear position where the teeth mesh with the second dog teeth, the rotating body has a guide groove extending in the axial direction on the outer peripheral surface, and the movable ring has one end portion. Is inserted into a recess provided in the inner peripheral surface through lubricating oil, and has a substantially cylindrical guide pin with the other end engaged with the guide groove.

  According to the present invention, one end portion of the substantially cylindrical guide pin that engages with the guide groove of the rotating body is rotatably inserted into the concave portion of the movable ring via the lubricating oil, so that the movable ring moves in the axial direction. Sometimes, one end of the guide pin rotates while sliding in the recess, and the other end rolls along the guide groove. For this reason, the stress which generate | occur | produces in a guide pin can be reduced with a simple structure, and damage to a guide pin can be prevented.

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 contained in the transmission of FIG. FIG. 2 is a cross-sectional view of a main part of the transmission showing an assembled state of a first gear coupling mechanism included in the transmission of FIG. 1. Sectional drawing which expands and shows the principal part structure of the 1st gear coupling mechanism cut | disconnected along the IV-IV line | wire of FIG. The figure which shows the positional relationship of a guide groove and a guide pin in case a 1st gear coupling mechanism exists in a neutral state. The figure which shows the transmission path of the torque of the 1st gear coupling mechanism at the time of acceleration driving | running | working. The figure which shows the transmission path of the torque of the 1st gear coupling mechanism at the time of deceleration driving | running | working. The figure which shows the modification of FIG.

  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 a differential 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 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 relatively rotatable with respect to the second main input shaft 12 via bearings (not shown). 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, etc.) 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 via bearings (not shown).

  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 33. 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 a differential gear mechanism (not shown) via the final gear 45.

  The transmission 1 has a plurality of gear coupling mechanisms (dog clutches) that couple the drive gears 21 to 29 to the torque transmission rotary shaft via dog teeth. 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, fixed to the second main input shaft 12, and centered on the axis line CL0. And a movable ring DR1 supported so as to be movable in the axial direction (the arrow AB direction in FIG. 3) along the outer peripheral surface of the hub HB1.

  More specifically, a plurality of substantially cylindrical guide pins 50 in the circumferential direction protrude from the inner peripheral surface of the movable ring DR1 radially inward, and the outer periphery of the hub HB1 corresponds to each guide pin 50. A plurality of substantially V-shaped guide grooves 60 in the circumferential direction are provided on the surface from one axial end surface to the other end surface. The guide pin 50 engages with the guide groove 60, and the guide pin 50 moves in the axial direction (direction of arrow AB in FIG. 3) integrally with the movable ring DR1 while being guided by the guide groove 60. Dog teeth D1 project from the one end surface in the axial direction of the movable ring DR1 at equal intervals in the circumferential direction, and dog teeth D2 project from the other end surface in the axial direction at equal intervals in the circumferential direction.

  The second-speed drive gear 22 has a transmission gear 22a formed on the outer peripheral surface, and dog teeth D3 provided at the end in the axial direction facing the dog teeth D1. More specifically, the second-speed drive gear 22 includes a gear main body 221 having a transmission gear 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. Are integrated. The meshing ring 222 is provided with a plurality of openings 22b in the circumferential direction corresponding to the dog teeth D1 of the movable ring DR1, and the axial end surface of the second speed drive gear 22 (meshing ring 222) is formed in an uneven shape in the circumferential direction. Is done. As a result, the dog tooth D3 is provided at the axial end of the second-speed drive gear 22 so as to face the dog tooth D1.

  The 8-speed drive gear 28 has a transmission gear 28a formed on the outer peripheral surface, and dog teeth D4 provided at the end in the axial direction facing the dog teeth D2. More specifically, the 8-speed drive gear 28 is provided with a plurality of circumferential openings 28b corresponding to the dog teeth D2 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 D4 are provided at the axial ends of the 8-speed drive gear 28 so as to face the dog teeth D2.

