JP6175420B2 - Power transmission device for vehicle - Google Patents

Description

  The present invention relates to a crank type vehicle power transmission device including a one-way clutch.

  Power transmission for vehicles equipped with a one-way clutch that converts the rotation of the input shaft connected to the engine to the reciprocating motion of the connecting rod, and further converts the reciprocating motion of the connecting rod to the rotational motion of the output shaft by the one-way clutch. An apparatus is described in US Pat. The one-way clutch described in Patent Document 1 includes an outer member, an inner member, a plurality of rollers disposed between the outer member and the inner member, and a plurality of coil springs that urge each of the rollers. When the rotational speed becomes faster than the rotational speed of the inner member, the roller is engaged with the wedge portion provided between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member, and the input shaft is changed to the output shaft. Torque is being transmitted.

Japanese Patent No. 5142234

  However, in the vehicle power transmission device described in Patent Document 1, when the one-way clutch is shifted from the engaged state to the non-engaged state, that is, when the torque of the one-way clutch is released, a large vibration is generated in the input / output shaft. I understood that. FIG. 12 shows the torque fluctuation of the one-way clutch and the vibration generated in the input / output shaft due to the torque fluctuation. It can be seen that a large vibration is generated in the input / output shaft when the torque of the one-way clutch is released. .

  An object of the present invention is to provide a vehicular power transmission device capable of suppressing vibration when a one-way clutch shifts from an engaged state to a non-engaged state.

  As a result of intensive studies, the present inventors have found that vibration occurs when the torque of the one-way clutch is released, as shown in FIG. 13, the time change of the torque transmitted to the output shaft by the one-way clutch suddenly occurs when the torque is released. It is found that this is due to a change, and it is intended to moderate the time change of the torque when releasing the torque, and the outer member of the one-way clutch has a split structure, and the first outer member and the first outer member that are split when torque is not transmitted The present invention has been achieved by configuring so that no surface pressure is generated between the two outer members.

In order to achieve the above object, the invention described in claim 1
An output shaft (for example, an embodiment described later) is obtained by shifting the rotation of an input shaft (for example, an input unit 2 and a cam disk 5 in an embodiment described later) connected to a drive source (for example, an engine ENG in an embodiment described later). A plurality of power transmission units (for example, a power transmission unit 20 according to an embodiment described later) that are transmitted in parallel in the axial direction between the input shaft and the output shaft,
Each of the power transmission units is
An input side fulcrum (for example, an eccentricity amount (for example, an eccentricity amount R1 of an embodiment to be described later) that is variable from an axis of the input shaft (for example, a rotation center axis P1 of an embodiment to be described later) is variable. , The center P3) of the rotating disk 6 of the embodiment described later,
An inner member (for example, an inner member 72 in an embodiment described later), an outer member (for example, an outer member 71 in an embodiment described later), and an inner peripheral surface of the outer member (for example, an inner peripheral surface in an embodiment described later) 71a) and an outer peripheral surface of the inner member (for example, an outer peripheral surface 72a in an embodiment described later) and a cage (for example , a roller 25 in an embodiment described later) and a cage (for example, includes a cage 31) of the embodiments described below, wherein the wedge portion provided on the outer peripheral surface of the inner member (e.g., by engaging the wedge W) to the roller embodiments described below, the input shaft A one-way clutch (for example, a one-way clutch 17 in an embodiment described later) that transmits torque to the output shaft,
An output side fulcrum provided on the outer member of the one-way clutch (for example, an output side fulcrum P4 in an embodiment described later);
A vehicle power transmission device (for example, a continuously variable transmission 1 according to an embodiment described later) including a connecting rod (for example, a connecting rod 15 according to an embodiment described later) connecting the input fulcrum and the output fulcrum; There,
The outer member is disposed in a relatively non-rotatable manner on a first outer member (for example, a first outer member 75 in an embodiment described later) on which the output side fulcrum is formed and an inner peripheral portion of the first outer member. A second outer member (for example, a second outer member 76 in an embodiment described later),
The first outer member and the second outer member are configured such that no surface pressure is generated when torque of the one-way clutch is not transmitted.

The invention described in claim 2 is the configuration of claim 1,
Between the first outer member and the second outer member, a predetermined radial gap (for example, a radial gap T in an embodiment described later) is provided when torque of the one-way clutch is not transmitted.
The radial clearance is equal to or less than the diameter expansion amount of the second outer member accompanying torque transmission of the one-way clutch.

The invention described in claim 3 is the structure described in claim 1 or 2,
The first outer member and the second outer member are configured to be relatively non-rotatable by a key (for example, a key 77 in an embodiment described later) and a key groove (for example, a key groove 75b, 76b in an embodiment described later). The

In order to achieve the above object, the invention described in claim 4 is:
An output shaft (for example, an embodiment described later) is obtained by shifting the rotation of an input shaft (for example, an input unit 2 and a cam disk 5 in an embodiment described later) connected to a drive source (for example, an engine ENG in an embodiment described later). A plurality of power transmission units (for example, a power transmission unit 20 according to an embodiment described later) that are transmitted in parallel in the axial direction between the input shaft and the output shaft,
Each of the power transmission units is
An input side fulcrum (for example, an eccentricity amount (for example, an eccentricity amount R1 of an embodiment to be described later) that is variable from an axis of the input shaft (for example, a rotation center axis P1 of an embodiment to be described later) is variable. , The center P3) of the rotating disk 6 of the embodiment described later,
An inner member (e.g., an inner member 72 in an embodiment described later), an outer member (e.g., an outer member 71 in an embodiment described later), and a roller (e.g., a roller 25 in an embodiment described later), A wedge portion (e.g., an outer peripheral surface (e.g., an inner peripheral surface 71a in an embodiment described later) of the outer member and an outer peripheral surface (e.g., an outer peripheral surface 72a in an embodiment described later) of the outer member are provided. and the roller is engaged with the wedge portion W) of the embodiments described below, the one-way clutch for transmitting torque to the output shaft from the input shaft (for example, one-way clutch 17 in embodiment),
An output side fulcrum provided on the outer member of the one-way clutch (for example, an output side fulcrum P4 in an embodiment described later);
A vehicle power transmission device (for example, a continuously variable transmission 1 according to an embodiment described later) including a connecting rod (for example, a connecting rod 15 according to an embodiment described later) connecting the input fulcrum and the output fulcrum; There,
The outer member includes a first outer member formed with the output side fulcrum (for example, a first outer member 75 in an embodiment described later) and an outer peripheral portion of the first outer member so as to avoid the output side fulcrum. A second outer member (for example, a second outer member 76 in an embodiment described later) disposed,
The first outer member and the second outer member are configured such that no surface pressure is generated when torque of the one-way clutch is not transmitted.

