JP6175477B2 - Power transmission device for vehicle - Google Patents

Description

  The present invention provides an input shaft connected to a drive source of a vehicle, an output shaft arranged in parallel with the input shaft, an eccentric member that rotates eccentrically integrally with the input shaft, and an eccentric amount of the eccentric member A variable speed actuator, a swing link supported swingably on the output shaft, a connecting rod connecting the eccentric member and the swing link, and the output shaft and the swing link, The present invention relates to a vehicular power transmission device including a one-way clutch that engages when a connecting rod moves in a pushing direction and disengages when the connecting rod moves in a pulling direction.

  A crank type that converts the rotation of the input shaft connected to the engine into reciprocating motions of multiple connecting rods that are out of phase with each other, and converts the reciprocating motion of multiple connecting rods into the rotational motion of the output shaft by multiple one-way clutches. In the continuously variable transmission mechanism, the radial thickness of the outer member of the one-way clutch arranged on the inner periphery of the swing link is positioned between the position close to the connecting rod and the connection portion of the swing link and the axis of the output shaft. The one-way clutch is miniaturized by making the connection portion closer to the axis of the output shaft while preventing the stress from concentrating on a part of the outer member by making the connection portion and the point symmetric with a thin wall. This is known from Patent Document 1 below.

  In addition, a plurality of wedge-shaped spaces are formed between the outer circumferential surface of the inner member of the one-way clutch and the inner inclined surface of the outer member, and a plurality of rollers having different diameters are arranged in each wedge-shaped space, thereby providing a one-way clutch. Japanese Patent Application Laid-Open No. 2004-151867 discloses a technique in which a load at the time of engaging a clutch is distributed to a plurality of rollers to reduce wear of the rollers and improve durability.

JP 2014-177777 A JP-A-8-28597

  By the way, in such a one-way clutch of the crank type continuously variable transmission mechanism, when an inclined surface is formed on the inner member side integral with the rotating output shaft among the outer member and the inner member sandwiching the roller, the inclined surface of the inner member is restrained. Since the roller thus rotated rotates together with the inner member, the wear amount of all the rollers is automatically equalized. However, when the inclined surface is formed on the outer member side integral with the swing link that reciprocally swings, the rollers restrained by the inclined surface of the outer member do not rotate together with the inner member. There is a problem that the wear of the one-way clutch deteriorates due to uneven wear.

  This will be described in detail with reference to the drawings. As shown in FIG. 7A, when the one-way clutch 01 is engaged, an inner member 02 having an arc surface on the outer periphery and an outer member 03 having an inclined surface on the inner periphery. During this time, the roller 04 is engaged, and a surface pressure P1 acts between the inclined surface of the outer member 03 and the roller 04.

  Further, as shown in FIG. 7B, when the one-way clutch 01 is engaged, the outer member 03 receives a pressing load F from the connecting rod 05. The surface pressure P2 acts between the roller 04 and the portion on the opposite side).

  FIG. 7C shows total surface pressures P3 and P4 obtained by adding the surface pressure P1 due to the engagement of the one-way clutch 01 and the surface pressure P2 due to the pressing load F from the connecting rod 05. It can be seen that the total surface pressures P3 and P4 acting between the roller and the roller 04 differ according to the circumferential position. That is, a small total surface pressure P3 acts between the roller 04 and the half circumference portion on the same side as the direction of the pressing load F of the outer member 03, but the half circumference on the opposite side to the direction of the pressing load F of the outer member 03. A large total surface pressure P4 acts between the portion and the roller 04. In the one-way clutch 01 having an inclined surface on the outer member 03 side, the roller 04 is restrained by the outer member 03 and does not rotate together with the inner member 02. Therefore, the roller 04 receiving a large total surface pressure P4 is worn early. There is a problem that this causes the durability of the one-way clutch 01 to decrease.

  The present invention has been made in view of the above circumstances, and an object thereof is to reduce the outer diameter while ensuring the durability of the one-way clutch.

  To achieve the above object, according to the first aspect of the present invention, an input shaft connected to a drive source of a vehicle, an output shaft arranged in parallel with the input shaft, and the input shaft are integrated. An eccentric member that rotates eccentrically, a speed change actuator that changes the amount of eccentricity of the eccentric member, a swing link that is swingably supported by the output shaft, and a connecting rod that connects the eccentric member and the swing link And a one-way clutch disposed between the output shaft and the swing link and engaged when the connecting rod moves in the pushing direction and disengaged when the connecting rod moves in the pulling direction. The one-way clutch is configured such that a plurality of rollers disposed between the inner member and the outer member bite into an inclined surface formed on the outer member side. Power is a transferable, the plurality of rollers for a vehicle power transmission device which is a larger diameter than those in the pushing side what is pulling side of the connecting rod is proposed.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, when the driving force transmitted by the one-way clutch is maximized, the connecting point of the connecting rod and the swing link and the A vehicular power transmission device is proposed in which the roller on the pulling side of the connecting rod has a larger diameter than the roller on the push side with respect to a boundary line connecting the axis of the output shaft.

