JP2013224712A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device reduced in friction produced between a gear and a support member for supporting the end face of the gear in power transmission devices each with a plurality of gears.SOLUTION: In a power transmission device, a pinion gear 4e rotates in a first rotation direction when a vehicle moves forward; a gear tooth 22 is formed to approach the second end face 29b side as it approaches the first rotation direction when the gear tooth 22 is viewed from a location apart from the circumferential surface of the pinion gear 4e; a first support part contains a first support plate 30 for supporting a first end face 29a, a second support plate disposed apart from the first support plate 30 in a pinion shaft extended direction, and a plurality of rotating members disposed between the first support plate 30 and the second support plate 36 and relatively rotatably supporting with the first support plate 30 and the second support plate 36; and a second support part is a plated member.

Description

  The present invention relates to a power transmission device.

  Conventionally, various power transmission devices such as planetary gear devices have been proposed. Various planetary gear mechanisms have been proposed in Japanese Patent Application Laid-Open Nos. 2011-132880 and 2008-261398.

  For example, a planetary gear device described in Japanese Patent Application Laid-Open No. 2000-337484 includes a pinion gear, a washer provided on an end face of the pinion gear, and a needle bearing disposed on the inner periphery of the pinion gear.

  Lubricating oil is supplied to the needle bearing, and the lubricating oil supplied to the needle bearing is also supplied between the washer and the pinion gear. An oil sump hole is formed in the washer so as to reduce the rotational resistance of the pinion gear.

JP 2011-132880 A JP 2008-261398 A JP 2000-337484 A

  The inventors have found a problem that when the planetary gear mechanism is driven, a thrust load is applied to the pinion gear, and the pinion gear shifts in the direction of the rotation axis.

  For this reason, for example, in the planetary gear mechanism described in Japanese Patent Laid-Open No. 2000-337484, if the pinion gear shifts in the direction of the rotation axis, the friction coefficient between the washer and the pinion gear increases, and the driving efficiency is significantly reduced. Problems arise.

  The above-described problem is not limited to the planetary gear mechanism, and a similar problem occurs in a power transmission device in which a plurality of gears mesh with each other.

  The present invention has been made in view of the above-described problems, and an object thereof is friction generated between a gear and a support member that supports an end face of the gear in a power transmission device including a plurality of gears. It is an object of the present invention to provide a power transmission device in which the reduction of the above is achieved.

  A power transmission device according to the present invention includes a pinion shaft, a pinion gear that is formed in a cylindrical shape and rotatably provided on the pinion shaft, and includes a first end surface and a second end surface that are arranged in the extending direction of the pinion shaft, and a plurality of pinion gears And a roller bearing provided between the inner peripheral surface of the pinion gear and the outer peripheral surface of the pinion shaft. The power transmission device includes a tooth portion formed on the outer peripheral surface of the pinion gear, a sun gear meshing with the tooth portion, a first support portion disposed on the first end surface side with respect to the pinion gear, and supporting the first end surface, and the pinion gear And a second support portion that is disposed on the second end face side and supports the second end face. The pinion gear rotates in the first rotation direction when the vehicle moves forward. When the tooth part is viewed from a position away from the peripheral surface of the pinion gear, the tooth part is formed so as to go to the second end face side as it goes to the first rotation direction. A first support plate that supports the first end surface, a second support plate that is spaced apart in the direction in which the first support plate and the pinion shaft extend, and a gap between the first support plate and the second support plate. And a plurality of first rotating members that are disposed and support the first supporting plate and the second supporting plate so as to be rotatable relative to each other. The second support part is a plate-like member. When the tooth portion is formed so as to be directed toward the second end face as it goes in the direction opposite to the first rotation direction when the tooth portion is viewed from a position away from the peripheral surface of the pinion gear, the first support is provided. The portion is a plate-like member, and the second support portion is a third support plate that supports the second end surface, and a fourth support plate that is disposed with an interval in the extending direction of the third support plate and the pinion shaft. And a plurality of second rotating members that are disposed between the third support plate and the fourth support plate and support the third support plate and the fourth support plate so as to be rotatable relative to each other.

  According to the power transmission device of the present invention, it is possible to reduce the friction generated between the gear and the support member that supports the gear.