The invention described in claim 5 is the configuration of claim 4,
Between the first outer member and the second outer member, a predetermined radial gap (for example, a radial gap T in an embodiment described later) is provided when torque of the one-way clutch is not transmitted.
The radial clearance is equal to or less than the diameter expansion amount of the first outer member accompanying torque transmission of the one-way clutch.

The invention described in claim 6 is the structure described in claim 4 or 5,
In the second outer member, at least two or more rigid members (for example, a second outer member piece 80 in an embodiment described later) are coupled by a coupling member (for example, a coupling member 79 in an embodiment described later).

  According to the configuration of claim 1, the outer member of the one-way clutch has a split structure, and is configured so that no surface pressure is generated between the first outer member and the second outer member when torque is not transmitted. When the roller is engaged with the wedge portion during transmission and the second outer member expands in diameter, the surface pressure is generated, so that when the one-way clutch is shifted from the engaged state to the non-engaged state. The time change of the torque can be made gentle, and the vibration due to the sudden change of the torque can be suppressed.

  According to the configuration of the second aspect, by making the first outer member and the second outer member a clearance fit, a surface pressure is reliably generated between the first outer member and the second outer member when torque is not transmitted. It can be configured not to.

  According to the configuration of the third aspect, the first outer member and the second outer member can be configured to be relatively non-rotatable with a simple configuration of the key and the key groove, and the first outer member and the second outer member By engaging the key and the key groove before the surface pressure is generated between the first outer member and the second outer member, the first outer member and the second outer member can rotate together to move the roller to the wedge portion.

According to the configuration of claim 4, the outer member of the one-way clutch is configured such that no surface pressure is generated between the first outer member and the second outer member when torque is not transmitted, and the roller is a wedge portion when torque is transmitted. Is configured so that the surface pressure is generated when the diameter of the second outer member is increased by engaging the gear, and the time change of the torque when shifting from the engaged state to the disengaged state of the one-way clutch is moderated. And vibration due to a sudden change in torque can be suppressed.
Further, since the second outer member functions as a simple rigid member, it is not necessary to set an axis.

  According to the fifth aspect of the present invention, by making the first outer member and the second outer member a clearance fit, a surface pressure is reliably generated between the first outer member and the second outer member when torque is not transmitted. It can be configured not to.

  According to the structure of Claim 6, since the 2nd outer member only needs to couple | bond together at least 2 or more rigid members with a coupling member, an assembly | attachment can be made easy.

It is sectional drawing of the continuously variable transmission which concerns on one Embodiment of this invention. It is explanatory drawing which shows the structure of the power transmission unit of the continuously variable transmission of FIG. 1 from an axial direction. It is explanatory drawing which shows the change of the rotation radius of the input side fulcrum of the power transmission unit of the continuously variable transmission of FIG. 1, (A) is a rotation radius "maximum", (B) is a rotation radius "medium", ( C) shows a case where the turning radius is “small”, and (D) shows a case where the turning radius is “0”. FIG. 7 is an explanatory diagram showing a change in the swing range of the output side fulcrum with respect to a change in the rotation radius of the input side fulcrum of the power transmission unit of the continuously variable transmission of FIG. B shows a case where the swing range is “medium”, (C) shows a case where the swing range is “small”, and (D) shows a case where the swing range is “0”. It is a disassembled perspective view of the one-way clutch of 1st Embodiment. In the one-way clutch of 1st Embodiment, (a) It is a figure which shows the state in which the radial direction clearance T existed between the 1st outer member and the 2nd outer member in the engagement initial stage of a roller, (b). It is a figure which shows the state which the roller bite into the wedge part and the radial clearance T between the 1st outer member and the 2nd outer member decreased, (c) is a 1st outer member and a 2nd outer member contact | adhered And it is a figure which shows the state in which the surface pressure acted between both. It is operation | movement explanatory drawing of the one-way clutch of 1st Embodiment. In the one-way clutches of the first and second embodiments, (a) is a graph showing the torque transmitted from the one-way clutch to the output shaft when the swinging link makes one rotation, and (b) is a graph showing that the swinging link is 1 It is a graph which shows the time change of the torque transmitted to an output shaft from a one-way clutch when rotating. It is a figure of the one-way clutch of 2nd Embodiment before the assembly | attachment to the 1st outer member of a 2nd outer member, (a) is a side view, (b) is a front view. It is a figure of the one-way clutch of 2nd Embodiment after the assembly | attachment to the 1st outer member of a 2nd outer member, (a) is a side view, (b) is a front view. In the modified one-way clutch, (a) is a diagram showing a state in which a radial clearance T exists between the first inner member and the second inner member in the initial stage of engagement of the roller, and (b) It is a figure which shows the state which the bit direction gap T between the 1st inner member and the 2nd inner member which bite into the wedge part decreased, (c) is a 1st inner member and a 2nd inner member closely_contact | adhering, It is a figure which shows the state to which the surface pressure acted between. 2 shows torque fluctuations in a conventional one-way clutch and vibrations generated in the input / output shafts with the torque fluctuations. In the conventional one-way clutch, (a) is a graph showing torque transmitted from the one-way clutch to the output shaft when the swinging link makes one rotation, and (b) is a one-way clutch when the swinging link makes one rotation. It is a graph which shows the time change of the torque transmitted to an output shaft from.

  Hereinafter, an embodiment of a vehicle power transmission device of the present invention will be described with reference to the drawings. The vehicle power transmission device of the present embodiment is a continuously variable transmission of a four-bar linkage mechanism, and the gear ratio h (h = rotation speed of the input shaft / rotation speed of the output shaft) is set to infinity (∞). It is a kind of transmission that can make the rotation speed of the output shaft “0”, so-called IVT (Infinity Variable Transmission).