  According to a third aspect of the present invention, in addition to the configuration of the second aspect, the roller has at least three diameters, and is a position farthest from the boundary line to the pulling side of the connecting rod. The vehicular power transmission device is proposed in which the roller having a maximum diameter and the roller located farthest from the boundary line on the pushing side of the connecting rod has a minimum diameter.

  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 first aspect, when the eccentric member rotates eccentrically with the input shaft, the connecting rod having one end connected to the eccentric member reciprocates, and the swing link to which the other end of the connecting rod is connected reciprocates. Swing. The one-way clutch is engaged when the swing link swings in the pushing direction of the connecting rod, and the one-way clutch is disengaged when the swing link swings in the pulling direction of the connecting rod. The rotation is shifted and transmitted to the output shaft. When the eccentric amount of the eccentric member is changed by the speed change actuator, the reciprocating stroke of the connecting rod is changed to change the speed ratio of the power transmission device.

  The one-way clutch is capable of transmitting driving force by engaging a plurality of rollers arranged between the inner member and the outer member with an inclined surface formed on the outer member side, so that the positional relationship between the outer member and each roller Is constant, the surface pressure generated in each roller is determined by the load applied from the connecting rod. The roller on the pulling side of the connecting rod that generates large surface pressure is larger in diameter than the roller on the connecting side of the connecting rod that generates small surface pressure, so it matches the surface pressure that generates the diameter of each roller. By setting the minimum necessary size, it is possible to reduce the outer diameter of the one-way clutch while ensuring the durability of the one-way clutch.

  According to the second aspect of the present invention, when the driving force transmitted by the one-way clutch reaches a maximum, the pulling of the connecting rod with respect to the boundary line connecting the connecting point of the connecting rod and the swing link and the axis of the output shaft. Since the roller on the side has a larger diameter than the roller on the push side, a plurality of rollers having different diameters can be accurately arranged to make the surface pressure uniform, and the reliability of the one-way clutch can be improved.

  According to the third aspect of the present invention, the roller has at least three diameters, and the roller located farthest from the boundary line toward the pulling side of the connecting rod has the maximum diameter, and the roller has a maximum diameter. Since the roller located at the furthest position on the push side has the smallest diameter, not only can the surface pressure of a plurality of rollers arranged at different positions in the circumferential direction be made uniform to further improve the reliability of the one-way clutch, It is possible to optimize the surface pressure of each roller with respect to the load applied from the connecting rod.

The longitudinal cross-sectional view of a continuously variable transmission. (First embodiment) FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. (First embodiment) The front view and sectional drawing of an eccentric disk. (First embodiment) The figure which shows the relationship between the eccentric amount of an eccentric disk, and a gear ratio. (First embodiment) The front view of a one-way clutch. (First embodiment) The front view of a one-way clutch. (Second Embodiment) Explanatory drawing of the surface pressure which acts on the roller of a one-way clutch. (Comparative example)

First embodiment

  Hereinafter, a first embodiment 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, rod portions 33 b and 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 FIG. 5, the outer peripheral surface of the inner member 39 of the one-way clutch 21 is constituted by a circumferential surface 39 a centering on the axis line Lo of the output shaft 13, but the inner peripheral surface of the outer member 38 is a roller 41. The number of inclined surfaces 38a... Is equal to the number (10 in the embodiment) of the inner member 39, and the ten rollers that hold the rollers 41 between the circumferential surface 39a of the inner member 39 and the inclined surface 38a of the outer member 38. A wedge-shaped space is formed. Since the outer circumferential surface of the inner member 39 is a circumferential surface 39a, the rollers 41 can freely move relative to the outer circumferential surface of the inner member 39, but the inclined surfaces 38a of the outer member 38 define a wedge-shaped space. Therefore, the rollers 41 are restrained on the corresponding inclined surfaces 38a of the outer member 38.

  The line L1 in FIG. 5 indicates the position of the outer member 38 at the moment when the roller 41 bites into the wedge-shaped space in the stroke in which the connecting rod 33 moving on the right side in the drawing presses the swing link 42 and the one-way clutch 36 is engaged. Is shown. When the connecting rod 33 is further pushed after the roller 41 is engaged with the wedge-shaped space, the circumferential surface 39a of the inner member 39, the inclined surface 38a of the outer member 38, and the roller 41 are elastically deformed, whereby the roller 41 ... Bite further into the circumferential surface 39 a of the inner member 39 and the inclined surface 38 a of the outer member 38, and the driving force is transmitted from the outer member 38 to the inner member 39. A line L2 in FIG. 5 indicates the position of the outer member 38 when the driving force transmitted by the one-way clutch 36 is maximized, and the angle α formed by the line L1 and the line L2 is defined as the maximum torsion angle. The maximum torsion angle α is about several degrees.

