JP2017197128A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce vibration and gear noise of a planetary gear mechanism without causing an increase in the weight and size of a case.SOLUTION: A power transmission device 100 includes: a second planetary gear mechanism 20 having a second sun gear 21 connected to a first motor, a second carrier 23 connected to an engine and a second ring gear 22; a selectable one-way clutch 30 for selectively causing the second ring gear 22 to become a lock state; and a case 60 that has a cylindrical case body 61 having openings on both sides covered with a front cover 62 and a rear cover 63 and in which the first motor 2, a first planetary gear mechanism 10, the second planetary gear mechanism 20 and the selectable one-way clutch 30 are accommodated. A sensor support member 64 for supporting the second ring gear 22 is fastened to the case body 61.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a power transmission device.

  In Patent Document 1, in a power transmission device for a hybrid vehicle, when power output from an engine is transmitted to a drive wheel, a selectable one-way clutch that is a gear lock mechanism fixes a ring gear of the planetary gear mechanism to thereby fix the planetary gear mechanism. Is functioning as a speed increaser.

Japanese Patent Laying-Open No. 2015-077786

  In the power transmission device described in Patent Document 1, since the planetary gear mechanism is supported by the rear cover of the case, vibration generated by the planetary gear mechanism is transmitted to the rear cover via a support member (center support). Therefore, it is conceivable to increase the rigidity of the rear cover in order to reduce vibrations and gear noise of the planetary gear mechanism. However, as a result of increasing the rigidity, the weight of the rear cover increases and the size of the rear cover increases, so even if vibration and gear noise can be reduced, the weight of the case increases and the size of the case increases.

  The present invention has been made in view of the above, and an object of the present invention is to provide a power transmission device that can reduce vibration and gear noise of a planetary gear mechanism without increasing the weight or size of the case. .

  A power transmission device according to the present invention includes an engine, an electric motor, a first rotating element coupled to the electric motor, a second rotating element coupled to the engine, and a third rotating element that outputs power to drive wheels. A first planetary gear mechanism having: a sun gear connected to the electric motor; a carrier connected to the engine; a second planetary gear mechanism having a ring gear; and a rotational direction of the ring gear being restricted in one direction. A selectable one-way clutch that switches between a locked state and an unlocked state that allows the ring gear to rotate in both directions; and a cylindrical case body that is covered with cover members on both sides, and the electric motor, The first planetary gear mechanism, the second planetary gear mechanism, and a case for accommodating the selectable one-way clutch therein, and the second planetary gear mechanism. Center support that supports the ring gear of the gear mechanism, characterized in that it is fastened to the case body.

  In the power transmission device according to the present invention, since the ring gear of the second planetary gear mechanism is supported by the case body, the vibration generated by the second planetary gear mechanism is transmitted to the case body via the center support. Thereby, compared with the conventional structure which supports a ring gear with the cover member of a case, the reduction effect of a vibration and a gear noise is acquired. Further, since it is not necessary to increase the rigidity of the cover member in order to reduce vibration and gear noise of the second planetary gear mechanism, vibration and gear noise can be reduced without increasing the weight of the case and increasing the size.

FIG. 1 is a skeleton diagram illustrating a power transmission device according to an embodiment. FIG. 2 is a cross-sectional view showing the peripheral structure of the second planetary gear mechanism inside the case. FIG. 3 is a view for explaining a path through which vibration generated by the second planetary gear mechanism is transmitted to the case body. FIG. 4 is a cross-sectional view for explaining a power transmission device of a comparative example. FIG. 5 is a view for explaining the assembly of the power transmission device. FIG. 6 is a diagram for explaining the assemblability of the comparative example. FIG. 7 is a cross-sectional view for explaining a power transmission device according to a modification.

  Hereinafter, a power transmission device according to an embodiment of the present invention will be described in detail with reference to the drawings.