  Hereinafter, with reference to FIGS. 1-8, the continuously variable transmission 1 as one Embodiment of the vehicle power transmission device of this invention is demonstrated.

  First, with reference to FIG.1 and FIG.2, schematic structure of the continuously variable transmission 1 of this embodiment is demonstrated.

  As shown in FIG. 1, the continuously variable transmission 1 of the present embodiment includes an input unit 2, an output shaft 3 arranged in parallel with the rotation center axis P <b> 1 of the input unit 2, and a rotation center axis P <b> 1 of the input unit 2. And six turning radius adjusting mechanisms 4 provided on the top.

  The input unit 2 rotates around the rotation center axis P <b> 1 by transmitting a driving force from the engine ENG as a main driving source. In addition, as a main drive source, you may use an electric motor other than an internal combustion engine.

  The output shaft 3 transmits a rotational driving force to driving wheels (not shown) of the vehicle via a differential gear (not shown). A propeller shaft may be provided instead of the differential gear.

  The turning radius adjusting mechanism 4 includes a cam disk 5 provided on the rotation center axis P <b> 1 of the input unit 2, and a rotating disk 6 that is rotatably fitted on the cam disk 5.

  The cam disks 5 have a disk shape, and are provided in pairs so that they can rotate integrally with the input unit 2 while being eccentric with respect to the rotation center axis P1 of the input unit 2. Each set of cam disks 5 is set so as to have a phase difference of 60 °, and is arranged so that the six sets of cam disks 5 make a round in the circumferential direction of the rotation center axis P1 of the input unit 2.

  The cam disk 5 is formed with a through hole 5 a that penetrates in the direction of the rotation center axis P <b> 1 of the input unit 2 and is formed at a position eccentric with respect to the center P <b> 2 of the cam disk 5. Further, the cam disk 5 communicates with the outer peripheral surface of the cam disk 5 and the inner peripheral surface of the through hole 5a in a region opposite to the center P2 of the cam disk 5 across the rotation center axis P1 of the input portion 2. A notch hole 5b is formed.

  A set of two cam disks 5 is fixed with bolts (not shown). Further, one of the two cam disks 5 is formed integrally with the other of the other two cam disks 5 of the adjacent turning radius adjusting mechanism 4 to form an integral cam portion. Yes. The cam disk 5 located closest to the engine ENG among the cam disks 5 is formed integrally with the input unit 2. In this way, the input unit 2 and the plurality of cam disks 5 constitute an input shaft (camshaft).

  The two cam disks 5 may be fixed by other means instead of bolts. The integral cam portion may be formed by integral molding, or may be integrated by welding two cam disks 5. In addition, as a method of integrally forming the cam disk 5 and the input portion 2 that are closest to the engine ENG, the cam disc 5 and the input portion 2 may be integrally formed. May be used.

  As shown in FIG. 2, the rotary disk 6 has a disk shape in which a receiving hole 6 a is provided at a position eccentric from the center P <b> 3, and is provided to be rotatable with respect to the rotation center axis P <b> 1 of the input unit 2. . A set of cam disks 5 is rotatably fitted in the receiving holes 6a. Further, as shown in FIG. 1, an internal tooth 6 b is provided in the receiving hole 6 a of the rotating disk 6 at a position between the pair of cam disks 5.

  Further, the receiving hole 6a of the rotating disk 6 has a distance Rx from the rotation center axis P1 of the input portion 2 to the center P2 of the cam disk 5 (center of the receiving hole 6a) and the center P2 of the cam disk 5 to the center of the rotating disk 6. The cam disk 5 is eccentric so that the distance Ry to P3 is the same.

  The input shaft configured by the input unit 2 and the plurality of cam disks 5 includes an insertion hole 50 configured by connecting through holes 5 a of the cam disk 5. Thereby, the input shaft has a hollow shaft shape in which one end opposite to the engine ENG is open and the other end is closed.

  In the insertion hole 50, the pinion shaft 7 is arranged concentrically with the rotation center axis P1 so as to be rotatable relative to the input shaft.

  The pinion shaft 7 has a pinion 7 a at a position corresponding to the internal teeth 6 b of the rotary disk 6. The pinion shaft 7 is provided with a pinion bearing 7b between the pinions 7a adjacent to each other in the direction of the rotation center axis P1 of the input unit 2. The pinion shaft 7 supports the input shaft via the pinion bearing 7b.

  The pinion 7 a is formed integrally with the shaft portion of the pinion shaft 7. The pinion 7 a meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. The pinion 7a may be configured separately from the pinion shaft 7 and connected to the pinion shaft 7 by spline coupling. In the present embodiment, the term “pinion 7 a” is defined as including the pinion shaft 7.

  The pinion shaft 7 is connected to a differential mechanism 8 constituted by a planetary gear mechanism or the like on one end side opposite to the engine ENG.

  As shown in FIG. 1, the differential mechanism 8 is configured as a planetary gear mechanism, for example, and includes a sun gear 9, a first ring gear 10 connected to an input shaft configured by the input unit 2 and a plurality of cam disks 5. A stepped pinion 12 comprising a second ring gear 11 connected to the pinion shaft 7, a large diameter portion 12 a meshing with the sun gear 9 and the first ring gear 10, and a small diameter portion 12 b meshing with the second ring gear 11 is rotated and rotated. And a carrier 13 that is pivotably supported.

  The sun gear 9 is connected to a rotation shaft 14 a of an actuator 14 that is a sub drive source for the pinion shaft 7, and a driving force is transmitted from the actuator 14. Therefore, the driving force of the actuator 14 is also transmitted to the pinion 7 a via the differential mechanism 8.

  When the rotation speed of the pinion shaft 7 is the same as the rotation speed of the input unit 2, the sun gear 9 and the first ring gear 10 rotate at the same speed. As a result, the four elements of the sun gear 9, the first ring gear 10, the second ring gear 11, and the carrier 13 are locked so that they cannot rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 is the same as the input unit 2. Rotates at speed.