  Assuming that the line L2 where the maximum torsion angle α is generated is a boundary line, the surface pressure of the rollers 41 is larger on the pulling side of the connecting rod 33 (the input shaft 12 side) than the boundary line L2, as already described with reference to FIG. Thus, the surface pressure of the rollers 41 becomes smaller on the pushing side of the connecting rod 33 (on the side opposite to the input shaft 12) than the boundary line L2. In the present embodiment, among the ten rollers 41 of the one-way clutch 36, the five rollers 41, which are located on the pulling side of the connecting rod 33 from the boundary line L2 and receive a large surface pressure, have a large diameter. The five rollers 41... That are positioned closer to the connecting rod 33 than the boundary line L2 and receive a small surface pressure have a small diameter.

  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.

  When the connecting rod 33 reciprocates and transmits driving force to the output shaft 13, the one-way clutch 36 is engaged in the pushing stroke of the connecting rod 33, and the one-way clutch 36 is disengaged in the pulling stroke of the connecting rod 33. To do. When the one-way clutch 36 is engaged in the pushing stroke of the connecting rod 33, the five rollers 41 on the pulling side of the connecting rod 33 with respect to the boundary line L2 are subjected to surface pressure due to the engagement of the one-way clutch 01 and the connecting force. A large surface pressure is added to the surface pressure due to the pressing load of the rod 33. However, since the five rollers 41 are formed in a large diameter, they support a large surface pressure while ensuring the necessary durability. can do.

  On the other hand, a small surface pressure obtained by subtracting the surface pressure due to the pressing load of the connecting rod 33 from the surface pressure due to the engagement of the one-way clutch 01 is applied to the five rollers 41. Therefore, the required durability can be ensured even if the five rollers 41 are formed to have a small diameter.

  If all the rollers have the same diameter as in a conventional one-way clutch, the roller diameter must be set so that it can withstand the largest surface pressure. Is excessive, the outer diameter of the one-way clutch 36 increases accordingly. However, according to the present embodiment, the outer diameter of the one-way clutch 36 can be reduced while ensuring the required durability by making the diameters of the rollers 41 different depending on the acting surface pressure.

  Further, if an inclined surface is provided on the inner member 39 side, the circumferential position of the rollers 41 changes as the inner member 39 rotates together with the output shaft 13, and the diameter of the rollers 41 varies. However, according to the present embodiment, by providing the inclined surface 38a on the outer member 38 side, the above-described problem can be solved by making the circumferential position of the rollers 41 constant.

Second embodiment

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the five rollers 41 positioned on the pulling side of the boundary line L have a large diameter, and the five rollers 41 positioned on the pressing side of the boundary line L have a small diameter. In the second embodiment, the diameters of the ten rollers 41 are made different according to the magnitude of the surface pressure acting on them. That is, the roller 41 on which the largest surface pressure acts away from the boundary line L2 to the pull side is the maximum diameter, and the roller 41 on the smallest distance from the boundary line L2 to the push side acts on the minimum diameter. The diameter of the rollers 41... Positioned between them is changed stepwise from the maximum diameter to the minimum diameter.

  As a result, the diameter of each of the rollers 41 can be set to the minimum necessary size according to the surface pressure acting, and the outer diameter of the one-way clutch 36 can be reduced as much as possible.

  In the second embodiment, the types of the diameters of the rollers 41 are arbitrary, and at least three types of diameters may be provided.

  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, the number of rollers 41... Of the one-way clutch 36 is not limited to ten in the embodiment.

12 Input shaft 13 Output shaft 19 Eccentric disc (eccentric member)
23 Transmission actuator 33 Connecting rod 36 One-way clutch 38 Outer member 38a Inclined surface 39 Inner member 41 Roller 42 Swing link E Engine (drive source)
Lo Output shaft axis L2 Boundary line

Claims (3)

An input shaft (12) connected to a drive source (E) of the vehicle;
An output shaft (13) disposed parallel to the input shaft (12);
An eccentric member (19) rotating eccentrically integrally with the input shaft (12);
A speed change actuator (23) for changing the amount of eccentricity of the eccentric member (19);
A swing link (42) supported swingably on the output shaft (13);
A connecting rod (33) connecting the eccentric member (19) and the swing link (42);
A one-way clutch that is disposed between the output shaft (13) and the swing link (42) and that engages when the connecting rod (33) moves in the pushing direction and disengages when it moves in the pulling direction. (36) a vehicle power transmission device comprising:
In the one-way clutch (36), a plurality of rollers (41) arranged between the inner member (39) and the outer member (38) are engaged with an inclined surface (38a) formed on the outer member (38) side. The plurality of rollers (41) have a larger diameter on the pulling side of the connecting rod (33) than on the push side, so that the driving force can be transmitted. apparatus.   When the driving force transmitted by the one-way clutch (36) is maximized, the connecting point of the connecting rod (33) and the swing link (42) is connected to the axis (Lo) of the output shaft (13). The roller (41) on the pulling side of the connecting rod (33) has a larger diameter than the roller (41) on the pushing side with respect to the boundary line (L2). Vehicle power transmission device.   The roller (41) has at least three diameters, and the roller (41) at a position farthest from the boundary line (L2) to the pulling side of the connecting rod (33) has a maximum diameter, The power transmission device for a vehicle according to claim 2, characterized in that the roller (41) located farthest from the boundary line (L2) to the pushing side of the connecting rod (33) has a minimum diameter. .

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