JP2017155777A - Power transmission device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To combine reduction of vibration/noise and improvement of shift responsiveness, in a power transmission device for a vehicle in which a plurality of crank-type transmission units are axially arranged in parallel.SOLUTION: An eccentric cam 18 includes supporting walls 18c holding a side wall 19c of an eccentric member 19 from axial both sides, friction members 44 are respectively disposed between the supporting wall 18c and the side wall 19c, and a V-shaped groove 43a is formed on a side face of the side wall 19c or a side face of the friction member 44 opposed to the side wall 19c. Vibration and noise easily generate when the eccentric member 19 rotates in a direction to increase an eccentric amount and receives inertia force, but as the groove 43a acts to increase frictional force at that time, the eccentric member 19 is strongly constrained and generation of vibration and noise can be suppressed. On the contrary, when the eccentric member 19 rotates in a direction to reduce the eccentric amount at the time of a kick-down operation and the like, increase of shift responsiveness is required, but as the groove 43a acts to reduce the frictional force at that time, the eccentric member 19 can quickly rotate and the shift responsiveness can be increased.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a vehicle power transmission device in which a plurality of crank-type transmission units that transmit driving force from an input shaft to an output shaft via a connecting rod that reciprocates and a one-way clutch are juxtaposed in the axial direction.

  In such a crank transmission unit of the vehicle power transmission device, the input shaft is bent by sandwiching a washer in the clearance between the eccentric cam and the eccentric disk (eccentric member) that rotate relative to each other when changing the gear ratio. Patent Document 1 below discloses that the eccentric cam and the eccentric disk come into contact with each other when the clearance fluctuates to prevent vibration and noise.

JP 2014-185653 A

  By the way, when the eccentric cam and the eccentric disk of the crank-type transmission unit rotate relative to each other, the washer sandwiched between them slides relative to the eccentric cam and the eccentric disk. No consideration is given to the frictional resistance that the eccentric cam and the eccentric disk receive by sliding. However, if the frictional force is changed in accordance with the direction in which the transmission ratio increases and decreases, that is, in the direction in which the eccentric cam and the eccentric disk rotate relative to each other, there is a possibility that it can contribute to improving the performance of the transmission unit. is there.

  The present invention has been made in view of the above circumstances, and in a vehicle power transmission device in which a plurality of crank-type transmission units are juxtaposed in the axial direction, both reduction of vibration and noise and improvement of shift response are achieved. With the goal.

  In order to achieve the above object, according to the first aspect of the present invention, a plurality of transmission units for shifting the rotation of the input shaft connected to the drive source and transmitting it to the output shaft are juxtaposed in the axial direction. Each of the transmission units is disposed coaxially with the input shaft, an eccentric cam that rotates integrally with the input shaft, an eccentric member formed with a ring gear that fits on the outer periphery of the eccentric cam so as to be relatively rotatable. A reciprocating motion connected to a transmission shaft rotated by a transmission actuator, a pinion provided on the transmission shaft and meshing with the ring gear, a one-way clutch provided on the output shaft, an eccentric member, and an outer member of the one-way clutch A connecting rod for rotating the shift shaft relative to the input shaft by the shift actuator, and the eccentric portion with respect to the eccentric cam. The power transmission device for a vehicle changes the gear ratio by changing the amount of eccentricity of the eccentric member from the axis of the input shaft by changing the phase of the input shaft, and the eccentric cam pivots on the side wall of the eccentric member. A pair of support walls sandwiched from both sides in the direction, a friction member is disposed between at least one of the pair of support walls and the side wall, and a V-shape is provided on the side surface of the side wall or the side surface of the friction member facing the side wall. Or a U-shaped groove is formed, and when the eccentric member rotates in a direction to increase the amount of eccentricity, the frictional force increases, and when the eccentric member rotates in a direction to decrease the amount of eccentricity. A vehicular power transmission device is proposed which is arranged in a direction in which the frictional force is reduced.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the groove is also formed on a side surface of the friction member facing the support wall. A device is proposed.

  The eccentric disk 19 of the embodiment corresponds to the eccentric member of the present invention, and the engine E of the embodiment corresponds to the drive source of the present invention.