  In FIG. 3, the dog teeth D1 and D2 of the movable ring DR1 are not meshed with the dog teeth D3 and D4 of the second speed drive gear 22 and the eighth speed drive gear 28, and the movable ring DR1 is located at 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 D1 mesh with the dog teeth D3, 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. When the movable ring DR1 moves to the in-gear position in the direction of arrow B and the dog tooth D2 meshes with the dog tooth D4, 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.

  The movable ring DR1 is operated by the dog operating device 40 from the neutral position to the in-gear position or from the in-gear position to the neutral position. Although not shown, the dog operating device 40 includes an actuator (such as an electric motor) that drives the movable ring DR1, and the actuator is driven and controlled by a control signal from the controller. For example, the controller calculates the required torque of the vehicle based on the vehicle speed and the amount of depression of the accelerator pedal, and controls the actuator so as to achieve a shift stage according to the required torque.

  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.

  When the fourth speed drive gear 24 is coupled to the second main input shaft 12 via the second gear coupling mechanism 2GE, the rotation of the second main input shaft 12 is transmitted via the fourth speed drive gear 24 and the 3-4 speed driven gear 43. It is transmitted to the output shaft 14 and the fourth gear is established. When the seventh speed drive gear 27 is coupled to the second main input shaft 12 via the second gear coupling mechanism 2GE, the rotation of the second main input shaft 12 is transmitted via the seventh speed drive gear 27 and the 5-7 speed driven gear 44. Transmission to the output shaft 14 establishes the seventh gear.

  When the first speed drive gear 21 is coupled to the sub input shaft 13 via the third gear coupling mechanism 3GE, the rotation of the sub input shaft 13 is transferred to the output shaft 14 via the first speed drive gear 21 and the first and second speed driven gear 41. The first gear is established. When the sixth speed drive gear 26 is coupled to the sub input shaft 13 via the third gear coupling mechanism 3GE, the rotation of the sub input shaft 13 is transferred to the output shaft 14 via the sixth speed drive gear 26 and the 6-8 speed driven gear 42. The 6th speed is established.

  When the third speed drive gear 23 is coupled to the sub input shaft 13 via the fourth gear coupling mechanism 4GE, the rotation of the sub input shaft 13 is transferred to the output shaft 14 via the third speed drive gear 23 and the 3-4 speed driven gear 43. The third gear is established. When the fifth speed drive gear 25 is coupled to the sub input shaft 13 via the fourth gear coupling mechanism 4GE, the rotation of the sub input shaft 13 is transferred to the output shaft 14 via the fifth speed drive gear 25 and the 5-7 speed driven gear 44. Then, the fifth gear is established.

  When the reverse drive gear 29 is coupled to the reverse shaft 15 via the fifth gear coupling mechanism 5GE, 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 drive A stage is established. Although illustration is omitted, when the movable ring DR5 moves to a predetermined position in the axial direction, the parking gear mechanism is activated, the engaging claw of the parking gear mechanism engages with the parking gear 30, and the gear mechanism 10 is locked. The

  As described above, in the present embodiment, the hubs HB1 to HB5 and the movable rings DR1 to DR5 of the gear coupling mechanisms 1GE to 5GE are connected to each other through the guide pins 50 engaged with the guide grooves 60 so that torque can be transmitted. (FIGS. 2 and 3). Hereinafter, this point will be described in detail.

  FIG. 4 is an enlarged cross-sectional view showing the main components of the hub HB1 and the movable ring DR1 of the first gear coupling mechanism 1GE cut along the line IV-IV in FIG. 3, and FIG. It is a figure which shows the positional relationship between the guide groove 60 and the guide pin 50. FIG. In addition, although illustration is abbreviate | omitted, the structure of the guide groove 60 and the guide pin 50 of other gear coupling mechanisms 2GE-5GE is also the same as what was shown in FIG.