It is sectional drawing which shows the planetary gear apparatus 4 which concerns on this Embodiment. 2 is an exploded perspective view of a thrust bearing 30. FIG. 3 is a perspective view showing a washer 36. FIG. 2 is an exploded perspective view of a thrust bearing 50. FIG. It is a figure when the 2nd sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d are seen from the direction away from the peripheral surface of the 2nd sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d. It is a schematic diagram which shows typically the short pinion gear 4e and the pinion shaft 20. FIG. It is a schematic diagram which shows typically the attitude | position of the short pinion gear 4e and the pinion shaft 20 at the time of a drive. It is a schematic diagram which shows the relationship between the inclination angle of the needle 24 with respect to the pinion shaft 20, the rotational direction R, and the thrust force P3. It is sectional drawing which shows the modification of the short pinion gear 4e. It is a front view which shows the modification of the washer 36. FIG. It is sectional drawing which shows the transmission 1 which concerns on a modification. In the transmission 1 shown in FIG. 11, the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d are viewed from the direction away from the peripheral surfaces of the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d.

An embodiment according to the present invention will be described with reference to FIGS.
FIG. 1 is a cross-sectional view showing a planetary gear device 4 according to the present embodiment. As shown in FIG. 1, the planetary gear device 4 is mounted on a vehicle and functions as a transmission, for example. The planetary gear device 4 includes a center shaft 3, a first sun gear 4a, a second sun gear 4b, a carrier 4c, a long pinion gear 4d, a short pinion gear 4e, and a ring gear 4f.

  The short pinion gear 4e and the long pinion gear 4d are supported by the carrier 4c. The first sun gear 4a meshes with the long pinion gear 4d, and the second sun gear 4b meshes with the short pinion gear 4e. The short pinion gear 4e meshes with the long pinion gear 4d.

  The ring gear 4f meshes with the long pinion gear 4d, and the long pinion gear 4d is connected to the output shaft 5. In the center shaft 3, an oil supply hole 10 extending in the axial direction of the center shaft 3 and a plurality of oil supply holes 11 reaching the outer peripheral surface of the center shaft 3 from the oil supply hole 10 are formed.

  The second sun gear 4 b includes a base portion 12 that is rotatably provided on the outer peripheral surface of the center shaft 3, and a plurality of tooth portions 13 that are formed on the outer peripheral surface of the base portion 12.

  The first sun gear 4 a includes a cylindrical base portion 14 provided on the outer peripheral surface of the cylindrical base portion 12 and a plurality of tooth portions 15 formed on the outer peripheral surface of the base portion 14.

  The carrier 4 c includes an end surface portion 16, an end surface portion 17 disposed at a distance from the end surface portion 16 in the axial direction of the center shaft 3, and a guide plate 18 provided on the end surface portion 16.

  The end surface portion 16 is formed with a hole portion 16a and a hole portion 16b, and the end surface portion 17 is formed with a hole portion 17a and a hole portion 17b.

  The pinion shaft 20 is inserted into the hole portion 16a and the hole portion 17a, and the pinion shaft 20 is provided so as to engage with the end surface portion 16 and the end surface portion 17 so as not to rotate. The second sun gear 4b is provided at a position closer to the end surface portion 16 of the carrier 4c than the first sun gear 4a. Second sun gear 4 b includes an end surface 19 that faces end surface portion 16.

  An oil supply hole 26 extending in the axial direction of the pinion shaft 20 and an oil supply hole 27 connected to the oil supply hole 26 and reaching the outer peripheral surface of the pinion shaft 20 are formed in the pinion shaft 20.

  The oil supply hole 26 is formed so as to reach the end face of the pinion shaft 20, and an opening 28 is formed in the end face of the pinion shaft 20. The opening 28 is formed to face the guide plate 18.

  A needle bearing 23 is provided on the outer peripheral surface of the pinion shaft 20. The needle bearing 23 includes a plurality of needles (rollers) 24 and a holder 25 that holds the needles 24 and maintains the interval between the needles 24. In the present embodiment, a needle bearing is employed as one of the roller bearings, but other types of roller bearings may be employed.

  The short pinion gear 4 e is provided on the outer periphery of the needle bearing 23, and is rotatably provided on the pinion shaft 20 by the needle bearing 23. The short pinion gear 4e includes a base portion 21 formed in a cylindrical shape and a plurality of tooth portions 22 formed on the outer peripheral surface of the base portion 21.