  When the rotational speed of the pinion shaft 7 is made slower than the rotational speed of the input unit 2, the rotational speed of the sun gear 9 is Ns, the rotational speed of the first ring gear 10 is NR1, and the gear ratio between the sun gear 9 and the first ring gear 10 (first When j is the number of teeth of the ring gear 10 / the number of teeth of the sun gear 9, the number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1). The gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / number of teeth of the small diameter portion 12b). ) Is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  That is, when there is a difference between the rotational speed of the input unit 2 and the rotational speed of the pinion shaft 7, the driving force transmitted from the actuator 14 transmitted through the internal teeth 6 b of the rotating disk 6 that meshes with the pinion 7 a of the pinion shaft 7. Thus, the rotating disk 6 rotates the periphery of the cam disk 5 around the center P2 of the cam disk 5.

  Incidentally, as shown in FIG. 2, the rotating disk 6 rotates with respect to the cam disk 5 from the rotation center axis P <b> 1 of the input unit 2 to the center P <b> 2 of the cam disk 5 and the center P <b> 2 of the cam disk 5. It is eccentric so that the distance Ry to the center P3 of the disk 6 is the same.

  Therefore, the center P3 of the rotary disk 6 is positioned on the same line as the rotation center axis P1 of the input unit 2, and the distance between the rotation center axis P1 of the input unit 2 and the center P3 of the rotary disk 6 (of the rotation radius adjusting mechanism 4). The rotation radius), that is, the eccentricity R1 can be set to “0”.

  At the periphery of the rotary disk 6, there is a large-diameter input-side annular portion 15 a at one end (on the input portion 2 side), and at the other end (output shaft 3), the diameter of the input-side annular portion 15 a is larger. A connecting rod 15 having a small-diameter output-side annular portion 15b is rotatably connected.

  An input-side annular portion 15 a of the connecting rod 15 is rotatably fitted to the rotary disk 6 via a connecting rod bearing 16.

  Six swing links 18 are pivotally supported on the output shaft 3 via the one-way clutch 17 so as to correspond to the connecting rod 15.

  As will be described in detail later, the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, and the swing link 18 is on one side with respect to the output shaft 3 about the rotation center axis P <b> 5 of the output shaft 3. When the rotation link 18 is to be rotated relative to the output shaft 3, the swing link 18 is fixed to the output shaft 3 (fixed state). Is idled (idle state).

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the output-side annular portion 15 b of the connecting rod 15 is provided below the swing link 18. The swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the output-side annular portion 15b from the axial direction. The pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the output-side annular portion 15b.

  By inserting the connecting pin 19 as a swing shaft into the insertion hole 18c and the output side annular portion 15b, the connecting rod 15 and the swing link 18 are connected so as to be relatively rotatable.

  In the continuously variable transmission 1 of the present embodiment, the power transmission unit 20 is configured by the turning radius adjusting mechanism 4 having the above-described configuration, the swing link 18, and the connecting rod 15.

  In addition, in this embodiment, what provided the six power transmission units 20 was demonstrated. However, the number of power transmission units in the continuously variable transmission of the present invention is not limited to that number, and may include, for example, 5 or less power transmission units, or 7 or more power transmission units. May be.

  Further, in the present embodiment, the input shaft 2 and the plurality of cam disks 5 constitute an input shaft, and the input shaft is provided with the insertion hole 50 configured by connecting the through holes 5 a of the cam disk 5. . However, the input shaft in the continuously variable transmission of the present invention is not limited to that configured as described above.

  For example, the input part is configured in a hollow shaft shape having an insertion hole so that one end is opened, and the through hole is formed to be larger than that of the present embodiment so that the input part can be inserted into a disc-shaped cam disk. The cam disk may be splined to the outer peripheral surface of the input portion configured in a hollow shaft shape.

  In this case, the input portion formed of the hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. Then, the pinion inserted into the input part meshes with the internal teeth of the rotating disk via the notch hole of the input part and the notch hole of the cam disk.

  Next, the power transmission unit 20 of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 1, the continuously variable transmission 1 of the present embodiment includes a total of six power transmission units 20 (four-bar linkage mechanisms). As shown in FIG. 2, the power transmission unit 20 includes a connecting rod 15, a swing link 18, and a rotating radius adjusting mechanism 4 having a rotating disk 6 and having an adjustable rotating radius. By this power transmission unit 20, the rotational motion of the input shaft is converted into the rocking motion of the rocking link 18.

  In the power transmission unit 20, when the rotation radius (eccentricity R 1) of the center P 3 (input side fulcrum) of the rotating disk 6 of the rotation radius adjusting mechanism 4 is not “0”, the input unit 2 and the pinion shaft 7 are the same. When rotating at a speed, each connecting rod 15 pushes the swing end 18a between the input unit 2 and the output shaft 3 toward the output shaft 3 or pulls it toward the input unit 2 while changing the phase. The rocking link 18 is rocked by alternately repeating.

  Since the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, the connecting rod 15 causes the swing link 18 to rotate to the one side with respect to the output shaft 3. When rotating at a speed exceeding the speed, the swing link 18 is fixed to the output shaft 3 and transmits torque to the output shaft 3. On the other hand, when the swing link 18 rotates to the other side with respect to the output shaft 3, the swing link 18 idles with respect to the output shaft 3, and no torque is transmitted to the output shaft 3.

  In the continuously variable transmission 1 of the present embodiment, the turning radius adjusting mechanisms 4 of the six power transmission units 20 are arranged with phases shifted by 60 degrees, so that the output shaft 3 has six power transmissions. The units 20 are sequentially rotated.

  FIG. 3 is a diagram showing the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the rotating radius (the eccentric amount R1) of the center P3 (input side fulcrum) of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. is there.

  FIG. 3A shows a state in which the eccentric amount R1 is “maximum”, and the rotation center axis P1 of the input unit 2, the center P2 of the cam disk 5 and the center P3 of the rotation disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. In this case, the gear ratio h is “minimum”.

  3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C shows that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B, and “large” which is larger than the gear ratio h in FIG. 3B in FIG. Become.

  FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 of the input unit 2 and the center P3 of the rotating disk 6 are located concentrically. In this case, the gear ratio h is “infinity (∞)”.

