JP5502720B2 - Power transmission device - Google Patents

Description

  The present invention relates to a power transmission device, and in particular, a ring gear of a planetary gear mechanism and an input shaft to which power is transmitted from an internal combustion engine via a damper device with a torque limiter are supported by a single case via a bearing. The present invention relates to a power transmission device.

  2. Description of the Related Art Conventionally, as a power transmission device for a vehicle, there are a power transmission device for an electric vehicle and a hybrid power transmission device using an internal combustion engine and an electric motor in combination with those using an electric motor as a drive source. As a hybrid power transmission device, an internal combustion engine as a prime mover, a generator driven by the internal combustion engine, and a gear train that is drivingly connected to wheels via a differential device are connected via a planetary gear mechanism. Therefore, it is possible to mutually transmit power between the internal combustion engine, the generator, and the wheel, driving the generator by the internal combustion engine, assisting the driving force using the generator as a motor, starting the internal combustion engine, differential from the wheel It is known that the generator can be regenerated by an inertial driving force that returns to the planetary gear mechanism via the device according to the traveling state (for example, see Patent Document 1).

  The power transmission device includes an input shaft coupled to an output shaft of an internal combustion engine, an electric motor shaft that is an output shaft of an electric motor, a counter output shaft, a counter output shaft having an input shaft, an electric motor shaft, and a counter drive gear. A planetary gear mechanism that is driven and connected to transmit power to each other, the input shaft is coaxially arranged on the inner periphery of the counter output shaft, and the input shaft and the counter output shaft are on one side of the planetary gear mechanism, and the motor shaft The counter output shaft is supported by the case of the power transmission device at the ends of the counter output shaft, and the input shaft is connected to the inner periphery of the counter output shaft. And is supported by the case of the power transmission device via the counter output shaft.

  By the way, the power transmission device having such a configuration includes a counter output shaft having a counter drive gear and a planetary gear mechanism, which are composed of separate members that are spaced apart in the axial direction of the input shaft. The power transmission device becomes long in the axial direction of the shaft.

  On the other hand, it is conceivable to reduce the length of the power transmission device by integrating the ring gear of the planetary gear mechanism and the counter drive gear, thereby reducing the size of the power transmission device.

FIG. 4 is a diagram showing a configuration of a power transmission device in which a ring gear and a counter drive gear of a planetary gear mechanism are integrated.
In FIG. 4, power is transmitted to the input shaft 1 from a crankshaft 10 of the internal combustion engine via a damper device 2 with a torque limiter. The input shaft 1 is connected to a case 4 via a needle bearing 3. The hollow support portion 4a is rotatably supported.

  A carrier 5C of a planetary gear mechanism 5 is connected to the input shaft 1. The sun gear 5S of the planetary gear mechanism 5 is connected to a motor shaft 6 of a generator (not shown) coaxially provided with the input shaft 1, and this sun gear 5S is a pinion gear provided rotatably on the carrier 5C. It is connected to the ring gear 5R via 5P. The ring gear 5R is provided integrally with the counter drive gear 7. The counter drive gear 7 is connected to the motor shaft of the electric motor through a gear train and is connected to the wheels through a differential device. Yes.

  The ring gear 5 </ b> R is rotatably supported on the outer periphery of the annular support portions 4 b and 4 c of the case 4 via a pair of ball bearings 8 and 9. The annular support portion 4c is formed on the wall portion 4d of the case 4 having an axis extending in a direction substantially orthogonal to the input shaft 1 from the outer peripheral portion of the hollow support portion 4a.

  In addition, the damper device 2 with the torque limiter is spline-fitted to the projecting portion 1A that discharges outward from the hollow support portion 4a of the case 4 at the radially inner end, and the radially outer end via the limiter portion 12. A damper 14 is connected to a flywheel 11 provided at the end of the crankshaft 10 and absorbs a fluctuating torque generated between the input shaft 1 and the crankshaft 10 by the elastic force of the compression spring 13.