  Short pinion gear 4e includes an end surface 29a arranged in the axial direction of pinion shaft 20 and an end surface 29b. The end surface 29 a faces the end surface portion 16, and the end surface 29 b faces the end surface portion 17.

  A thrust bearing 30 is arranged between the end surface of the base portion 21 on the end surface 29 a side and the end surface portion 16. A washer 36 is disposed between the end surface 29 b side end surface of the base portion 21 and the end surface portion 17. The washer 36 is an example of a sliding bearing.

  FIG. 2 is an exploded perspective view of the thrust bearing 30. As shown in FIG. 2, the thrust bearing 30 includes a plurality of balls 31 arranged in an annular shape, a holding portion 32 that holds an interval between the balls 31, an end face plate 33 and an end face plate that sandwich the balls 31 and the holding portion 32. 34.

  The end face plate 33 is formed with a groove 35 that extends in an annular shape and receives the ball 31, and the end face plate 34 is also formed with a similar annular groove.

  By rotating the ball 31 as the rotating member, the end face plate 33 and the end face plate 34 are rotatable relative to each other.

  The end face plate 34 supports the end face 29a of the short pinion gear 4e shown in FIG. The end face plate 33 is supported by the carrier 4c. When the short pinion gear 4e rotates, the end face plate 34 also rotates.

  FIG. 3 is a perspective view showing the washer 36. As shown in FIG. 3, the washer 36 is a plate-like member. The washer 36 is formed in an annular shape. The washer 36 includes a main surface 36a and a main surface 36b arranged in the thickness direction. The main surface 36a of the washer 36 supports the end surface 29b of the short pinion gear 4e.

  In FIG. 1, a pinion shaft 40 is inserted into the hole 16b and the hole 17b. The end of the pinion shaft 40 on the hole 17 a side is fixed to the end surface portion 17 by a pin 46. For this reason, the pinion shaft 40 is restricted from rotating and being displaced in the axial direction of the pinion shaft 40.

  A needle bearing 41 is provided on the outer peripheral surface of the pinion shaft 40. The needle bearing 41 includes a plurality of needles 42 arranged on the outer peripheral surface of the pinion shaft 40, and a holder 43 that holds an interval between the needles 42.

  The long pinion gear 4 d is provided on the outer peripheral surface of the needle bearing 41. For this reason, the long pinion gear 4 d is rotatably provided on the pinion shaft 40 by the needle bearing 41.

  The long pinion gear 4 d includes a base portion 44 formed in a cylindrical shape and a plurality of tooth portions 45 formed on the outer peripheral surface of the base portion 44. A needle bearing 41 is disposed between the inner peripheral surface of the base portion 44 and the outer peripheral surface of the pinion shaft 40.

  Long pinion gear 4d includes an end surface 56a and an end surface 56b arranged in the axial direction of pinion shaft 40. The end surface 56a is positioned on the end surface portion 16 side, and the end surface 56b is positioned on the end surface portion 17 side.

  A thrust bearing 50 is disposed between the end surface 56 b side end surface of the base portion 44 and the end surface portion 17. A washer 57 is disposed between the end face on the end face 56 a side of the base portion 44 and the end face portion 16.

  FIG. 4 is an exploded perspective view of the thrust bearing 50. As shown in FIG. 4, the thrust bearing 50 includes a plurality of balls 51 arranged in an annular shape, a holding tool 52 that holds a space between the balls 51, an end face plate 53 and an end face plate that sandwich the balls 51 and the holding tool 52. 54.

  The end face plate 53 is formed with an annular groove portion 55 for receiving the plurality of balls 51, and the end face plate 54 is also formed with the same groove portion.

  In FIG. 1, an oil supply hole 47 extending in the axial direction of the pinion shaft 40 and an oil supply hole 48 connected to the oil supply hole 47 and reaching the outer peripheral surface of the pinion shaft 40 are formed in the pinion shaft 40.

  The oil supply hole 48 reaches the end surface of the pinion shaft 40, and an opening 49 is formed in the end surface of the pinion shaft 40. The opening 49 faces the guide plate 18.

  Ring gear 4f includes a base portion 60 formed in an annular shape so as to cover long pinion gear 4d and short pinion gear 4e, and a plurality of tooth portions 61 formed on the inner peripheral surface of base portion 60. The base 60 is connected to the output shaft 5 by a connecting portion 62 formed in a plate shape. Between the connecting portion 62 and the carrier 4c, a fluid flow path 63 through which lubricating oil can flow is formed.