  FIG. 4 is a diagram showing the relationship between the rotation radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotary radius adjusting mechanism 4 and the swing range θ2 of the swing motion of the swing link 18. It is.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio h is “minimum”), and FIG. B) is “medium” (when the gear ratio h is “medium”), FIG. 4C shows the case where the eccentricity R1 is “small” in FIG. 3C (the gear ratio h is FIG. 4D shows a case where the eccentricity R1 is “0” in FIG. 3D (when the gear ratio h is “infinity (∞)”).

  Here, R2 is the length of the swing link 18. More specifically, R2 is the distance from the rotation center axis P5 of the output shaft 3 to the connection point between the connecting rod 15 and the swinging end 18a, that is, the center of the connection pin 19 (output-side fulcrum P4). . Θ1 is the phase of the rotating disk 6 of the turning radius adjusting mechanism 4.

  As is apparent from FIG. 4, as the eccentric amount R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower, and when the eccentric amount R1 becomes “0”, the swing link 18 swings. Stops moving.

  Next, the structure and operation of the one-way clutch 17 will be described in detail with reference to FIG.

  The one-way clutch 17 of the present embodiment includes an annular outer member 71 that is partly formed integrally with the swing link 18, a cylindrical inner member 72 that is formed integrally with the output shaft 3, and a circular shape of the outer member 71. 12 rollers 25 arranged between the inner peripheral surface 71a of the inner member 72 and the outer peripheral surface 72a of the inner member 72 bent in a wave shape, an engagement spring 24 for urging the roller 25, and the roller 25 are held rotatably. And a cage 31 that is a holding member for supporting the engagement spring 24, and the roller 25 is formed in a wedge shape formed between the inner peripheral surface 71 a of the outer member 71 and the outer peripheral surface 72 a of the inner member 72. By engaging with the wedge portion W (see FIG. 7), which is a space, torque can be transmitted from the outer member 71 (swinging link 18) to the inner member 72 (output shaft 3). You have me.

  The cage 31 includes a pair of annular members 32 and 32 made of an annular plate member, and twelve spring support members 33 that are arranged at equal intervals in the circumferential direction and connect the pair of annular members 32 and 32 to each other. The pair of annular members 32, 32 are arranged on both axial sides of the twelve rollers 25, and twelve spring support members 33 are arranged between the twelve rollers 25. Referring also to FIG. 7, one end of the engagement spring 24 is formed with a fixed end portion 24 a fixed to the spring support member 33 of the cage 31, and the other end of the engagement spring 24 is disposed on the outer peripheral surface of the roller 25. An urging end 24b that abuts on 25a is formed. The fixed end 24a has a U-shaped cross section, and is fixed by being pressed into a spring support member 33 having a rectangular cross section.

  The outer member 71 has a pair of link plates 73 projecting radially outward at both ends of a cylindrical outer member body, and has a substantially U-shaped cross section. The pair of link plates 73 are integrally formed with a projecting piece 18b having an insertion hole 18c. In FIG. 5, reference numeral 28 denotes a clip that restricts the connecting pin 19 inserted into the insertion hole 18 c from being pulled out.

  Here, the outer member 71 of the present embodiment has a divided structure, and includes a first outer member 75 and a second outer member 76. In the following, the first embodiment is such that the second outer member 76 is fitted into the inner peripheral portion of the first outer member 75 integrally formed with the swing link 18, and the first outer member 75 is integrally formed with the swing link 18. A description will be given of a second embodiment in which a second outer member 76 is fitted on the outer peripheral portion of one outer member 75.

<First Embodiment>
First, the one-way clutch 17 of the first embodiment will be described with reference to FIGS.
In the one-way clutch 17 of the present embodiment, a first outer member 75 having a substantially U-shaped cross section in which a pair of link plates 73 and a cylindrical portion 74 connecting the pair of link plates 73 are integrally formed, and a cylindrical first 2 outer members 76, and the second outer member 76 is disposed on the inner periphery of the first outer member 75. That is, the first outer member 75 is formed integrally with the swing link 18, and the second outer member 76 is separate from the swing link 18.

  The key grooves 75b and 76b are positioned at the same phase on the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76 (in this embodiment, 180 ° from the insertion hole 18c). The key 77 engages with the key grooves 75b and 76b, so that the first outer member 75 and the second outer member 76 cannot be rotated relative to each other.

  The first outer member 75 and the second outer member 76 are fitted with a clearance, and a predetermined radial direction is provided between the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76. A gap T is provided. The radial clearance T is set to be equal to or less than the diameter expansion amount of the second outer member 76 that accompanies torque transmission of the one-way clutch 17, and when the torque of the one-way clutch 17 is not transmitted, the inner peripheral surface 75 a of the first outer member 75. And the outer peripheral surface 76a of the second outer member 76 are set so as not to generate surface pressure. On the other hand, when the torque of the one-way clutch 17 is transmitted, the roller 25 is engaged with the wedge portion W, and the inner peripheral surface 76c of the second outer member 76 is pushed radially outward by the roller 25 to increase the diameter, whereby the first outer member. The radial gap T between the inner peripheral surface 75 a of the second outer member 76 and the outer peripheral surface 76 a of the second outer member 76 is eliminated, and the gap between the inner peripheral surface 75 a of the first outer member 75 and the outer peripheral surface 76 a of the second outer member 76 is eliminated. Is set to generate surface pressure.

  Paying attention to one power transmission unit 20 among the six power transmission units 20 having the one-way clutch 17 having such a configuration, torque transmission of the one-way clutch 17 in the continuously variable transmission 1 is shown in FIGS. This will be described with reference to FIGS. 6 (the same applies to FIGS. 9 to 11), for simplicity, the outer peripheral surface 72a of the inner member 72 (output shaft 3) is simplified as a cylindrical surface, and the cage 31 and the engagement spring 24 are omitted. . Further, the drawing is focused on the radial gap T, and the rotation of the one-way clutch 17 is not shown (the same applies to FIG. 11).