  As shown in FIG. 4, a circular bottomed hole 52 is provided in the inner peripheral surface 51 of the movable ring DR <b> 1, and one end of a cylindrical guide pin 50 is inserted into the bottomed hole 52. The diameter D1 of the bottomed hole 52 is larger than the diameter D0 of the guide pin 50 by a predetermined length Δd, and the gap 53 between the bottomed hole 52 and the guide pin 50 is filled with lubricating oil. Instead of press-fitting the guide pin 50 into the bottomed hole 52 in this way, the guide pin 50 is dropped from the bottomed hole 52 by inserting the gap 53 having a predetermined length Δd into the bottomed hole 52. Instead, it is rotatably held in the bottomed hole 52 by the surface tension of the lubricating oil. The predetermined length Δd is set to a value that can form a lubricating oil film in the gap 53, for example, about several hundred μm.

  In FIG. 5, the rotation direction of the hub HB1 during forward traveling and reverse traveling of the vehicle is indicated by arrows F and R, respectively, and the moving direction of the movable ring DR1 along the axial direction is indicated by the arrow AB as in FIG. Show. As shown in FIG. 5, the guide groove 60 of the outer peripheral surface 61 of the hub HB1 has a pair of side surfaces 62 facing each other, that is, a side surface 62a on the arrow R direction side and a side surface 62b on the arrow F direction side.

  The guide groove 60 has a constant length (groove width L1) from one side surface 62a to the other side surface 62b over the entire length in the axial direction (AB direction) of the hub HB1, and the axial length L0 of the hub HB1. It is formed symmetrically with respect to the axis CL1 passing through the middle. An angle θ formed by the pair of side surfaces 62b on both sides of the axis CL1 is smaller than 180 °. The groove width L1 is larger than the diameter D0 of the guide pin 50 and further larger than the diameter D1 of the bottomed hole 52 (see FIG. 4). Therefore, a gap 63 larger than the gap 53 is formed between the guide groove 60 and the guide pin 50.

  As shown in FIG. 4, when the hub HB1 rotates in the direction of arrow A, torque acts on the movable ring DR1 via the guide pin 50, and the movable ring DR1 rotates with the hub HB1. At this time, a pressing force F1 acts on the guide pin 50 from the side surface 62a of the guide groove 60, and a pressing force F2 acts on the peripheral surface of the bottomed hole 52 from the guide pin 50. FIG. 4 shows the directions of the pressing forces F1 and F2 during acceleration traveling. Since torque acts on the hub HB1 from the movable ring DR1 during deceleration traveling, the directions of the pressing forces F1 and F2 are opposite.

  The pressing forces F1 and F2 act on the contact surface S1 between the guide pin 50 and the guide groove 60 and the contact surface S2 between the guide pin 50 and the bottomed hole 52, respectively. The distance R1 from the axis CL0, which is the center of rotation of the hub HB1, to the radial intermediate position of the contact surface S1 is shorter than the distance R2 from the axis CL0 to the radial intermediate position of the contact surface S2 (R1 <R2). For this reason, since the torques acting on the contact surfaces S1 and S2 are equal to each other (R1 · F1 = R2 · F2), the pressing force F2 is smaller than the pressing force F1 (F1> F2).

  Accordingly, assuming that the friction coefficient μ1 between the guide pin 50 and the guide groove 60 on the contact surface S1 and the friction coefficient μ2 between the guide pin 50 and the bottomed hole 52 on the contact surface S2 are equal to each other, The frictional force (μ1 · F1) is larger than the frictional force (μ2 · F2) on the contact surface S2. Thereby, when the guide pin 50 moves along the guide groove 60 in the direction of the arrow AB in FIG. 5, one end portion of the guide pin 50 is easy to roll on the contact surface S1 having a large frictional force and the contact surface S2 having a small frictional force. The other end of the guide pin 50 is easy to slide.