  The limiter unit 12 is fixed to the flywheel 11 with the friction members 15a and 15b attached to the radially outer end of the damper unit 14, and sandwiches the friction members 15a and 15b. The input shaft 1 and the crankshaft 10 The ring-shaped member 16 is configured to rotate relative to the damper portion 14 by sliding with respect to the friction materials 15a and 15b when the fluctuation torque generated between and the friction member 15a exceeds a predetermined value.

JP 2003-191760 A

  However, when the inner peripheral portion of the ring gear 5R of the planetary gear mechanism 5 is supported on the outer peripheral portions of the annular support portions 4b and 4c of the case 4 via the ball bearings 8 and 9, the ball bearing 9 and the needle bearing 3 are If it is disposed on an axis perpendicular to the axial direction of the input shaft 1, the hollow support portion 4a and the annular support portion 4c may be deformed.

  That is, in the damper device 2 with the torque limiter, the damper portion 14 and the limiter portion 12 are integrated so that the friction materials 15 a and 15 b are press-fitted into the ring-shaped member 16 of the limiter portion 12.

  For this reason, if the assembly accuracy of the damper part 14 and the limiter part 12 is poor, the damper part 14 may be displaced in the radial direction of the damper part 14 from the normal mounting position with respect to the limiter part 12. When the position difference between the damper portion 14 and the limiter portion 12 occurs in this way, when the input shaft 1 rotates, the damper device 2 with the torque limiter rotates eccentrically in a direction orthogonal to the axial direction of the input shaft 1. End up.

  For this reason, as shown by an arrow P1 in FIG. 4, the eccentric load of the damper device 2 with the torque limiter is transmitted to the input shaft 1, and this eccentric load is transmitted from the needle bearing 3 to the hollow support portion 4a.

  In addition, since the inner peripheral portion of the ring gear 5R of the planetary gear mechanism 5 is supported by the outer peripheral portion of the annular support portion 4c of the case 4 via the ball bearing 9, as shown by an arrow P2 in FIG. The reaction force of the ring gear 5R is transmitted to the annular support portion 4c through the ball bearing 9.

  Therefore, when the ball bearing 9 and the needle bearing 3 are arranged on an axis perpendicular to the axial direction of the input shaft 1, the resultant force of the eccentric load of the damper device 2 with the torque limiter and the gear reaction force of the ring gear 5R is supported hollowly. There is a possibility that the hollow support portion 4a and the annular support portion 4c may be deformed by being added to the portion 4a and the annular support portion 4c.

  In addition to this, since the central portion in the axial direction of the rotation center axis of the needle bearing 3 is offset from the wall portion 4d of the case 4 by the distance A in the axial direction of the input shaft 1, the eccentric load of the damper device 2 with the torque limiter is Is transmitted to the input shaft 1, a rotational moment M centering on the axial center of the rotational center axis of the needle bearing 3 is applied to the hollow support portion 4 a and the annular support portion 4 c, resulting in the resultant force. In combination with this, there is a risk of promoting the deformation of the hollow support portion 4a and the annular support portion 4c.

  If the hollow support portion 4a and the annular support portion 4c are deformed, the meshing of the ring gear 5R, the pinion gear 5P, and the sun gear 5S of the planetary gear mechanism 5 is deteriorated along with the deformation of the hollow support portion 4a and the annular support portion 4c. As a result, in addition to the NV (noise and vibration) performance of the power transmission device, the durability may deteriorate.

  In order to improve such a point, it is conceivable to increase the thickness of the hollow support portion 4a and the annular support portion 4c by increasing the thickness of the hollow support portion 4a and the annular support portion 4c. If the annular support portion 4c is made thick, the entire weight of the case 4 increases, and the manufacturing cost of the power transmission device increases accordingly.

  The present invention has been made to solve the conventional problems as described above, and suppresses deformation of the hollow support portion and the annular support portion when an eccentric load of the damper mechanism is applied to the input shaft. Another object of the present invention is to provide a power transmission device that can prevent deterioration in NV performance and durability due to deterioration in meshing of the planetary gear mechanism.