[1. Overall structure]
FIG. 1 is a skeleton diagram illustrating a power transmission device according to an embodiment. As shown in FIG. 1, a power transmission device 100 for a vehicle Ve includes a power split mechanism in addition to an engine (ENG) 1, a first motor (MG1) 2, and a second motor (MG2) 3 as a power source for traveling. 1, a second planetary gear mechanism 20 as a transmission unit, a selectable one-way clutch (hereinafter referred to as “SOWC”) 30 as a gear lock mechanism, a counter gear mechanism 40, and a differential gear mechanism 50. The engine 1 is constituted by a known internal combustion engine. Each of the motors 2 and 3 is a well-known motor / generator having a motor function and a power generation function, and is electrically connected to a battery (both not shown) via an inverter.

  In the power transmission device 100, the power output from the engine 1 is divided by the first planetary gear mechanism 10 into the first motor 2 side and the drive wheel 4 side. In particular, when power is transmitted from the engine 1 to the drive wheels 4, the second planetary gear mechanism 20 functions as a speed increaser by the SOWC 30 being locked and receiving an engine reaction force. Further, when the first motor 2 is caused to function as a generator by the power divided on the first motor 2 side, the electric power generated by the first motor 2 can be charged to the battery or supplied to the second motor 3. it can. The second motor 3 functions as a motor when supplied with electric power.

  As shown in FIG. 1, the input shaft 5 of the power transmission device 100 is connected to the crankshaft of the engine 1. The engine 1 is disposed outside the case 60 that houses the first motor 2 and the like. Inside the case 60, the first motor 2, the first planetary gear mechanism 10, the second planetary gear mechanism 20, and the SOWC 30 are arranged coaxially with the crankshaft of the engine 1. A second motor 3 and a mechanical oil pump (MOP) 70 are disposed on a shaft different from the crankshaft of the engine 1. The mechanical oil pump 70 is an oil pump driven by the engine 1.

  The first planetary gear mechanism 10 is constituted by a single pinion type planetary gear mechanism, and as the three rotating elements, a first sun gear 11, a first ring gear 12 disposed concentrically with respect to the first sun gear 11, And a first carrier 13 holding a pinion gear 14 meshing with the first sun gear 11 and the first ring gear 12 so as to be capable of rotating and revolving. The first rotor shaft 6 of the first motor 2 is connected to the first sun gear 11 as the first rotating element so as to rotate integrally. The first rotor shaft 6 is a hollow shaft, and the input shaft 5 is inserted therein. The engine 1 is connected to the first carrier 13 that is the second rotating element. The first carrier 13 rotates integrally with the input shaft 5. The first ring gear 12, which is a third rotating element, is an output element that outputs torque from the first planetary gear mechanism 10 to the drive wheel 4 side, and rotates integrally with the output gear 7.

  The output gear 7 is connected to the differential gear mechanism 50 via the counter gear mechanism 40. Torque output from the output gear 7 is transmitted to the left and right drive wheels 4 via the counter gear mechanism 40 and the differential gear mechanism 50.

  Further, in the power transmission device 100, the torque output from the second motor 3 can be added to the torque transmitted from the output gear 7 to the drive wheel 4. The second motor 3 has a second rotor shaft 8 arranged in parallel with the input shaft 5. A reduction gear 9 meshed with the counter driven gear of the counter gear mechanism 40 is attached to the second rotor shaft 8 so as to rotate integrally.

  The second planetary gear mechanism 20 is configured by a double pinion type planetary gear mechanism, and as the three rotating elements, a second sun gear 21, a second ring gear 22 disposed concentrically with respect to the second sun gear 21, And a second carrier 23 holding the first pinion gear 24 and the second pinion gear 25 so that they can rotate and revolve. A plurality of pinion gears 24 and 25 are provided, the first pinion gear 24 meshes with the second sun gear 21, and the second pinion gear 25 meshes with the first pinion gear 24 and the second ring gear 22.

  The first rotor shaft 6 of the first motor 2 is connected to the second sun gear 21 so as to rotate integrally. The engine 1 is connected to the second carrier 23. The second carrier 23 rotates integrally with the input shaft 5. In the relationship between the second planetary gear mechanism 20 and the first planetary gear mechanism 10, the second sun gear 21 rotates integrally with the first sun gear 11, and the second carrier 23 rotates integrally with the first carrier 13. The second ring gear 22 is a reaction force element that is selectively fixed (locked) by the SOWC 30 and rotates integrally with a notch plate 32 that is a rotating member of the SOWC 30.