  According to the configuration of claim 1, the transmission unit connects the eccentric member supported by the eccentric cam provided on the input shaft and rotating together with the input shaft, and the outer member of the one-way clutch provided on the output shaft by the connecting rod. Therefore, when the input shaft rotates and the connecting rod reciprocates, the one-way clutch is intermittently engaged, whereby the output shaft rotates intermittently and the driving force is transmitted. At this time, the amount of eccentricity of the eccentric member from the axis of the input shaft is changed by rotating the transmission shaft relative to the input shaft with the speed change actuator and rotating the ring gear with the pinion to change the phase of the eccentric member with respect to the eccentric cam. Can be changed to change the gear ratio.

  The eccentric cam includes a pair of support walls sandwiching the side wall of the eccentric member from both sides in the axial direction, and a friction member is disposed between at least one of the pair of support walls and the side wall, and the side surface of the side wall or the friction member facing the side wall is provided. A V-shaped or U-shaped groove is formed on the side surface. Even if the eccentric member receives an inertial force when rotating in the direction of increasing the eccentricity, the groove acts to increase the frictional force at that time, so the eccentric member is strongly restrained to generate vibration and noise. Can be suppressed. Conversely, when the eccentric member rotates in a direction to reduce the eccentric amount, such as during kickdown, it is desirable to increase the shift response, but since the groove acts to reduce the frictional force at that time, the eccentric member is The speed change responsiveness can be improved by quickly rotating.

  According to the second aspect of the present invention, since the groove is also formed on the side surface of the friction member facing the support wall, not only the side surface of the side wall and the side surface of the friction member but also the side surface of the support wall and the side surface of the friction member. Grooves are also interposed between them, and the total frictional force increases accordingly, and the eccentric member is more strongly restrained, and the generation of vibration and noise can be more effectively suppressed.

The longitudinal cross-sectional view of the power transmission device for vehicles. FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. The front view and sectional drawing of an eccentric disk. The figure which shows the relationship between the eccentric amount of an eccentric disk, and a gear ratio. FIG. 5 is an enlarged view of part 5 of FIG. 1. The exploded perspective view of a friction member. The exploded perspective view of an eccentric cam, an eccentric disk, and a friction member. The graph explaining the torque which acts on a transmission shaft.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 3, an input shaft 12 and an output shaft 13 are supported in parallel with each other on a pair of side walls 11a and 11b of a transmission case 11 of a crank type continuously variable transmission T for an automobile. The rotation of the input shaft 12 connected to the engine E is transmitted to drive wheels (not shown) via the six transmission units 14, the output shaft 13 and a differential gear (not shown). A variable speed shaft 15 sharing an axis L with the input shaft 12 is fitted into the hollow formed input shaft 12 via seven needle bearings 16 so as to be relatively rotatable.

  Since the structure of the six transmission units 14 is substantially the same, the structure will be described below with one transmission unit 14 as a representative.

  The transmission unit 14 includes a pinion 17 provided on the outer peripheral surface of the transmission shaft 15, and the pinion 17 is exposed from an opening 12 a (see FIG. 2) formed in the input shaft 12. A disc-shaped eccentric cam 18 divided into two in the direction of the axis L is splined to the outer periphery of the input shaft 12 so as to sandwich the pinion 17. The center O1 of the eccentric cam 18 is eccentric with respect to the axis L of the input shaft 12 by a distance d. In addition, the six eccentric cams 18 of the six transmission units 14 are offset in phase by 60 ° from each other.

  On the outer peripheral surface of the eccentric cam 18, a pair of eccentric recesses 19 a and 19 a formed on both end surfaces in the axis L direction of the disc-shaped eccentric disk 19 are rotatably supported via a pair of needle bearings 20 and 20. . The center O1 of the eccentric recesses 19a, 19a (that is, the center O1 of the eccentric cam 18) is shifted from the center O2 of the eccentric disk 19 by a distance d. That is, the distance d between the axis L of the input shaft 12 and the center O1 of the eccentric cam 18 and the distance d between the center O1 of the eccentric cam 18 and the center O2 of the eccentric disk 19 are the same.

  A pair of crescent-shaped guide portions 18 a and 18 a are provided coaxially with the center O 1 of the eccentric cam 18 on the outer periphery of the split surface of the eccentric cam 18 divided into two in the axis L direction. The tooth tips of the ring gear 19b formed so as to communicate between the bottoms of the eccentric recesses 19a and 19a slidably contact the outer peripheral surfaces of the guide portions 18a and 18a of the eccentric cam 18. Then, the pinion 17 of the transmission shaft 15 meshes with the ring gear 19b of the eccentric disk 19 through the opening 12a of the input shaft 12.