  In order to achieve the above object, a power transmission device according to the present invention includes (1) an input shaft rotatably supported by a hollow support portion of a case of the power transmission device via a first bearing, and the hollow support portion. A damper portion that is attached to a protruding portion of the input shaft that protrudes outward from the input shaft and absorbs a fluctuating torque generated between the input shaft and the output shaft of the internal combustion engine by an elastic force; and the output shaft and the damper portion And a damper mechanism having a limiter portion that rotates relative to the damper portion when the fluctuation torque exceeds a predetermined value, and is provided so as to surround the input shaft. A planetary gear mechanism having a ring gear that transmits power transmitted to the input shaft to predetermined components of the power transmission device, and the case is in a direction substantially orthogonal to the input shaft from the outer peripheral portion of the hollow support portion A power transmission device having a wall portion having an extending axis, the inner peripheral portion of the ring gear being rotatably supported by an annular support portion provided on the wall portion via a second bearing; The rotation center axis of the first bearing and the second bearing is separated in the axial direction of the input shaft, and the axial center of the rotation center axis of the first bearing is on the axis of the wall portion It is composed of things that are positioned.

  The power transmission device includes a first bearing that supports the input shaft on the hollow support portion of the case, and a second bearing that supports the inner peripheral portion of the ring gear on the annular support portion of the case formed on the outer peripheral portion of the hollow support portion. Since the center axis of rotation with the bearing is separated in the axial direction of the input shaft, when the eccentric load of the damper mechanism is applied to the input shaft, the eccentric load received by the hollow support portion via the first bearing and the second load The reaction force of the ring gear received by the annular support part via the bearing can be dispersed in the axial direction of the input shaft, and deformation of the hollow support part and the annular support part can be suppressed.

  Further, the first bearing is positioned so that the axial center portion of the rotation center shaft is positioned on the axis of the case wall portion so that the axial center portion of the first bearing and the case wall portion are not eccentric in the axial direction. Therefore, it is possible to suppress the rotational moment from being applied to the hollow support portion and the annular support portion due to the eccentric load of the damper mechanism, and it is possible to suppress the deformation of the hollow support portion and the annular support portion.

  Thus, since it can suppress that a hollow support part and an annular support part deform | transform, it can prevent that the meshing | engagement of a planetary gear mechanism deteriorates, and NV performance and durability of a power transmission device deteriorate. Can be prevented.

  Moreover, since it can suppress that a hollow support part deform | transforms, while being able to support an input shaft stably to a hollow support part, it becomes unnecessary to raise the intensity | strength of a hollow support part and an annular support part. The power transmission device can be reduced in weight, and the manufacturing cost of the power transmission device can be prevented from increasing.

  (2) In the power transmission device according to (1), (2) the axial direction of the input shaft from the wall portion so that the annular support portion is separated from the first bearing in the axial direction of the input shaft. It is comprised from what protrudes along.

  In this power transmission device, the annular support portion protrudes from the wall portion along the axial direction of the input shaft so as to be separated from the first bearing and the axial direction of the input shaft. The second bearing can be separated from the first bearing in the axial direction of the input shaft while being positioned on the line.

  In the power transmission device according to the above (1) or (2), (3) a first electric motor having a first rotating shaft coaxial with the input shaft, and provided in parallel with the first rotating shaft. A second electric motor having a second rotating shaft, wherein the planetary gear mechanism includes a sun gear attached to the first rotating shaft, a carrier connected to the input shaft, and a power transmission unit. And the ring gear coupled to the second electric motor, the ring gear is provided integrally with a counter drive gear, and the counter drive gear is connected to the second rotation via the power transmission unit. It is comprised from what is connected with a shaft and the axle.

  In the planetary gear mechanism of the power transmission device, the sun gear is attached to the first rotating shaft of the first electric motor, the carrier is connected to the input shaft, the ring gear is connected to the axle through the counter drive gear and the power transmission unit. However, since the meshing of the planetary gear mechanism is suppressed from being deteriorated, power is transmitted between the internal combustion engine, the first motor, the second motor, and the axle via the planetary gear mechanism. It can be transmitted smoothly.