  The SOWC 30 has a pocket plate 31 fixed to the case 60 (the case main body 61), and functions as a mechanism for handling the engine reaction force by locking the second ring gear 22. The SOWC 30 switches between a locked state in which the rotation direction of the second ring gear 22 is restricted to only one direction and an unlocked state in which the second ring gear 22 can rotate in both directions. For example, when the SOWC 30 is in the locked state, the second ring gear 22 is restricted from rotating in the forward direction. The forward direction is the same direction as the direction in which the crankshaft rotates while the engine 1 is being driven.

The case 60 is a cylindrical case body 61 that is open on both sides, a front cover 62 that is a cover member that covers an opening on the engine 1 side, and a cover member that covers an opening on the side opposite to the engine 1. And a rear cover 63. The front cover 62 is bolted to one end portion (end portion on the engine 1 side) of the case body 61 and integrated with the case body 61.
The rear cover 63 is bolted to the other end (the end opposite to the engine 1) of the case main body 61 and integrated with the case main body 61.

  The mechanical oil pump 70 has a pump drive gear 71, a pump driven gear 72, and a pump shaft 73. The pump drive gear 71 rotates integrally with the input shaft 5 and the second carrier 23 and meshes with the pump driven gear 72. The pump driven gear 72 is attached to the pump shaft 73 so as to rotate integrally. The pump shaft 73 is disposed on a different axis from the input shaft 5. The oil discharged from the mechanical oil pump 70 is supplied as lubrication oil to the lubrication required parts (the first planetary gear mechanism 10, the second planetary gear mechanism 20, the SOWC 30, etc.) inside the case 60.

[2. Detailed structure]
FIG. 2 is a cross-sectional view showing the peripheral structure of the second planetary gear mechanism 20 inside the case 60. As shown in FIG. 2, in the power transmission device 100, the second ring gear 22 of the second planetary gear mechanism 20 is supported by the case body 61 via the center support 64. That is, the power transmission device 100 is configured to receive the vibration generated by the second planetary gear mechanism 20 by the case body 61.

  The center support 64 is a support member that supports the rotating member inside the case 60, and is fastened to an end portion (a flange portion or the like) of the case main body 61 by a bolt 81. The portion of the case main body 61 where the center support 64 is fastened is included in the vicinity of the end where the case main body 61 and the rear cover 63 are fastened by the bolt 82, that is, in a highly rigid portion. Further, the fastening portion between the center support 64 and the case main body 61 is located radially inside the fastening portion between the rear cover 63 and the case main body 61. When assembling the power transmission device 100, the rear cover 63 is fastened to the case body 61 after the center support 64 is fastened. After the assembly, the center support 64 extends in the radial direction so as to form a partition in the case 60. The center support 64 is provided with a through hole in the radially inner portion, and a bearing 91 that receives a radial load from the ring gear flange 221 is fitted into the through hole. The outer peripheral portion (outer race) of the bearing 91 is fitted in the through hole of the center support 64, and the inner peripheral portion (inner race) of the bearing 91 is fitted in the ring gear flange 221.

  The ring gear flange 221 is a support member that supports the second ring gear 22, and is disposed on the radially inner side of the second ring gear 22. The ring gear flange 221 has a flange portion 221 a whose outer peripheral portion is spline-fitted with the second ring gear 22, and a boss portion 221 b whose outer peripheral portion is fitted with the bearing 91. The flange portion 221a extends radially outward from the boss portion 221b, and is provided between the carrier plate 233 and the center support 64 of the second carrier 23 in the axial direction. The boss portion 221 b is arranged so that the tip end portion is inserted into the through hole of the center support 64 and is a portion attached to the center support 64 via the bearing 91.

  In addition to the bearing 91, a rolling bearing 92 that supports the first rotor shaft 6 is fitted in the through hole of the center support 64. That is, the first rotor shaft 6 is supported by the center support 64. As shown in FIG. 2, the rolling bearing 92 is located closer to the engine 1 than the bearing 91. The outer race of the rolling bearing 92 is fitted into the through hole of the center support 64, and the inner race of the rolling bearing 92 is fitted to the outer peripheral portion of the first rotor shaft 6. Since the first rotor shaft 6 is a hollow shaft, the input shaft 5 is attached to the inner peripheral portion of the first rotor shaft 6 via a needle bearing 93. The “engine 1 side” means that the axial position is relatively on the engine 1 side (right side in FIG. 2). “Rear cover 63 side” means that the axial position is relatively opposite to the engine 1 (left side in FIG. 2).