  The tooth part 61 meshes with the tooth part 45 formed in the long pinion gear 4d. In addition, the tooth part 61 is arrange | positioned at intervals from the tooth part 22 of the short pinion gear 4e, and the tooth part 61 and the tooth part 22 are not meshing.

  A carrier cover 65 is integrally connected to the end surface portion 17 of the carrier 4c. The carrier cover 65 is formed in a drum shape so as to surround the outer periphery of the ring gear 4f. The carrier cover 65 includes a clutch hub 66 that engages with a brake clutch plate, and an inner ring portion 67 that constitutes an inner ring of the one-way clutch.

  First, the flow of oil when the planetary gear device 4 configured as described above is driven will be described. In FIG. 1, power is applied to the center shaft 3 and the center shaft 3 rotates. Oil is supplied into the oil supply hole 10 from an oil pump (not shown).

  The oil supplied into the oil supply hole 10 is ejected from the oil supply hole 11 to the outside of the center shaft 3. Of the plurality of oil supply holes 11, the oil ejected from the oil supply holes 11 a passes through the oil flow path 63.

  Part of the oil flowing in the flow oil passage 63 enters the oil supply hole 26 of the pinion shaft 20 by the guide plate 18.

  The oil that has entered the oil supply hole 26 is supplied from the oil supply hole 27 to the needle bearing 23. After flowing through the needle bearing 23, the oil is supplied between the thrust bearing 30 and the short pinion gear 4 e and into the thrust bearing 30. Then, it flows outside the planetary gear unit 4.

  The oil that has flowed through the needle bearing 23 also enters between the washer 36 and the short pinion gear 4e.

  Part of the oil flowing in the oil flow passage 63 is guided by the guide plate 18 and enters the oil supply hole 47. The oil that has entered the oil supply hole 47 then enters the needle bearing 41 from the oil supply hole 48. The oil that has entered the needle bearing 41 enters between the thrust bearing 50 and the long pinion gear 4 d and into the thrust bearing 50. Similarly, it enters between the washer 57 and the long pinion gear 4d.

  In this way, the oil goes around the planetary gear unit 4 so that each part is lubricated and each part is cooled.

  Next, driving of each gear when the vehicle on which the transmission 1 is mounted moves forward will be described. FIG. 5 is a schematic diagram showing an engaged state of the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d. FIG. 5 shows the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d as viewed from the direction away from the peripheral surfaces of the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d.

  As shown in FIG. 5, the second sun gear 4b and the short pinion gear 4e mesh with each other, and the short pinion gear 4e and the long pinion gear 4d mesh with each other. Furthermore, the long pinion gear 4d is engaged with the ring gear 4f.

  When the transmission 1 is set to the forward gear, the second sun gear 4b rotates in the rotation direction R1. Then, the short pinion gear 4e rotates in the rotation direction R2, and the long pinion gear 4d rotates in the rotation direction R3.

  The tooth portion 22 of the short pinion gear 4e is formed so as to go from the end surface 29a to the end surface 29b in the rotational direction R2.

  The tooth portion 13 of the second sun gear 4b is formed so as to be separated from the end surface 19 in the rotational direction R1.

  The tooth portion 45 of the long pinion gear 4d is formed so as to move away from the end surface 56a and approach the end surface 56b as it goes in the rotation direction R3.

  Then, when the tooth portion 13 of the second sun gear 4b and the tooth portion 22 of the short pinion gear 4e are engaged, when the second sun gear 4b rotates in the rotation direction R1, the tooth portion 22 of the short pinion gear 4e extends from the tooth portion 13. Is loaded.

  Thereby, as shown in FIG. 6, a thrust force P1 is applied to the short pinion gear 4e from the second sun gear 4b.

  In FIG. 5, the short pinion gear 4e meshes with the long pinion gear 4d, and the tooth portion 22 of the short pinion gear 4e receives a load from the tooth portion 45 of the long pinion gear 4d. Therefore, as shown in FIG. 6, a thrust force P2 is applied to the short pinion gear 4e.

  As shown in FIG. 6, a moment M1 is generated in the short pinion gear 4e by the thrust force P1 and the thrust force P2.

  In FIG. 7, the short pinion gear 4e is inclined with respect to the pinion shaft 20 by the moment M1.