  As described above, one end of the guide pin 50 moves along the guide groove 60 while rolling without sliding on the side surface 62 of the guide groove 60, and the entire outer periphery of the guide pin 50 sequentially becomes the contact surface S1. Thereby, the stress of the one end part of the guide pin 50 can be reduced compared with the case where the guide pin 50 is slid without rolling. At this time, the other end of the guide pin 50 rotates while sliding in the bottomed hole 52. For this reason, the guide pin 50 is in a fluid lubrication state and contacts the peripheral surface of the bottomed hole 52 through the lubricating oil. As a result, the slidability of the guide pin 50 is improved, and the stress at the other end of the guide pin 50 can be reduced.

  FIGS. 6 and 7 show the state of the torque in the state where the movable ring DR1 of the first gear coupling mechanism 1GE is moved in the direction of arrow A by the operation of the dog operating device 40, that is, in the acceleration traveling and the deceleration traveling in the second gear. It is a figure which shows a transmission path | route. Although illustration is omitted, torque transmission paths at other speed stages are the same as in FIGS.

  During acceleration traveling, the rotation of the hub HB1 is faster than the rotation of the movable ring DR1. For this reason, as shown in FIG. 6, the side surface 62 a of the guide groove 60 of the hub HB <b> 1 contacts the guide pin 50. As a result, a pressing force F1 in the acceleration direction (arrow F direction) acts on the guide pin 50 at the contact portion 50a, and an acceleration torque Ta acts on the second-speed drive gear 22 (dog teeth D2b) by this pressing force F1. At this time, since the side surface 62a of the guide groove 60 is inclined with respect to the axial direction, the force Fa in the direction of arrow A perpendicular to the pressing force F1, that is, the second speed drive gear 22 and the movable ring DR1 is applied to the guide pin 50. A force (engagement promoting force) that promotes the engagement is applied.

  On the other hand, during deceleration travel, the rotation of the hub HB1 is slower than the rotation of the movable ring DR1, and as shown in FIG. 7, the deceleration torque Tb acts on the movable ring DR1 from the second speed drive gear 22. Therefore, the side surface 62b of the guide groove 60 of the hub HB1 contacts the guide pin 50, and a pressing force F3 in the deceleration direction (arrow R direction) acts on the guide pin 50 at the contact portion 50b. At this time, since the side surface 62b of the guide groove 60 is inclined with respect to the axial direction, the guide pin 50 has a force Fb in the direction of arrow B perpendicular to the pressing force F3, that is, the second speed drive gear 22 and the movable ring DR1. A force (mesh release force) that releases the mesh is applied.

  In the present embodiment, the dog operating device 40 operates the movable ring so that the lower gear and the upper gear mesh at the same time during the upshift. For example, at the time of upshifting from the second gear to the third gear, the fourth gear coupling mechanism 4GE is further moved with the second speed drive gear 22 coupled to the second main input shaft 12 via the first gear coupling mechanism 1GE. The third speed drive gear 23 is coupled to the sub input shaft 13 via the first input gear 13.

  In this case, the rotation of the hub HB1 of the first gear coupling mechanism 1GE is slower than the rotation of the movable ring DR1 (second speed drive gear 22). 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 (third speed drive gear 23). For this reason, the 2nd speed drive gear 22 will be in the deceleration state of FIG. 7, and the 3rd speed drive gear 23 will be in the acceleration state of FIG. Therefore, when the second speed drive gear 22 and the third speed drive gear 23 are simultaneously meshed with the movable rings DR1 and DR4, respectively, during the upshift, a part of the output torque circulates through the output shaft 14 in the second speed drive gear 22. Acts as torque.

  Due to this circulating torque, the mesh release force Fb (FIG. 7) acts on the guide pin 50 of the first gear coupling mechanism 1GE, and the movable ring DR1 moves in the direction of arrow B (mesh release direction) in FIG. As a result, the meshing between the dog tooth D2a of the movable ring DR1 and the dog tooth D2b of the second-speed drive gear 22 is released, and the first gear coupling mechanism 1GE is in a neutral state. At this time, the engagement promoting force Fa (FIG. 6) acts on the guide pin 50 of the fourth gear coupling mechanism 4GE, and the movable ring DR4 is pressed toward the third speed drive gear 23 side. As a result, the dog teeth D3a of the movable ring DR4 and the dog teeth D3b of the third-speed drive gear 23 remain engaged with each other, and the fourth gear coupling mechanism 4GE enters the gear coupled state.