  The first rotor shaft 6 extends to the rear cover 63 side from the portion where the rolling bearing 92 and the needle bearing 93 are fitted, and the tip portion thereof is located in the vicinity of the gear portion 211 of the second sun gear 21. . The second sun gear 21 is spline-fitted on the tip end side of the first rotor shaft 6. The second sun gear 21 has a gear part 211 and a boss part 212. The gear portion 211 is disposed closer to the rear cover 63 than the tip portion of the first rotor shaft 6. The boss portion 212 protrudes from the inner peripheral portion of the gear portion 211 toward the engine 1 in the axial direction, and the protruding portion is spline-fitted with the inner peripheral portion of the first rotor shaft 6. As shown in FIG. 2, the input shaft 5 and the second carrier 23 are spline-fitted at a portion (first spline portion) where the second sun gear 21 and the first rotor shaft 6 are spline-fitted. It is located closer to the engine 1 than the portion (second spline portion).

  The front end of the input shaft 5 protrudes from the first rotor shaft 6 toward the rear cover 63, and the second carrier 23 is spline fitted to the protruding portion. The second carrier 23 has an annular carrier body 231, a pinion shaft 232, and a disc-shaped carrier plate 233. The carrier body 231 includes a boss portion 231a formed on the inner peripheral portion and a carrier flange portion 231b extending from the rear cover 63 side of the boss portion 231a toward the radially outer side. The boss portion 231 a is spline-fitted with the outer peripheral portion of the input shaft 5. The carrier flange portion 231b is provided between the second sun gear 21 and the rear cover 63 in the axial direction. The pinion shaft 232 rotatably supports the first and second pinion gears 24 and 25, and one end portion thereof is attached to the carrier flange portion 231 b and the other end portion is attached to the carrier plate 233. The carrier plate 233 is disposed on the opposite side of the carrier flange portion 231b with respect to the pinion shaft 232 and the first and second pinion gears 24 and 25.

  Since the pump drive gear 71 is integrated with the outer peripheral portion of the carrier flange portion 231b, the power output from the engine 1 is transmitted to the pump driven gear 72 via the carrier body 231. The pump driven gear 72 is attached to the rear cover 63 side portion of the pump shaft 73 and rotates integrally with the pump rotor 74 attached to the engine 1 side portion of the pump shaft 73. The pump rotor 74 is provided inside the pump body 75. The pump body 75 is integrated with a center support 64 fixed to the case body 61. The pump body 75 and the center support 64 may be an integrally formed structure or separate bodies.

  A notch plate 32 is spline-fitted to the outer periphery of the second ring gear 22. The SOWC 30 is an annular gear lock mechanism, and is provided on the radially outer side of the second planetary gear mechanism 20. The SOWC 30 includes a pocket plate 31 that is a fixed member, a notch plate 32 that is a rotating member, a selector plate 33 that is a member that switches between a locked state and an unlocked state of the SOWC 30, and a strut 34 that is an engagement piece. I have. The pocket plate 31 is fastened to the center support 64 by bolts 83 and is supported by the case body 61 via the center support 64. The pocket plate 31 is provided with a plurality of pockets for accommodating struts (engagement pieces) 34 that engage with the notch plate 32 in portions facing the notch plate 32 and the selector plate 33 in the axial direction. A plurality of struts 34 are provided at positions spaced apart from each other in the circumferential direction of the pocket plate 31. The notch plate 32 is provided with a plurality of engaging recesses (notches) with which the struts 34 are engaged at circumferential positions corresponding to the struts 34. The selector plate 33 is a disk-shaped plate member disposed between the notch plate 32 and the pocket plate 31, and has a window hole (allowing the strut 34 on the pocket plate 31 side to protrude toward the notch plate 32 side). (Not shown) are provided in the circumferential direction. Further, the selector plate 33 is connected to an actuator (not shown) via an arm 35. When the force output from the actuator is transmitted to the selector plate 33 via the arm 35, the selector plate 33 rotates relative to the pocket plate 31 and the notch plate 32. As a result, the SOWC 30 can switch between the locked state and the unlocked state. For example, when the SOWC 30 is in an unlocked state, the strut 34 is pushed into the pocket on the pocket plate 31 side by the plate portion of the selector plate 33, so that the notch plate 32 does not engage with the strut 34 in both directions. It can be rotated. On the other hand, when the SOWC 30 is in the locked state, the strut 34 rises to the notch plate 32 side through the window hole of the selector plate 33. Therefore, the strut 34 is engaged with the notch plate 32 and the rotational direction is restricted to one direction. . An elastic member (not shown) that urges the strut 34 toward the notch plate 32 is provided between the strut 34 and the bottom of the pocket.