  In the continuously variable transmission 1, the input unit 2 is rotated by the engine ENG in a state where the eccentricity R 1 is not “0”, and the rotational speed of the pinion shaft 7 is the same as the rotational speed of the input unit 2. When the rotary shaft 14a is rotated, the input shaft constituted by the input unit 2 and the plurality of cam disks 5 and the pinion shaft 7 are integrated with each other in the counterclockwise direction about the rotation center axis P1 ( Eccentric rotation (see arrow A in FIG. 2). The connecting rod 15 having the input side annular portion 15a supported on the outer periphery of the rotating disk 6 via a connecting rod bearing 16 is rotatably supported by a connecting pin 19 at the tip of the output side annular portion 15b. The swing link 18 integral with the outer member 75 is rotated counterclockwise (see arrow B in FIGS. 2 and 7).

  When the first outer member 75 rotates in the counterclockwise direction in this way, the second outer member 76 also rotates in the counterclockwise direction. At the initial stage of engagement of the roller 25, a state in which a radial gap T exists between the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76, that is, the first outer member 75 The roller 25 is engaged with the wedge portion W in a state where no surface pressure is generated between the inner peripheral surface 75a and the outer peripheral surface 76a of the second outer member 76, but the rigidity of the outer member 71 is low and the inner member 72 ( Little torque is transmitted to the output shaft 3) (FIG. 6A). Then, when the roller 25 is engaged with the wedge portion W and the inner peripheral surface 76c of the second outer member 76 is pushed radially outward by the roller 25 to increase the diameter, the radial gap T gradually decreases (FIG. 6B). )). Thereafter, the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76 are brought into close contact with each other, and a surface pressure acts between them (FIG. 6C), and the rigidity of the outer member 71 is increased. A large torque is transmitted to the inner member 72 (output shaft 3), and the inner member 72 (output shaft 3) rotates counterclockwise (see arrow B in FIGS. 2 and 7).

  When the input shaft and the pinion shaft 7 further rotate, the rotating disk 6 further rotates eccentrically in the counterclockwise direction (see arrow A in FIG. 2). The connecting rod 15 having the input side annular portion 15a supported on the outer periphery of the rotating disk 6 via a connecting rod bearing 16 is rotatably supported by a connecting pin 19 at the tip of the output side annular portion 15b. The swing link 18 integral with the outer member 75 is rotated clockwise (see arrow B ′ in FIGS. 2 and 7).

  When the first outer member 75 rotates in the clockwise direction in this way, the second outer member 76 also rotates in the clockwise direction. As the second outer member 76 rotates, the roller 25 is pushed out from the wedge portion W while compressing the engagement spring 24. At this time, since the diameter of the second outer member 76 that has been increased in diameter by being pushed radially outward by the roller 25 is gradually reduced, the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76 are reduced. Are gradually separated from the close contact state, and the surface pressure between them gradually decreases. Therefore, as shown in FIG. 8, the time change of the torque at the time of torque release becomes gentle compared with FIG. 13, and the time change of the torque is prevented from changing abruptly at the time of torque release. 3 vibration is suppressed. Then, when the roller 25 is separated from the wedge portion W, the outer member 71 rotates relative to the inner member 72 and torque transmission to the output shaft 3 is completed.

  Thus, when the outer member 71 reciprocally rotates, the output shaft 3 is counterclockwise (arrows in FIGS. 2 and 7) only when the rotation direction of the outer member 71 is counterclockwise (see arrow B in FIGS. 2 and 7). B)), the output shaft 3 rotates intermittently. Further, when the roller 25 transitions from the disengaged state to the engaged state and when the roller 25 transitions from the engaged state to the disengaged state, the radial clearance T causes the inner peripheral surface 75a of the first outer member 75 and the first 2 Since the surface pressure between the outer member 76 and the outer peripheral surface 76a is adjusted, the time change of the torque when the one-way clutch 17 is shifted from the engaged state to the non-engaged state can be particularly moderated. . Although the above description has been made with a focus on one power transmission unit 20, in the continuously variable transmission 1, the turning radius adjusting mechanisms 4 of the six power transmission units 20 are arranged by changing the phase by 60 degrees each. Therefore, the output shaft 3 is sequentially rotated by the six power transmission units 20.

  As described above, according to this embodiment, the outer member 71 of the one-way clutch 17 has a split structure, and surface pressure is generated between the first outer member 75 and the second outer member 76 when torque is not transmitted. The inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface of the second outer member 76 when the roller 25 engages with the wedge portion W during torque transmission and the second outer member 76 expands in diameter. Since the surface pressure is generated between the one-way clutch 17 and the non-engaged state of the one-way clutch 17, the time change of the torque can be moderated, and the torque changes suddenly. Can suppress vibrations.

  Further, by making the first outer member 75 and the second outer member 76 a clearance fit, the inner peripheral surface 75a of the first outer member 75 and the outer peripheral surface 76a of the second outer member 76 can be reliably transmitted when torque is not transmitted. It is possible to configure so that no surface pressure is generated between them.

  Furthermore, the first outer member 75 and the second outer member 76 can be configured to be relatively non-rotatable with a simple configuration of the key 77 and the key grooves 75b and 76b, and the inner peripheral surface 75a of the first outer member 75. The first outer member 75 and the second outer member 76 are integrated by engaging the key 77 and the key grooves 75b and 76b before the surface pressure is generated between the outer peripheral surface 76a of the second outer member 76 and the second outer member 76. By rotating, the roller 25 can be moved to the wedge portion W.

Second Embodiment
Next, the one-way clutch 17 of the second embodiment will be described with reference to FIGS.
In the one-way clutch 17 of the present embodiment, a first outer member 75 having a substantially U-shaped cross section in which a pair of link plates 73 and a cylindrical portion 74 connecting the pair of link plates 73 are integrally formed, and a cylindrical first 2 outer members 76, and the second outer member 76 is disposed on the outer periphery of the first outer member 75. That is, the first outer member 75 is formed integrally with the swing link 18, and the second outer member 76 is separate from the swing link 18.

  The second outer member 76 is arranged on the outer peripheral portion of the cylindrical portion 74 sandwiched between the pair of link plates 73 so as to avoid interference with the insertion hole 18c, and is divided into two half-cylindrical second outer members. The member piece 80 is coupled by a coupling member 79 such as a bolt at a fastening portion 78 formed on the mating surface.