  Accordingly, the needle bearing 23 and the needle 24 provided on the needle bearing 23 are also tilted with respect to the pinion shaft 20. Further, the needle 24 on the front side of the paper is strongly subjected to the load by the load received by the tooth portion 22.

  FIG. 8 shows the relationship between the tilt angle of the needle 24 with respect to the pinion shaft 20, the rotational direction R2, and the thrust force P3. The short pinion gear 4e is displaced toward the direction D1 shown in FIG. 7 by the thrust force P3.

  In FIG. 1, when the short pinion gear 4 e is displaced in the direction D <b> 1, the end surface 29 a of the short pinion gear 4 e is pressed against the thrust bearing 30.

  Here, as shown in FIG. 2, the thrust bearing 30 includes a plurality of balls 31, and even when pressed by the thrust bearing 30, the friction coefficient between the thrust bearing 30 and the short pinion gear 4e is suppressed from increasing. Has been.

  For this reason, even if the short pinion gear 4e rotates at high speed, it is possible to suppress the occurrence of adverse effects such as burning of the short pinion gear 4e. Furthermore, the power transmission efficiency of the transmission 1 can be improved.

  On the other hand, as shown in FIG. 1, the end surface 29b of the short pinion gear 4e is supported by a washer 36 which is a sliding bearing.

  When the transmission 1 configures at least one of the plurality of forward gears, the short pinion gear 4e is easily displaced in the direction D1 as described above.

  For this reason, it can suppress that the surface pressure between the end surface 29b and the short pinion gear 4e becomes large. For this reason, even when the rotation speed of the short pinion gear 4e is small, it is possible to suppress an increase in the friction coefficient between the short pinion gear 4e and the washer 36.

  FIG. 10 is a front view showing a modified example of the washer 36. As shown in FIG. 10, a plurality of grooves 36 c extending in the radial direction may be formed on the main surface 36 a of the washer 36. By forming such a groove portion 36c, an oil film is easily formed between the washer 36 and the short pinion gear 4e. Thereby, the friction between the washer 36 and the short pinion gear 4e can be reduced.

  FIG. 9 is a cross-sectional view showing a modification of the short pinion gear 4e. In the example shown in FIG. 9, the short pinion gear 4e is formed with a through hole 70 into which the pinion shaft 20 is inserted.

  The through hole 70 includes a hole main body 71 and a taper 72 that is connected to the hole main body 71 and is formed so as to increase in diameter toward the end surface 29a. The taper 72 extends in an annular shape.

  Thus, according to the formed short pinion gear 4e, a large amount of oil is supplied between the end face 29a and the thrust bearing 30 by the taper 72. Thereby, the friction between the thrust bearing 30 and the end surface 29a can be reduced.

  In particular, the thrust bearing 30 allows oil to pass more easily than a sliding bearing such as the washer 36. For this reason, the amount of oil supplied between the thrust bearing 30 and the short pinion gear 4e is made larger than the amount of oil supplied between the washer 36 and the short pinion gear 4e, so that the short pinion gear 4e and the thrust bearing 30 It can suppress that image sticking arises between.

  The transmission 1 according to the present embodiment will be described with reference to FIG. 11 and FIG. Of the configurations shown in FIGS. 11 and 12, the same or corresponding components as those shown in FIGS. 1 to 10 may be assigned the same reference numerals and descriptions thereof may be omitted.

  FIG. 11 is a cross-sectional view showing a transmission 1 according to a modification. In the example shown in FIG. 11, a washer 36 is provided on the end surface 29a of the short pinion gear 4e. A thrust bearing 30 is provided on the end surface 29b of the short pinion gear 4e.

  12 shows the transmission 1 shown in FIG. 11 when the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d are viewed from the direction away from the peripheral surfaces of the second sun gear 4b, the short pinion gear 4e, and the long pinion gear 4d. FIG.

  In the example shown in FIG. 12, the tooth portion 13 of the second sun gear 4b is formed so as to approach the end surface 19 as it goes in the rotation direction R1. The tooth portion 22 of the short pinion gear 4e is formed so as to approach the end surface 29b as it goes in the direction opposite to the rotation direction R2. The tooth portion 45 of the long pinion gear 4d is formed so as to approach the end surface 56a as it goes in the rotation direction R3.