  Thus, by shifting while partially engaging some of the drive gears (for example, the second speed drive gear 22 and the third speed drive gear 23), a smooth upshift can be achieved without torque loss. At the time of downshift, after returning the movable ring of the gear coupling mechanism corresponding to the upper gear stage in the coupled state to the neutral position, the gear coupling mechanism corresponding to the lower gear stage is set to the gear coupled state. The dog operating device 40 operates the movable rings DR1 to DR5.

According to the embodiment of the present invention, the following effects can be obtained.
(1) The transmission 1 is hubs HB1 to HB5 that rotate about the axis line CL0, and can move relative to the hubs HB1 to HB5 in the axial direction around the hubs HB1 to HB5 and rotate integrally with the hubs HB1 to HB5. A movable gear DR1 to DR5 having dog teeth D1 and D2 and a drive gear 21 having dog teeth D3 and D4 provided to be rotatable relative to the hubs HB1 to HB5 and facing the dog teeth D1 and D2. Dog operation device 40 for operating the movable rings DR1 to DR5 from the neutral position where the dog teeth D1 and D2 are separated from the dog teeth D3 and D4 to the in-gear position where the dog teeth D1 and D2 mesh with the dog teeth D3 and D4. (FIGS. 1 and 3). The hubs HB1 to HB5 have guide grooves 60 extending in the axial direction on the outer peripheral surface 61, and the movable rings DR1 to DR5 are provided with lubricating oil in a bottomed hole 52 provided at one end portion on the inner peripheral surface 51. And a guide pin 50 having a substantially cylindrical shape with the other end engaged with the guide groove 60 (FIGS. 4 and 5).

  Thus, by inserting the guide pin 50 into the bottomed hole 52 of the inner peripheral surface 51 of the movable rings DR1 to DR5 via the lubricating oil so as to be rotatable, the guide pin is moved when the movable rings DR1 to DR5 are moved in the axial direction. One end of 50 rotates while sliding in the bottomed hole 52, and the other end rolls along the guide groove 60. For this reason, for example, the stress generated in the guide pin 50 can be reduced as compared with the case where the guide pin 50 is non-rotatably pressed into the inner peripheral surface 51 of the movable rings DR1 to DR5 and is slid along the guide groove 60. It is possible to prevent the guide pin 50 from being damaged with a simple configuration. In addition, in order to improve the slidability with the guide groove 60 in the contact surface S1 of the guide pin 50, attaching a bush to the one end part of the guide pin 50 is also considered. However, in this case, not only the number of parts increases, but also the bush may be damaged by the pressing force F1 (FIG. 4).

(2) The gap 53 between the guide pin 50 and the bottomed hole 52 is set so as to be rotatably held in the bottomed hole 52 by the surface tension of the lubricating oil (FIG. 4). Accordingly, the guide pin 50 can be easily rotatably held in the bottomed hole 52 simply by inserting the end of the guide pin 50 into the bottomed hole 52 filled with the lubricating oil.

(3) The gap 53 between the guide pin 50 and the bottomed hole 52 is smaller than the gap 63 between the guide pin 50 and the guide groove 60. In other words, the diameter D1 of the bottomed hole 52 is smaller than the groove width L1 of the guide groove 60 (FIG. 4). As a result, the guide pin 50 abuts only on one side surface 62 a or 62 b of the guide groove 60, and the guide pin 50 can easily roll on the side surface 62.