[3. Vibration transmission]
FIG. 3 is a view for explaining a path through which vibration generated by the second planetary gear mechanism 20 is transmitted to the case body 61. Since the second planetary gear mechanism 20 generates vibration and gear noise due to a gear meshing transmission error, the second planetary gear mechanism 20 becomes a source of vibration generation force inside the case 60. On the other hand, since the power transmission device 100 has a structure in which the second ring gear 22 is supported by the case main body 61, vibration generated by the second planetary gear mechanism 20 is transmitted to the case main body 61 via the center support 64. The Specifically, the vibration of the second planetary gear mechanism 20 is transmitted from the second ring gear 22 to the bearing 91 via the ring gear flange 221. As indicated by black arrows in FIG. 3, vibration is transmitted from the bearing 91 to the center support 64. That is, when vibration is transmitted to the center support 64 that is a fixed member, it is transmitted to the center support 64 directly (without a plurality of members) only through the bearing 91 that is in contact with the ring gear flange 221. 3, the vibration transmitted to the center support 64 is transmitted from the fastening portion between the center support 64 and the case main body 61 to the case main body 61. The case body 61 is a structure having higher rigidity than the rear cover 63. Therefore, in the power transmission device 100 in which the second planetary gear mechanism 20 is supported by the case body 61, the vibration is smaller than in the conventional structure in which the second planetary gear mechanism 20 is supported by the rear cover 63 (a comparative example shown in FIG. 4 described later). In addition, an effect of reducing gear noise can be obtained. The case body 61 and the rear cover 63 do not need to be structurally changed (for example, increased in thickness, etc.) so as to be more rigid than the conventional case body and rear cover. Further, the case main body is often a structure having higher rigidity than the rear cover (cover member) even in the conventional structure as well as the embodiment. Therefore, it is not necessary to change the structure described above, the cost can be suppressed, and weight and size are not increased.

  FIG. 4 is a cross-sectional view for explaining a power transmission device 300 of a comparative example. In the description of this comparative example, the description of the same configuration as that of the power transmission device 100 of the embodiment is omitted, and the reference numerals thereof are cited. As shown in FIG. 4, in the power transmission device 300 of the comparative example, unlike the power transmission device 100 of the embodiment, the second ring gear 22 is supported by the rear cover 63. In addition, it has a center support 65 fastened to the rear cover 63 by a bolt 84, and a needle bearing 94 provided between the ring gear flange 221 and the boss portion 63a of the rear cover 63. The ring gear flange 221 is disposed between the rear cover 63 and the second sun gear 21 (second carrier 23) in the axial direction, and is supported by the rear cover 63 via a needle bearing 94 that is a radial bearing. Specifically, the flange portion 221 a of the ring gear flange 221 is disposed between the rear cover 63 and the carrier body 231 of the second carrier 23 in the axial direction. The outer race of the needle bearing 94 is fitted to the inner peripheral portion of the boss portion 221b. A boss portion 63 a of the rear cover 63 protrudes toward the input shaft 5 in the axial direction, and a tip portion thereof is inserted (fitted) into the input shaft 5. The pump driven gear 72 is attached to the engine 1 side portion of the pump shaft 73, and the pump rotor 74 is attached to the rear cover 63 side portion of the pump shaft 73. The pump shaft 73 is rotatably supported by the center support 65. In the comparative example, the vibration generated in the second planetary gear mechanism 20 of the vibration generating source surrounded by the broken line shown in FIG. 4 is changed from the second ring gear 22 to the ring gear flange 221 and It is transmitted to the rear cover 63 via the needle bearing 94 and also transmitted to the rear cover 63 from the center support 65 via the fastening portion by the bolt 84. In this case, since the rear cover 63 has lower rigidity than the case main body 61 (vibration transmission sensitivity is poor), film vibration of the rear cover 63 may be excited by vibration transmitted from the second planetary gear mechanism 20 to the rear cover 63. There is. In short, the power transmission device 100 of the embodiment has a greater effect of reducing vibration and gear noise of the second planetary gear mechanism 20 than this comparative example. In the comparative example, a radial load acting on the second ring gear 22 from the SOWC 30 is received by the rear cover 63 via the ring gear flange 221.