  Moreover, since the ring gear and the counter drive gear are provided integrally, the power transmission device can be reduced in size.

  According to the present invention, when the eccentric load of the damper mechanism is applied to the input shaft, the deformation of the hollow support portion and the annular support portion is suppressed, and the NV performance and the durability due to the deterioration of the meshing of the planetary gear mechanism are achieved. A power transmission device capable of preventing deterioration can be provided.

1 is a diagram showing an embodiment of a power transmission device according to the present invention, and is a main system configuration diagram of a power system centering on a transaxle of a hybrid vehicle. It is a figure which shows one Embodiment of the power transmission device which concerns on this invention, and is sectional drawing of a power distribution device. It is a figure which shows one Embodiment of the power transmission device which concerns on this invention, and is a figure which shows the eccentric load of the damper apparatus with a limiter added to a hollow support part and a cyclic | annular support part. It is sectional drawing of the power distribution device with which the ring gear and the counter drive gear were provided integrally.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a control device for a power transmission device according to the present invention will be described with reference to the drawings.
1-3 is a figure which shows one Embodiment of the power transmission device which concerns on this invention.
First, the configuration will be described.
In FIG. 1, a transaxle as a power transmission device is a motor generator MG1 as a first electric motor that converts kinetic energy of an engine 21 that is an internal combustion engine into electric energy, and a second that functions as an auxiliary power source of the engine 21. Motor generator MG2 as an electric motor, and a power distribution device (power transmission mechanism) 22 that distributes the output of engine 21 to each of two systems of motor generator MG1 and drive wheel 45.

  As shown in FIG. 1 and FIG. 2, the power distribution device 22 includes a planetary gear mechanism, an external gear sun gear 23S that rotates at the center of a plurality of gear elements, and a sun gear 23S that circumscribes the sun gear 23S. Pinion gear 23P, which is an external gear that revolves while rotating around its periphery, ring gear 23R, which is an internal gear that is formed in a hollow ring so as to mesh with pinion gear 23P, and pinion gear 23P that is rotatably supported via pinion shaft 23PS. And a carrier 23C that rotates through the revolution of the pinion gear 23P.

  A one-way clutch 24 that prevents reverse rotation of the engine 21 is connected to the carrier 23C, and the one-way clutch 24 is attached to a transaxle case 25 (corresponding to the case of the present invention).

  The rotational torque generated by rotationally driving the engine 21 is transmitted to an input shaft 28 as an input shaft via a crankshaft 26 as an output shaft of the engine 21 and a damper device 27 with a coil spring type torque limiter. An oil pump 29 is disposed on the axis of the input shaft 28.

  The oil pump 29 is operated, for example, by receiving supply of rotational torque of the input shaft 28. As the oil pump 29, a trochoid pump, a gear pump, or the like can be used.

  The oil pan 30 is filled with oil, and the lubricating oil sucked by the oil pump 29 is conveyed to the power system of each part such as the power distribution device 22 and the like, and the rotating part and sliding part of each gear element and each shaft. Circulates and cools each part, reduces frictional resistance, plays a role in preventing corrosion and maintaining airtightness.

  The motor generator MG1 includes a motor shaft 31 as a first rotating shaft that is disposed coaxially with the input shaft 28 around the input shaft 28, and a rotor 32R made of a permanent magnet attached to the motor shaft 31. And an AC synchronous generator provided with a stator 32S around which a three-phase winding is wound, and supplies power for battery charging and motor driving (not shown).

  The motor generator MG2 includes a motor shaft 33 as a second rotation shaft that is rotatably installed in parallel with the input shaft 28, a rotor 34R made of a permanent magnet attached to the motor shaft 33, and a three-phase winding. And a stator 34S wound with an AC synchronous generator. By supplying a three-phase AC current to the three-phase winding, a rotating magnetic field is generated in the motor generator MG2, and a predetermined rotation is achieved. Output torque.

  The motor generator MG2 assists smooth start and acceleration as an auxiliary power source of the engine 21, and converts the kinetic energy of the vehicle into electric energy and charges the battery when the regenerative braking is activated.