  Further, the first outer member 75 and the second outer member 76 are fitted with a clearance, and between the outer peripheral surface 75 c of the cylindrical portion 74 of the first outer member 75 and the inner peripheral surface 76 c of the second outer member 76. Is provided with a predetermined radial gap T (not shown). The first outer member 75 and the second outer member 76 are rotatable relative to each other by the radial gap T. The second outer member 76 is integrated with the first outer member 75 as long as the radial gap T exists. It can move independently of the movement of the swing link 18. The radial clearance T is set to be equal to or less than the diameter expansion amount of the first outer member 75 that accompanies the torque transmission of the one-way clutch 17, and when the one-way clutch 17 does not transmit torque, It is set so that the surface pressure is not generated between the inner peripheral surface 76 c of the second outer member 76. On the other hand, when the torque of the one-way clutch 17 is transmitted, the roller 25 is engaged with the wedge portion W, and the inner peripheral surface 75a of the first outer member 75 is pushed radially outward by the roller 25 to increase the diameter, thereby the first outer member. The radial gap T between the outer peripheral surface 75c of 75 and the inner peripheral surface 76c of the second outer member 76 is eliminated, and the space between the outer peripheral surface 75c of the first outer member 75 and the inner peripheral surface 76c of the second outer member 76 is eliminated. Is set to generate surface pressure.

  As in the first embodiment, paying attention to one power transmission unit 20 among the six power transmission units 20 including the one-way clutch 17 having the above configuration, torque transmission of the one-way clutch 17 in the continuously variable transmission 1. In the state where the eccentric amount R1 is not “0”, the input unit 2 is rotated by the engine ENG, and the rotational axis of the actuator 14 is set so that the rotational speed of the pinion shaft 7 is the same as the rotational speed of the input unit 2. When 14a is rotated, the input shaft constituted by the input unit 2 and the plurality of cam disks 5 and the pinion shaft 7 are integrated with each other in the counterclockwise direction (in FIG. 2) about the rotation center axis P1. Eccentric rotation in the direction of arrow A). The connecting rod 15 having the input side annular portion 15a supported on the outer periphery of the rotating disk 6 via a connecting rod bearing 16 is rotatably supported by a connecting pin 19 at the tip of the output side annular portion 15b. The swing link 18 integral with the outer member 75 is rotated counterclockwise (see arrow B in FIGS. 2 and 7).

  When the first outer member 75 rotates in the counterclockwise direction in this way, at the initial stage of engagement of the roller 25, it is between the outer peripheral surface 75 c of the first outer member 75 and the inner peripheral surface 76 c of the second outer member 76. In a state where the radial gap T exists, that is, in a state where no surface pressure is generated between the outer peripheral surface 75c of the first outer member 75 and the inner peripheral surface 76c of the second outer member 76, the roller on the wedge portion W 25, but the rigidity of the outer member 71 is low, and almost no torque is transmitted to the inner member 72 (output shaft 3). Then, when the roller 25 bites into the wedge portion W and the inner peripheral surface 75a of the first outer member 75 is pushed radially outward by the roller 25 to increase the diameter, the radial gap T gradually decreases. Thereafter, the outer peripheral surface 75c of the first outer member 75 and the inner peripheral surface 76c of the second outer member 76 are brought into close contact with each other, so that a surface pressure acts between them, and the rigidity of the outer member 71 is increased, and the inner member 72 (the output shaft 3) ), A large torque is transmitted, and the inner member 72 (output shaft 3) rotates counterclockwise (see arrow B in FIGS. 2 and 7).

  When the input shaft and the pinion shaft 7 further rotate, the rotating disk 6 further rotates eccentrically in the counterclockwise direction (see arrow A in FIG. 2). The connecting rod 15 having the input side annular portion 15a supported on the outer periphery of the rotating disk 6 via a connecting rod bearing 16 is rotatably supported by a connecting pin 19 at the tip of the output side annular portion 15b. The swing link 18 integral with the outer member 75 is rotated clockwise (see arrow B ′ in FIGS. 2 and 7).

  When the first outer member 75 rotates in the clockwise direction in this way, the second outer member 76 also rotates in the clockwise direction. As the first outer member 75 rotates, the roller 25 is pushed out from the wedge portion W while compressing the engagement spring 24. At this time, the outer diameter 75c of the first outer member 75 and the inner circumference 76c of the second outer member 76 are gradually reduced since the diameter of the first outer member 75 that has been expanded radially by the roller 25 is increased. Are gradually separated from the close contact state, and the surface pressure between them gradually decreases. Therefore, similarly to FIG. 6, the time change of the torque at the time of torque release becomes gentle, the time change of the torque is prevented from changing suddenly at the time of torque release, and the vibration of the output shaft 3 as in the prior art is suppressed. Then, when the roller 25 is separated from the wedge portion W, the outer member 71 rotates relative to the inner member 72 and torque transmission to the output shaft 3 is completed.

  Thus, when the first outer member 75 reciprocates, the output shaft 3 is counterclockwise only when the rotation direction of the first outer member 75 is counterclockwise (see arrow B in FIGS. 2 and 7) (FIG. 2). , 7 (see arrow B), the output shaft 3 rotates intermittently. Further, when the roller 25 transitions from the disengaged state to the engaged state, and when the roller 25 transitions from the engaged state to the disengaged state, the outer circumferential surface 75c of the first outer member 75 and the second are separated by the radial gap T. Since the surface pressure with the inner peripheral surface 76c of the outer member 76 is adjusted, the time change of the torque when the one-way clutch 17 is shifted from the engaged state to the non-engaged state can be particularly moderated. . Although the above description has been made with a focus on one power transmission unit 20, in the continuously variable transmission 1, the turning radius adjusting mechanisms 4 of the six power transmission units 20 are arranged by changing the phase by 60 degrees each. Therefore, the output shaft 3 is sequentially rotated by the six power transmission units 20.

  As described above, according to this embodiment, the outer member 71 of the one-way clutch 17 has a split structure, and surface pressure is generated between the first outer member 75 and the second outer member 76 when torque is not transmitted. The outer peripheral surface 75c of the first outer member 75 and the inner peripheral surface of the second outer member 76 when the roller 25 engages with the wedge portion W during torque transmission and the first outer member 75 expands in diameter. Since the surface pressure is generated between the one-way clutch 17 and the one-way clutch 17 from the engaged state to the non-engaged state, the time change of the torque can be moderated, and the torque changes suddenly. Can suppress vibrations.