[4. Assembly]
FIG. 5 is a view for explaining the assembling property of the power transmission device 100. FIG. 6 is a diagram for explaining the assemblability of the comparative example. When assembling the power transmission devices 100 and 300, components are placed so that the horizontal direction shown in FIGS. 5 and 6 is the actual horizontal direction, and the components shown in FIGS. 5 and 6 are shown. Assemble another component from the assembly direction of the white arrow. That is, the constituent members are assembled from the lower side to the upper side in the direction orthogonal to the horizontal direction shown in FIGS.

  As shown in FIG. 5, in the embodiment, the center support 64 is fastened to the case main body 61. Thereby, when the power transmission device 100 is assembled, the first spline part (spline fitting part between the second sun gear 21 and the first rotor shaft 6) surrounded by the broken line shown in FIG. 5 and the one-dot chain line shown in FIG. The second spline part (spline fitting part between the second carrier 23 and the input shaft 5) surrounded by (2) can be separately assembled (engaged). Specifically, the center support 64 is first fastened to the case body 61 before the first spline part and the second spline part are fitted. After the center support 64 is fastened to the case body 61, the second sun gear 21 is assembled to the first rotor shaft 6 in a state where the mesh with the first pinion gear 24 is released. That is, since the second sun gear 21 and the second carrier 23 can be assembled separately, first, the first spline portion is in a fitted state. Then, after the second sun gear 21 is assembled to the first rotor shaft 6, the second carrier 23 is assembled to the input shaft 5. That is, in a state where the first spline portion is already fitted, the second spline portion formed by the second carrier 23 and the input shaft 5 is in a fitted state. Thereafter, the rear cover 63 is fastened to the case body 61. Thus, since the simultaneous meshing of the first spline portion and the second spline portion can be eliminated when the power transmission device 100 is assembled, the assembling work is facilitated and the assembling property is improved. That is, since the rear cover 63 and the second planetary gear mechanism 20 are not unitized, the assembling work is facilitated.

  On the other hand, as shown in FIG. 6, in the comparative example, the center support 65 is fastened to the rear cover 63. That is, the components on the rear cover 63 side (including the second planetary gear mechanism 20, SOWC 30, rear cover 63, center support 65, mechanical oil pump 70, etc.) are assembled in a united state. Thus, when the power transmission device 300 is assembled, the component members on the side of the rear cover 63 are assembled to the first rotor shaft 6 and the input shaft 5 at the same time. In this case, since the two locations of the first spline portion and the second spline portion are assembled at the same time, simultaneous engagement becomes necessary, and the assembly work is not easy.

  As described above, in the power transmission device 100, since the second ring gear 22 is supported by the case body 61, vibration generated in the second planetary gear mechanism 20 is transmitted to the case body 61 via the center support 64. . Thereby, compared with the conventional structure (comparative example) which supports the 2nd planetary gear mechanism with the rear cover 63, the reduction effect of a vibration and gear noise can be acquired. Further, since the case body 61 is a structure having higher rigidity than the rear cover 63, it is not necessary to increase the rigidity of the rear cover 63, and the case 60 does not increase in weight or size.