  The right end side of the input shaft 12 is directly supported by the right side wall 11 a of the mission case 11 via a ball bearing 21. A cylindrical portion 18b (see FIG. 1) provided integrally with one eccentric cam 18 located on the left end side of the input shaft 12 is supported on the left side wall 11b of the mission case 11 via a ball bearing 22. The left end side of the input shaft 12 splined to the inner periphery of the eccentric cam 18 is indirectly supported by the transmission case 11.

  The speed change actuator 23 that changes the speed ratio of the continuously variable transmission T by rotating the speed change shaft 15 relative to the input shaft 12 is supported by the transmission case 11 so that the motor shaft 24a is coaxial with the axis L. A motor 24 and a planetary gear mechanism 25 connected to the electric motor 24 are provided. The planetary gear mechanism 25 includes a carrier 27 that is rotatably supported by an electric motor 24 via a needle bearing 26, a sun gear 28 that is fixed to the motor shaft 24a, and a plurality of two stations that are rotatably supported by the carrier 27. A pinion 29, a first ring gear 30 splined to the shaft end of the hollow input shaft 12 (strictly speaking, the cylindrical portion 18b of the one eccentric cam 18), and a spline to the shaft end of the transmission shaft 15 And a second ring gear 31 coupled thereto. Each double pinion 29 includes a first pinion 29a having a large diameter and a second pinion 29b having a small diameter. The first pinion 29a meshes with the sun gear 28 and the first ring gear 30, and the second pinion 29b has a second ring gear. Mesh with 31.

  The connecting rod 33 includes a large end portion 33 a, a rod portion 33 b, and a small end portion 33 c, and the large end portion 33 a is supported on the outer periphery of the eccentric disk 19 via the roller bearing 32.

  The output shaft 13 is supported on a pair of side walls 11a and 11b of the mission case 11 by a pair of ball bearings 34 and 35, and a one-way clutch 36 is provided on the outer periphery thereof. The one-way clutch 36 includes a swing link 42 pivotally supported by a small end 33c of the connecting rod 33 via a pin 37, a ring-shaped outer member 38 fixed to the inner periphery of the swing link 42, an outer member A ring-shaped inner member 39 disposed inside the shaft 38 and fixed to the output shaft 13, and a wedge-shaped space formed between the inner peripheral surface of the outer member 38 and the outer peripheral surface of the inner member 39. And a plurality of rollers 41 urged by a plurality of springs 40.

  As shown in FIGS. 5 and 6, a pair of support walls 18c, 18c extending outward in the radial direction is formed on the outer circumferences of the eccentric cams 18, 18, and a pair of second support walls 18c, 18c are paired with each other. A pair of side walls 19c and 19c of the needle bearings 20 and 20 and the eccentric disk 19 are clamped. Between the pair of support walls 18c, 18c of the eccentric cams 18, 18 and the pair of side walls 19c, 19c of the eccentric disk 19, a clearance in the direction of the axis L for allowing relative rotation of the eccentric cams 18, 18 and the eccentric disk 19 In this clearance, a friction member 44 having a three-layer structure in which metal second washers 43 and 43 are superimposed on both sides of the rubber first washer 42 is disposed.

  On the outer surface of the second washers 43, 43, that is, the surface facing the support wall 18c of the eccentric cam 18 and the side wall 19c of the eccentric disk 19, a large number of V-shaped grooves 43a are formed along the circumferential direction. . The direction in which the sharp tips of the V-shaped grooves 43a are directed is clockwise in the embodiment shown in FIG. Therefore, when the friction member 44 is viewed from one direction, the V-shaped groove 43a of the second washer 43 on the near side (clockwise direction) and the V-shaped groove 43a of the second washer 43 on the far side are located. The directions of ... (counterclockwise) are opposite to each other.

  Next, the operation of one transmission unit 14 of the continuously variable transmission T will be described.

  As is clear from FIGS. 2 and 4A to 4D, when the center O2 of the eccentric disk 19 is eccentric with respect to the axis L of the input shaft 12, the input shaft 12 is rotated by the engine E. When the large end portion 33a of the connecting rod 33 rotates eccentrically around the axis L, the connecting rod 33 reciprocates.