  Further, by making the first outer member 75 and the second outer member 76 a clearance fit, the outer peripheral surface 75c of the first outer member 75 and the inner peripheral surface 76c of the second outer member 76 can be reliably transmitted when torque is not transmitted. It is possible to configure so that no surface pressure is generated between them.

  Further, since the second outer member 76 only needs to be coupled by the coupling member 79 with the second outer member piece 80 functioning as at least two or more rigid members, assembly can be facilitated. In the one-way clutch 17 according to the second embodiment, since the second outer member 76 can move independently of the movement of the swing link 18 integrated with the first outer member 75, the setting of the axis is not necessary. .

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 above embodiment, the outer member 71 has a divided structure, but as shown in FIG. 11, the inner member 72 may have a divided structure. In the example shown in FIG. 11, the cylindrical inner member 72 that is integrally formed with the output shaft 3 in the above embodiment is replaced with a first inner member 81 that is integrally formed with the output shaft 3, and a cylindrical second inner member. 82, and the second inner member 82 is disposed on the outer peripheral portion of the first inner member 81. Further, the first inner member 81 and the second inner member 82 are clearance-fitted, and a predetermined radial direction is provided between the outer peripheral surface 81a of the first inner member 81 and the inner peripheral surface 82a of the second inner member 82. A gap T is provided. The radial clearance T is set to be equal to or smaller than the amount of diameter reduction of the second inner member 82 accompanying the torque transmission of the one-way clutch 17, and when the one-way clutch 17 is not transmitting torque, It is set so that no surface pressure is generated between the inner peripheral surface 82a of the second inner member 82. On the other hand, when the torque of the one-way clutch 17 is transmitted, the roller 25 is engaged with the wedge portion W, and the inner peripheral surface 82a of the second inner member 82 is pushed radially inward by the roller 25 to reduce the diameter, whereby the first inner member. The radial clearance T between the outer peripheral surface 81a of 81 and the inner peripheral surface 82a of the second inner member 82 is eliminated, and the space between the outer peripheral surface 81a of the first inner member 81 and the inner peripheral surface 82a of the second inner member 82 is eliminated. Is set to generate surface pressure.

  As described above, the inner member 72 is divided, and a predetermined radial clearance T is provided between the outer peripheral surface 81a of the first inner member 81 and the inner peripheral surface 82a of the second inner member 82. Similar to the first and second embodiments, the time change of the torque when the one-way clutch 17 shifts from the engaged state to the non-engaged state can be moderated, and vibration due to a sudden change in torque can be suppressed. it can.

1 continuously variable transmission (vehicle power transmission device)
2 Input section (input shaft)
3 Output shaft 5 Cam disc (input shaft)
15 connecting rod 17 one-way clutch 20 power transmission unit 25 roller 71 outer member 71a inner peripheral surface (inner peripheral surface of outer member)
72 Inner member 72a Outer peripheral surface (outer peripheral surface of inner member)
75 First outer member 75b Key groove 76 Second outer member 76b Key groove 77 Key 79 Connecting member 80 Second outer member piece (rigid member)
ENG engine (drive source)
P1 Rotation center axis (axis of input shaft)
P3 Center of rotating disk (input side fulcrum)
P4 Output side fulcrum R1 Eccentricity T Radial gap W Wedge

Claims (6)

A plurality of power transmission units that shift the rotation of the input shaft connected to the drive source and transmit it to the output shaft are juxtaposed in the axial direction between the input shaft and the output shaft,
Each of the power transmission units is
An input side fulcrum that is variable in eccentricity from the axis of the input shaft and rotates with the input shaft;
An inner member, an outer member, said comprising a roller provided between the inner peripheral surface and the outer peripheral surface of the inner member of the outer member, and the cage for holding the roller, and the outer peripheral surface of the inner member A one-way clutch that engages the roller with a provided wedge and transmits torque from the input shaft to the output shaft;
An output side fulcrum provided on the outer member of the one-way clutch;
A vehicle power transmission device comprising: a connecting rod connecting the input side fulcrum and the output side fulcrum,
The outer member includes a first outer member on which the output fulcrum is formed, and a second outer member that is disposed on the inner periphery of the first outer member so as not to be relatively rotatable.
The first outer member and the second outer member are vehicle power transmission devices configured so that surface pressure is not generated when torque of the one-way clutch is not transmitted. The vehicle power transmission device according to claim 1,
A predetermined radial clearance is provided between the first outer member and the second outer member when torque of the one-way clutch is not transmitted,
The radial clearance is a vehicular power transmission device that is equal to or less than a diameter expansion amount of the second outer member accompanying torque transmission of the one-way clutch. The vehicle power transmission device according to claim 1 or 2,
The first outer member and the second outer member are vehicle power transmission devices configured to be relatively unrotatable by a key and a key groove. A plurality of power transmission units that shift the rotation of the input shaft connected to the drive source and transmit it to the output shaft are juxtaposed in the axial direction between the input shaft and the output shaft,
Each of the power transmission units is
An input side fulcrum that is variable in eccentricity from the axis of the input shaft and rotates with the input shaft;
An inner member, an outer member, and a roller. The roller is engaged with a wedge portion provided between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member, and A one-way clutch that transmits torque to the output shaft;
An output side fulcrum provided on the outer member of the one-way clutch;
A vehicle power transmission device comprising: a connecting rod connecting the input side fulcrum and the output side fulcrum,
The outer member includes a first outer member on which the output fulcrum is formed, and a second outer member disposed on an outer peripheral portion of the first outer member so as to avoid the output fulcrum,
The first outer member and the second outer member are vehicle power transmission devices configured so that surface pressure is not generated when torque of the one-way clutch is not transmitted. The vehicle power transmission device according to claim 4,
A predetermined radial clearance is provided between the first outer member and the second outer member when torque of the one-way clutch is not transmitted,
The radial clearance is a power transmission device for a vehicle, wherein the radial clearance is equal to or less than a diameter expansion amount of the first outer member accompanying torque transmission of the one-way clutch. The vehicle power transmission device according to claim 4 or 5,
The second outer member is a vehicle power transmission device in which at least two or more rigid members are coupled by a coupling member.

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