(4) The guide groove 60 has an approximately V shape that is inclined with respect to the axial direction and symmetrical with respect to the axial direction (FIG. 5). By forming the guide groove 60 in this way, for example, when the lower transmission gear and the upper transmission gear are simultaneously meshed during upshifting, the movable ring of any gear coupling mechanism corresponding to the lower transmission gear is used. DR1 to DR5 can be moved to the neutral position by the circulating torque via the output shaft 14. In this case, an excessive mesh release force Fb acts on the guide pin 50, but as described above, the guide pin 50 is rotated through the bottomed hole 52 of the inner peripheral surface 51 of the movable rings DR1 to DR5 via the lubricating oil. By inserting the guide pin 50 as possible, the guide pin 50 rolls on the side surface 62 of the guide groove 60, and the stress generated in the guide pin 50 can be reduced.

(5) The movable rings DR1 to DR9 move relative to the hubs HB1 to HB5 in the axial direction around the hubs HB1 to HB5 that rotate integrally with the rotation shafts (second input shaft 12, output shaft 14, and reverse shaft 15). The guide groove 60 is provided on the outer peripheral surface 61 of the hubs HB1 to HB5 (FIGS. 4 and 5). By supporting the movable rings DR1 to DR9 via the hubs HB1 to HB5 in this way, the movable rings DR1 to DR5 can be configured to be relatively movable in the axial direction with respect to the rotation axis and to be rotatable integrally with the rotation axis. it can.

  In the above embodiment, the engine 2 and the electric motor 3 are connected to the gear mechanism 10 of the transmission 1 via the clutch mechanism C. However, for example, the electric motor 3 may be omitted, and the configuration of the transmission 1 Is not limited to those described above. FIG. 8 is a diagram showing a modification of FIG. In the transmission 1A of FIG. 8, the electric motor 3 is omitted, and the torque of the engine 2 is input to the input shaft 12A through the single clutch C. Around the input shaft 12A, a 5-speed drive gear 25A, a 2-speed drive gear 22A, a 6-speed drive gear 26A, and a 3-speed drive gear 23A are arranged in this order so as to be rotatable relative to the input shaft 12A. Further, gears 34 and 35 are arranged on the side of the third speed drive gear 23A and fixed to the input shaft 12A.

  The output shaft 14A meshes with a gear 46 meshed with the fifth speed drive gear 25A, a gear 47 meshed with the second speed drive gear 22A, a gear 48 meshed with the sixth speed drive gear 26A, and a third speed drive gear 23A. The gear 49 and the final gear 45A are fixed. Around the output shaft 14A, a 4-speed drive gear 24A and a 1-speed drive gear 21A are disposed between the gear 49 and the final gear 45 so as to be rotatable relative to the output shaft 14A, respectively. And the first-speed drive gear 21A are engaged with gears 34 and 35, respectively. In FIG. 8, the illustration of the reverse drive gear is omitted.

  A gear coupling mechanism 6GE is provided between the second speed driving gear 22A and the sixth speed driving gear 26A, and a gear coupling mechanism 7GE is provided between the third speed driving gear 23A and the sixth speed driving gear 26A. A gear coupling mechanism 8GE is provided between the drive gear 21A and the fourth speed drive gear 24A. The gear coupling mechanism is configured in the same manner as the first gear coupling mechanism to the fifth gear coupling mechanism described above, and a hub fixed to the rotation shaft (input shaft 12A, output shaft 21A) and an outer peripheral surface of the hub. And a movable ring relatively movable in the axial direction. One of the second speed drive gear 22A and the fifth speed drive gear 25A can be coupled to the input shaft 12A via the gear coupling mechanism 6GE, and one of the third speed drive gear 23A and the sixth speed drive gear 26A is coupled via the gear coupling mechanism 7GE. The first speed drive gear 21A and the fourth speed drive gear 24A can be coupled to the output shaft 14A via the gear coupling mechanism 8GE. As a result, one of the first to sixth gears is established.