  As a result, when the connecting rod 33 is reciprocated and pushed to the right in the figure, the outer member 38 swings counterclockwise in FIG. 2 together with the swing link 42 and the roller 41 urged by the springs 40. .. Bite into a wedge-shaped space between the outer member 38 and the inner member 39, and the outer member 38 and the inner member 39 are coupled via rollers 41, so that the one-way clutch 36 is engaged and the connecting rod 33 The movement is transmitted to the output shaft 13. On the contrary, when the connecting rod 33 is reciprocated and pulled to the left in the figure, the outer member 38 swings clockwise in FIG. 2 together with the swing link 42, and the roller 41. When the outer member 38 and the inner member 39 are pushed out of the wedge-shaped space between the member 38 and the inner member 39 and slip, the one-way clutch 36 is disengaged and the movement of the connecting rod 33 is transmitted to the output shaft 13. It will not be done.

  Thus, since the rotation of the input shaft 12 is transmitted to the output shaft 13 for a predetermined time while the input shaft 12 rotates once, the output shaft 13 rotates intermittently when the input shaft 12 rotates continuously. The eccentric amounts ε of the eccentric disks 19 of the six transmission units 14 are all the same, but the phases in the eccentric direction are shifted by 60 ° from each other, so that the six transmission units 14 of the input shaft 12 By alternately transmitting the rotation to the output shaft 13, the output shaft 13 rotates continuously.

  At this time, as the eccentric amount ε of the eccentric disk 19 increases, the reciprocating stroke of the connecting rod 33 increases, and the one-time rotation angle of the output shaft 13 increases, and the transmission ratio of the continuously variable transmission T decreases. Conversely, the smaller the eccentric amount ε of the eccentric disk 19, the smaller the reciprocating stroke of the connecting rod 33, the smaller the rotation angle of the output shaft 13, and the higher the gear ratio of the continuously variable transmission T. When the eccentric amount ε of the eccentric disk 19 becomes zero, the connecting rod 33 stops moving even when the input shaft 12 rotates, so the output shaft 13 does not rotate, and the gear ratio of the continuously variable transmission T is maximized ( Infinity).

  When the transmission shaft 15 does not rotate relative to the input shaft 12, that is, when the input shaft 12 and the transmission shaft 15 rotate at the same speed, the transmission ratio of the continuously variable transmission T is maintained constant. In order to rotate the input shaft 12 and the transmission shaft 15 at the same speed, the electric motor 24 may be rotationally driven at the same speed as the input shaft 12. The reason is that the first ring gear 30 of the planetary gear mechanism 25 is connected to the input shaft 12 and rotates at the same speed as the input shaft 12. When the electric motor 24 is driven at the same speed, the sun gear 28 and the first ring gear 30 are driven. Rotate at the same speed, the planetary gear mechanism 25 is locked and rotates as a whole. As a result, the input shaft 12 and the transmission shaft 15 connected to the first ring gear 30 and the second ring gear 31 that rotate integrally are integrated and rotate at the same speed without relative rotation.

  When the rotational speed of the electric motor 24 is increased or decreased with respect to the rotational speed of the input shaft 12, the first ring gear 30 coupled to the input shaft 12 and the sun gear 28 connected to the electric motor 24 rotate relative to each other. The carrier 27 rotates relative to the first ring gear 30. At this time, the gear ratio of the first ring gear 30 and the first pinion 29a meshing with each other is slightly different from the gear ratio of the second ring gear 31 and the second pinion 29b meshing with each other. And the transmission shaft 15 connected to the second ring gear 31 rotate relative to each other.

  When the transmission shaft 15 rotates relative to the input shaft 12 in this manner, the eccentric recesses 19 a and 19 a of the eccentric disk 19 in which the ring gear 19 b is engaged with the pinion 17 of each transmission unit 14 are integrated with the input shaft 12. The cam 18 rotates while being guided by the guide portions 18a, 18a, and the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 changes.

  FIG. 4A shows a state where the speed ratio is minimum (speed ratio: TD). At this time, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the axis L of the input shaft 12. To a center O1 of the eccentric cam 18 and a maximum value equal to 2d, which is the sum of the distance d from the center O1 of the eccentric cam 18 to the center O2 of the eccentric disk 19. When the transmission shaft 15 rotates relative to the input shaft 12, the eccentric disk 19 rotates relative to the eccentric cam 18 integral with the input shaft 12, as shown in FIGS. 4B and 4C. Furthermore, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is gradually decreased from the maximum value 2d, and the transmission ratio is increased. When the transmission shaft 15 further rotates relative to the input shaft 12, the eccentric disk 19 further rotates relative to the eccentric cam 18 integral with the input shaft 12, and finally, as shown in FIG. The center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentricity ε becomes zero, the transmission gear ratio is maximized (infinite) (transmission ratio: UD), and power is transmitted to the output shaft 13. Blocked.