  As shown in FIG. 12, the end surfaces 19, 29a, and 56a facing the tooth portions 13, 22, and 45 in the rotational directions R1, R2, and R3 are respectively connected to the tooth portions 13, 22, and 45 shown in FIG. Are end faces that face each rotation direction R1, R2, R3, and opposite end faces.

  For this reason, the thrust force applied to the short pinion gear 4e shown in FIG. 12 is opposite to the thrust force applied to the short pinion gear 4e shown in FIG.

  As a result, the short pinion gear 4e is displaced in the direction D3 shown in FIG. 11 during driving. On the other hand, in the transmission 1 shown in FIG. 11, as described above, the end surface 29b of the short pinion gear 4e is supported by the thrust bearing 30, so that a large frictional force is generated on the end surface 29b of the short pinion gear 4e. This can be suppressed.

  The end surface 29a of the short pinion gear 4e is supported by a washer 36. Since no load is applied to the short pinion gear 4e so as to be pressed against the washer 36, even if the end face 29a is supported by the washer 36 of the plate-like member, the frictional force is unlikely to be excessive, but the washer 36 By supporting the end surface 29a, it is possible to prevent the lubricating oil from coming out of the needle bearing 23.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and is intended to include meanings equivalent to the scope of claims for patent and all modifications within the scope.

  The present invention is suitable for a power transmission device including a planetary gear mechanism.

  DESCRIPTION OF SYMBOLS 1 Transmission, 3 Center shaft, 4 Planetary gear apparatus, 4a 1st sun gear, 4b 2nd sun gear, 4c carrier, 4d Long pinion gear, 4e Short pinion gear, 4f Ring gear, 5 Output shaft 10, 11, 11a, 26, 27 , 47, 48 Refueling hole, 12, 14, 21, 44, 60 Base, 13, 15, 22, 45, 61 Tooth, 14 Cylindrical base, 16, 17 End face, 16a, 16b, 17a, 17b Hole , 18 Guide plate, 19, 29a, 29b, 56a, 56b End face, 20, 40 Pinion shaft, 23, 41 Needle bearing, 24, 42 Needle, 25, 52 Holder, 28, 49 Opening, 30, 50 Thrust bearing , 31, 51 ball, 32 holding part, 33, 34, 53, 54 end face plate, 35, 36c, 5 groove part, 36 washer, 36a, 36b main surface, 57 washer, 62 connection part, 63 fluid flow path, 65 carrier cover, 66 clutch hub, 67 inner ring part, 70 through hole, 71 hole body, 72 taper, B2 brake, D1 direction, F direction clutch, M1 moment, P1, P2, P3 thrust force, P5, P6 component force, R1, R2, R3 rotation direction.

Claims (1)

A pinion shaft,
A pinion gear formed in a cylindrical shape and rotatably provided on the pinion shaft and including a first end surface and a second end surface arranged in a direction in which the pinion shaft extends;
A roller bearing including a plurality of rollers, provided between an inner peripheral surface of the pinion gear and an outer peripheral surface of the pinion shaft;
Teeth formed on the outer peripheral surface of the pinion gear;
A sun gear meshing with the tooth portion;
A first support part disposed on the first end face side with respect to the pinion gear and supporting the first end face;
A second support part disposed on the second end face side with respect to the pinion gear and supporting the second end face;
Comprising a power transmission device mounted on a vehicle,
The pinion gear rotates in a first rotation direction when the vehicle moves forward,
When the tooth part is formed so as to go to the second end face side in the first rotation direction when the tooth part is viewed from a position away from the peripheral surface of the pinion gear, 1 support part, the 1st support plate which supports the 1st end face, the 2nd support plate arranged at intervals in the direction where the 1st support plate and the pinion shaft extend, The 1st support plate, A plurality of first rotating members disposed between the second support plate and rotatably supported relative to the first support plate and the second support plate, wherein the second support portion is a plate; Shaped member,
When the tooth part is viewed from the position away from the peripheral surface of the pinion gear, when the tooth part is formed to face the second end face as it goes in the opposite direction to the first rotation direction, The first support portion is a plate-like member, and the second support portion is spaced apart in a direction in which the third support plate supporting the second end surface, the third support plate, and the pinion shaft extend. A plurality of fourth support plates disposed between the third support plate and the fourth support plate and rotatably supported relative to the third support plate and the fourth support plate; A power transmission device including two rotating members.

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