  As shown in FIGS. 1 and 2, in the power distribution device 22, the carrier 23 </ b> C is connected to the input shaft 28 of the engine 21, and the sun gear 23 </ b> S is spline-fitted to the motor shaft 31.

The ring gear 23R is provided integrally with a counter drive gear 35. The counter drive gear 35 is connected to a motor generator MG2 and a drive shaft 37 as an axle via a gear train 36 constituting a power transmission unit. Has been.
In the present embodiment, motor generator M2 and drive shaft 37 constitute predetermined components of the transaxle.

  The ring gear 23R of the present embodiment is configured to include a portion where internal teeth are formed and a portion where no internal teeth are formed, and a portion where no internal teeth are formed is an inner portion of the ring gear 23R. It constitutes the periphery.

  The power distribution device 22 transmits a part of the output of the engine 21 to the drive wheels 45 through the input shaft 28, the carrier 23C, the pinion gear 23P, the ring gear 23R, and the counter drive gear 35, and the remaining part of the output shaft. 28, is transmitted to the rotor 32R of the motor generator MG1 via the carrier 23C, the pinion gear 23P and the sun gear 23S and used for power generation.

  In the transaxle of the present embodiment, the gear train has a four-axis configuration, and the motor generator MG1, the power distribution device 22, and the counter drive gear 35 are arranged on the main shaft with the input shaft 28 as the center.

Also, on the second shaft, a counter driven gear 38 to which the rotational torque of the counter drive gear 35 is transmitted, a counter driven gear 40 that is provided integrally with the counter driven gear 38 and attached to one end of the counter drive shaft 39, A differential drive pinion 41 provided at the other end of the counter drive shaft 39 is disposed around the counter drive shaft 39.
The counter driven gear 38, the counter driven gear 40 and the differential drive pinion 41 constitute a gear train 36.

  On the third shaft, a motor shaft 33 of the motor generator MG2 and a counter driven gear 42 provided at the end of the motor shaft 33 and transmitting the rotation of the rotor 34R to the counter driven gear 40 are arranged.

  On the fourth shaft, there are a differential ring gear 43 to which power is transmitted from the differential drive pinion 41, a differential device 44 for distributing rotational torque so as to absorb the rotational difference between the inner and outer wheels of the drive wheel 45, and the differential device 44 A drive shaft 37 that transmits the differential output to the drive wheels 45 is disposed.

  As shown in FIG. 2, the motor shaft 31 of the motor generator MG1 is rotatably attached to the transaxle case 25 via a ball bearing 51. The ring gear 23R of the power distribution device 22 has an inner peripheral portion thereof. The case 25 is rotatably supported on the annular support portions 25 a and 25 b via ball bearings 52 and 53. Note that the ball bearing 53 constitutes a second bearing.

  The motor shaft 31 is formed in a hollow shape, and the end of the input shaft 28 is spline fitted to the end of the motor shaft 31. One end of an oil pump drive shaft 54 is attached to the end of the input shaft 28, and the other end of the oil pump drive shaft 54 is connected to the oil pump 29. That is, the oil pump drive shaft 54 has a function of driving the oil pump 29 and discharging oil by transmitting the power of the input shaft 28 to the oil pump 29.

  A communication hole 54a extending along the axial direction of the oil pump drive shaft 54 is formed inside the oil pump drive shaft 54, and the oil discharged from the oil pump 29 passes through the communication hole 54a. The other end of 54 is supplied to one end.

  A communication hole 28 a extending along the axial direction of the input shaft 28 is formed inside the input shaft 28, and the communication hole 28 a communicates with the communication hole 54 a of the oil pump drive shaft 54. . Further, a radiation hole 28b is formed in the communication hole 28a, and this radiation hole 28b extends in the radial direction of the input shaft 28 from the communication hole 28a.

  Oil supplied from the oil pump 29 to the communication hole 54a of the oil pump drive shaft 54 and the communication hole 28a of the input shaft 28 is supplied to the power distribution device 22 from the radiation hole 28b by the centrifugal force generated by the rotation of the input shaft 28, The dispensing device 22 is lubricated.