  FIG. 8 shows changes in torque acting on the transmission shaft 15, where the solid line indicates the torque due to the driving force transmitted from the input shaft 12 to the output shaft 13, and the alternate long and short dash line indicates the inertial force transmitted from the one-way clutch 36. The two-dot chain line indicates the torque due to the inertial force transmitted from the connecting rod 33, the broken line indicates the torque due to the inertial force (centrifugal force) transmitted from the eccentric disk 19, and the dotted line indicates all these torques. The total torque is shown. The region on the upper side of the horizontal axis is a region where torque in the direction of decreasing the eccentric amount ε of the eccentric disk 19 acts on the transmission shaft 15, and the region on the lower side of the horizontal axis increases the amount of eccentricity ε of the eccentric disk 19. This is a region where torque in the direction to be applied acts on the transmission shaft 15.

  When the connecting rod 33 that reciprocates by the eccentric disk 19 that rotates eccentrically integrally with the input shaft 12 pushes the swing link 42 and the one-way clutch 36 is engaged and the output shaft 13 is driven, the eccentric disk 19 is connected to the connecting rod 33. The reaction force in the direction of being pushed back from the output shaft 13 is received through 33, and this reaction force is transmitted to the transmission shaft 15 through the pinion 17 meshing with the ring gear 19 b of the eccentric disk 19, and the eccentric amount ε is transmitted to the transmission shaft 15. Is applied (refer to the torque by the driving force indicated by the solid line in FIG. 8).

  On the other hand, for example, an inertial force (centrifugal force) acting on the eccentric disk 19 urges the eccentric disk 19 outward in the radial direction, and this inertial force applies a torque in a direction that increases the eccentricity ε to the transmission shaft 15 ( (Refer to the torque by the centrifugal force shown by the broken line in FIG. 8). Similarly, both the inertial force of the one-way clutch 36 and the inertial force of the connecting rod 33 apply torque in a direction that increases the eccentricity ε to the transmission shaft 15 (see the one-dot chain line and the two-dot chain line in FIG. 8).

  As a result, the total torque obtained by adding these torques crosses the horizontal axis as shown by the dotted line in FIG. 8, and the direction of the torque applied to the transmission shaft 15 increases the eccentric amount ε and decreases the eccentric amount ε. In this case, rattling noise is generated between the ring gear 19b of the eccentric disk 19 and the pinion 17 of the transmission shaft 15.

  According to the present embodiment, the friction member 44 applies a frictional force to the eccentric disk 19 to suppress the radially outward movement, and prevents the transmission shaft 15 from being applied with a torque in a direction that increases the eccentricity ε. Thus, the total torque applied to the transmission shaft 15 can be moved to the upper region of the horizontal axis, and rattling noise that occurs when straddling the horizontal axis can be prevented.

  In FIG. 7, it is assumed that the eccentric cam 18 and the eccentric disk 19 rotate relative to each other in the direction of arrow A when the eccentric amount ε of the eccentric disk 19 increases. At this time, since the eccentric disk 19 rubs from the opened side of the V-shaped groove 43a (solid line) of the friction member 44 to the pointed side, a large frictional force is generated between the eccentric disk 19 and the friction member 44, Further, since the eccentric cam 18 also rubs from the side where the V-shaped grooves 43a... (Shown by broken lines) of the friction member 44 are opened to a pointed side, a large frictional force is generated between the eccentric cam 18 and the friction member 44.

  Conversely, when the eccentric amount ε of the eccentric disk 19 decreases, the eccentric cam 18 and the eccentric disk 19 rotate relative to each other in the arrow B direction. At this time, since the eccentric disk 19 rubs the V-shaped groove 43a ... (shown by the solid line) of the friction member 44 from the sharp side to the opened side, a small frictional force is generated between the eccentric disk 19 and the friction member 44, Further, the eccentric cam 18 also rubs the V-shaped grooves 43a (shown by broken lines) of the friction member 44 from the pointed side to the opened side, so that a small frictional force is generated between the eccentric cam 18 and the friction member 44.

  As described above, when the eccentric disk 19 moves radially outward (in the direction in which the eccentric amount ε increases) by the inertial force, the grooves 43a of the friction member 44 act so as to increase the frictional force. 19 can be restrained to cancel the inertial force. On the contrary, when the kick-down operation in which the accelerator pedal is strongly depressed is performed and the eccentric disk 19 moves in a direction to decrease the eccentricity ε, it is desirable to improve the shift response, but at that time, the grooves 43a of the friction member 44 are formed. Since it acts so as to reduce the frictional force, the eccentric disk 19 can be quickly moved by the inertial force, and the shift response can be improved.