  Further, since the second ring gear 22 is not supported by the rear cover 63 in the power transmission device 100, it is possible to suppress the membrane vibration of the rear cover 63 from being excited by the vibration generated by the second planetary gear mechanism 20. Thereby, it is possible to suppress the occurrence of vibration and noise of the rear cover 63 due to the vibration of the second planetary gear mechanism 20.

  Further, since a plurality of struts 34 are arranged in the circumferential direction in the SOWC 30, not all the struts 34 are uniformly engaged (engaged) with the notch plate 32 in the locked state. If each strut 34 meshes unevenly, a radial load is generated at the SOWC 30. Even when the SOWC 30 is in a locked state, if any of the struts 34 is not engaged with the notch plate 32, a moment that decenters the center of the notch plate 32 is generated and a radial load is generated in the SOWC 30. The radial load acts on the second ring gear 22 from the notch plate 32. On the other hand, in the power transmission device 100, since the second ring gear 22 is supported by the case main body 61 via the support members (ring gear flange 221, bearing 91, center support 64), the radial load generated by the SOWC 30 is reduced. It can be received by the case body 61. That is, since the radial load generated in the SOWC 30 does not act on the second carrier 23 from the second ring gear 22 as an eccentric load, misalignment of the second carrier 23 can be suppressed. Thereby, in the configuration having the SOWC 30, it is possible to suppress the vibration and gear noise of the second planetary gear mechanism 20 from deteriorating.

  Note that the structure is not limited to a structure in which vibration is directly transmitted from the ring gear flange 221 to the center support 64, and as a modification, a structure in which vibration is transmitted through a plurality of members may be used. FIG. 7 is a cross-sectional view for explaining a power transmission device according to a modification. In the description of the modified example, the description of the same configuration as that of the above-described embodiment is omitted, and the reference numerals thereof are cited. As shown in FIG. 7, in the power transmission device 100 according to the modification, a needle bearing 95 is provided instead of the bearing 91 of the above-described embodiment. The support structure from the second ring gear 22 to the case body 61 includes a ring gear flange 221, a needle bearing 95, a first rotor shaft 6, a rolling bearing 92, and a center support 64. Specifically, the ring gear flange 221 is attached to the first rotor shaft 6 via the needle bearing 95. The needle bearing 95 is fitted to a portion of the first rotor shaft 6 that protrudes closer to the rear cover 63 than the portion to which the rolling bearing 92 is fitted. In this case, the vibration of the second planetary gear mechanism 20 is transmitted from the second ring gear 22 to the needle bearing 95 via the ring gear flange 221. Then, it is transmitted from the needle bearing 95 to the center support 64 via the first rotor shaft 6 and the rolling bearing 92. The vibration transmitted to the center support 64 is transmitted to the case body 61 from the fastening portion between the center support 64 and the case body 61.

  In the embodiment and the modification described above, the second ring gear 22 and the ring gear flange 221 are configured as separate members. However, the power transmission device 100 includes a ring gear flange formed integrally with the second ring gear 22. Also good.

1 Engine 2 First Motor 10 First Planetary Gear Mechanism 11 First Sun Gear (First Rotating Element)
12 First ring gear (third rotating element)
13 First carrier (second rotating element)
20 Second planetary gear mechanism 21 Second sun gear 22 Second ring gear 23 Second carrier 30 Selectable one-way clutch (SOWC)
60 Case 61 Case body 63 Rear cover 64 Center support 81 Bolt 91 Bearing 100 Power transmission device

Claims (1)

Engine,
An electric motor,
A first planetary gear mechanism having a first rotating element coupled to the electric motor, a second rotating element coupled to the engine, and a third rotating element that outputs power to a drive wheel;
A second planetary gear mechanism having a sun gear coupled to the electric motor, a carrier coupled to the engine, and a ring gear;
A selectable one-way clutch that switches between a locked state that restricts the rotational direction of the ring gear in one direction and an unlocked state that allows the ring gear to rotate in both directions;
A case body having a cylindrical case body whose openings on both sides are covered by a cover member; and housing the electric motor, the first planetary gear mechanism, the second planetary gear mechanism, and the selectable one-way clutch inside,
With
A power transmission device, wherein a center support supporting the ring gear of the second planetary gear mechanism is fastened to the case body.

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