  In the above embodiment, the rotating shafts 12, 13, 15 as the rotating bodies and the hubs HB1 to HB5 are configured as separate bodies. However, a part of the outer peripheral surface of the rotating shafts 12, 13, 15 is, for example, the hubs HB1 to HB5. They may be configured in the same shape, and the guide groove 60 may be provided on the rotating shaft itself. Therefore, the rotating body having the movable rings DR1 to DR5 around it may be a rotating shaft, and the hub may be omitted. In the above embodiment, the dog teeth D1 and D2 are projected as the first dog teeth on the axial end faces of the movable rings DR1 to DR5 that are movable in the axial direction. Not exclusively. Therefore, the configuration of the dog teeth D3 and D4 of the drive gears 21 to 29 (transmission gear) corresponding to the dog teeth D1 and D2 of the movable rings DR1 to DR5 provided so as to be rotatable relative to the rotation shaft, that is, the second dog The configuration of the teeth is not limited to that described above. That is, the configuration of the dog clutch is not limited to that described above. For example, the inner peripheral surface of the movable ring and the outer peripheral surface of the transmission gear are configured to face each other, and the first dog is respectively provided on the inner peripheral surface and the outer peripheral surface. Teeth and second dog teeth may be formed.

  In the above embodiment, the drive gears 21 to 29 of the eighth forward speed and the first reverse speed are provided as the gears for shifting, but the number of gears for shifting is not limited to this. The transmission 1 may be a manual transmission instead of an automatic transmission. As long as the movable rings DR1 to DR5 are operated from the neutral position to the in-gear position, the dog operation device 40 may be any device. For example, the driver himself inputs the target gear position to the dog operation device 40, and according to the target gear position. You may make it operate movable ring DR1-DR5.

  In the above embodiment, the V-shaped guide groove 60 is formed on the outer peripheral surface of the hubs HB1 to HB5 as the guide groove extending in the axial direction. However, the shape of the guide groove is not limited to this, for example, a straight guide It may be a groove. In the above embodiment, the substantially cylindrical guide pin 50 is rotatably inserted into the bottomed hole 52 of the inner peripheral surface 51 of the movable rings DR1 to DR5 via the lubricating oil, but the configuration of the recess into which the guide pin is inserted. Is not limited to this. In the above embodiment, the diameter D1 of the bottomed hole 52 is smaller than the groove width L1 of the guide groove 60, but the magnitude relationship between D1 and L1 is not limited thereto.

  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.

1, 1A Transmission, 12 Second main input shaft, 13 Sub input shaft, 21 to 29 Drive gear, 40 Dog operating device, 50 Guide pin, 52 Bottomed hole, 53 Clearance, 60 Guide groove, 63 Clearance, 1GE 8GE gear coupling mechanism, D1-D4 dog teeth, DR1-DR5 movable ring, HB1-HB5 hub

Claims (5)

A rotating body that rotates about an axis;
A movable ring having a first dog tooth provided around the rotating body so as to be movable relative to the rotating body in the axial direction and rotatable integrally with the rotating body;
A transmission gear provided so as to be relatively rotatable with respect to the rotating body, and having a second dog tooth facing the first dog tooth;
A dog operating device that operates the movable ring from a neutral position where the first dog teeth are separated from the second dog teeth to an in-gear position where the first dog teeth mesh with the second dog teeth;
The rotating body has a guide groove extending in the axial direction on the outer peripheral surface,
The movable ring has a substantially cylindrical guide pin whose one end is rotatably inserted into a recess provided on the inner peripheral surface via lubricating oil, and the other end engages with the guide groove. A transmission characterized by. The transmission according to claim 1, wherein
The transmission is characterized in that a gap between the guide pin and the recess is set to be rotatably held in the recess by a surface tension of the lubricating oil. The transmission according to claim 1 or 2,
A transmission characterized in that a gap between the guide pin and the recess is smaller than a gap between the guide pin and the guide groove. The transmission according to any one of claims 1 to 3,
The transmission is characterized in that the guide groove is inclined with respect to the axial direction and has a substantially V-shape that is symmetrical in the axial direction. The transmission according to any one of claims 1 to 4,
The rotating body is a hub that rotates integrally with a rotating shaft,
The movable ring is provided around the hub so as to be axially movable relative to the hub and rotatable integrally with the hub.
The transmission is characterized in that the guide groove is provided on an outer peripheral surface of the hub.

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