  Even if the clearance between the support walls 18c and 18c of the eccentric cam 18 and the side walls 19c and 19c of the eccentric disk 19 is clogged by the bending of the input shaft 12 due to the reaction force received by the connecting rod 33 from the output shaft 13, By preventing the arranged friction member 44 from directly contacting the eccentric cams 18 and 18 and the eccentric disk 19, generation of noise and vibration can be suppressed. At this time, the first rubber washer 42 of the friction member 44 is elastically deformed, so that vibration due to contact can be attenuated.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the embodiment, the grooves 43a are provided on the side surface of the friction member 44 facing the side wall 19c of the eccentric disc 19 and the side surface of the friction member 44 facing the support wall 18c of the eccentric cam 18. The groove 43a on the side surface of the friction member 44 facing the 18 support wall 18c can be omitted, and the groove 43a on the side surface of the friction member 44 facing the side wall 19c of the eccentric disk 19 is omitted. Alternatively, a groove may be formed on the side surface of the side wall 19 c of the eccentric disk 19 that faces the side surface of the friction member 44. However, if a groove is provided between the side surface of the side wall 19c of the eccentric disk 19 and the side surface of the friction member 44, and a groove is provided between the side surface of the support wall 18c of the eccentric cam 18 and the side surface of the friction member 44, the total amount corresponding to that. Thus, the eccentric disk 19 can be restrained more strongly and the generation of vibration and noise can be more effectively suppressed.

  In the embodiment, the grooves 43a are V-shaped with a sharp tip, but may have a U-shape with a rounded tip.

  In the embodiment, the pair of friction members 44 and 44 are arranged on the side walls 19c and 19c on both sides in the axial direction of the eccentric disk 19, but only one friction member 44 is provided on one side wall 19c in the axial direction of the eccentric disk 19. May be arranged.

  In addition, a metal wave spring may be used instead of the first rubber washer 42, and the friction member 44 is configured with only one metal washer by eliminating the first rubber washer 42 and the wave spring. Also good.

12 Input shaft 13 Output shaft 14 Transmission unit 15 Transmission shaft 17 Pinion 18 Eccentric cam 18c Support wall 19 Eccentric disc (eccentric member)
19b Ring gear 19c Side wall 23 Speed change actuator 33 Connecting rod 36 One-way clutch 38 Outer member 43a Groove 44 Friction member E Engine (drive source)
L Input shaft axis ε Eccentricity of eccentric member

Claims (2)

A plurality of transmission units (14) for shifting the rotation of the input shaft (12) connected to the drive source (E) and transmitting the rotation to the output shaft (13) are juxtaposed in the axial direction,
Each of the transmission units (14)
An eccentric cam (18) rotating integrally with the input shaft (12);
An eccentric member (19) formed with a ring gear (19b) that fits on the outer periphery of the eccentric cam (18) in a relatively rotatable manner;
A transmission shaft (15) disposed coaxially with the input shaft (12) and rotated by a transmission actuator (23);
A pinion (17) provided on the transmission shaft (15) and meshing with the ring gear (19b);
A one-way clutch (36) provided on the output shaft (13);
A connecting rod (33) connected to the eccentric member (19) and the outer member (38) of the one-way clutch (36) to reciprocate;
By changing the phase of the eccentric member (19) with respect to the eccentric cam (18) by rotating the transmission shaft (15) relative to the input shaft (12) by the transmission actuator (23), the input A vehicle power transmission device for changing a gear ratio by changing an eccentric amount (ε) of the eccentric member (19) from an axis (L) of a shaft (12),
The eccentric cam (18) includes a pair of support walls (18c) sandwiching the side wall (19c) of the eccentric member (19) from both axial sides, and at least one of the pair of support walls (18c) and the side wall (19c). Between the side wall (19c) and the side surface of the friction member (44) facing the side wall (19c), a V-shaped or U-shaped groove (43a). ) And the groove (43a) has a large frictional force when the eccentric member (19) rotates in a direction to increase the amount of eccentricity (ε), and the eccentric member (19) has an amount of eccentricity (ε). The vehicle power transmission device is arranged in a direction in which the frictional force decreases when rotating in a direction to reduce the power. The vehicle power transmission device according to claim 1, wherein the groove (43a) is also formed on a side surface of the friction member (44) facing the support wall (18c).

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