  On the other hand, the input shaft 28 is rotatably connected to the hollow support portion 25c of the case 25 via a needle bearing 55 as a first bearing, and is rotatably supported on the motor shaft 31 via a needle bearing 56. Has been.

  The case 25 includes a wall portion 25 d having an axis extending in a direction substantially orthogonal to the input shaft 28 from the outer peripheral portion of the hollow support portion 25 c, and the annular support portion 25 b is provided with respect to the needle bearing 55. It protrudes along the axial direction of the input shaft 28 from the wall portion 25d so as to be spaced apart in the axial direction.

  For this reason, the rotation center axes of the ball bearing 53 and the needle bearing 55 are set apart in the axial direction of the input shaft 28. The central portion in the axial direction of the rotation center axis of the needle bearing 55 is located on the axis of the wall portion 25d. As a result, the ball bearing 53 and the needle bearing 55 are installed between the ring gear 23R and the input shaft 28.

As shown in FIG. 2, the damper device 27 with a torque limiter constituting the damper mechanism includes a damper part 61 and a limiter part 62.
The damper portion 61 is a mechanism that buffers and absorbs fluctuations in the drive torque of the flywheel 46 that is fixed to the crankshaft 26 of the engine 21. The limiter unit 62 is a mechanism that limits power transmission from the crankshaft 26 to the input shaft 28 when the fluctuation torque between the damper unit 61 and the flywheel 46 reaches a predetermined value (limit torque value).

  The damper portion 61 includes a hub 63, side plates 64A and 64B, a damper member 65, a disk 66, a friction material 67, and a rivet 68.

  The hub 63 includes a flange portion 63A extending in the radial direction and an inner spline, and is connected to an outer spline formed on the outer peripheral surface of the protruding portion 28A of the input shaft 28 protruding outward from the hollow support portion 25c. ing. The flange portion 63A is provided with a plurality of cutout portions that are cut out radially outward, and a damper member 65 supported by a spring seat is disposed in the cutout portion.

  The side plates 64 </ b> A and 64 </ b> B are each provided with a through hole on the outer peripheral side, and support the disc 66 by the rivet 68 and are disposed coaxially with the hub 63 and relatively rotatable. The side plates 64A and 64B are provided with a plurality of window holes for accommodating the damper member 65.

  The damper member 65 is composed of a coil spring, and is accommodated in a notch and a window hole formed at positions where the hub 63 and the side plates 64A and 64B face each other. The disk 66 is a substantially annular disk disposed on the outer peripheral side of the side plates 64A and 64B. The disk 66 is sandwiched by the side plates 64A and 64B from both outer sides, and is substantially annular on both sides in the axial direction of the disk 66. The friction material 67 is fixed.

  The limiter portion 62 has a substantially circular opening, plates 69A and 69B fixed to the flywheel 46 by bolts 70, a friction plate 71 that holds the friction material 67 together with the plate 69A, the friction plate 71 and the plate The disc spring 72 is interposed between the disc 69B and urges the friction plate 71 toward the plate 69A to clamp the friction material 67 between the plate 69A and the friction plate 71.

  The limit torque value is determined by the biasing force of the disc spring 72, the flywheel 46 and the damper portion 61 are brought into a friction engagement state via the limiter portion 62, and the fluctuation torque between the damper portion 61 and the flywheel 46 is changed. When the limit torque value is exceeded, the friction material 67 slides with respect to the plate 69A and the friction plate 71, so that power transmission from the crankshaft 26 to the input shaft 28 can be limited.

Next, the operation will be described.
The rotational torque generated by rotationally driving the engine 21 is transmitted to the input shaft 28 via the crankshaft 26 of the engine 21 and the damper device 27 with a torque limiter, and the rotational torque is driven by the power distribution device 22 with the motor generator M1. Distributed to the wheel 45.

  Here, when the damper device 27 with the torque limiter is assembled between the input shaft 28 and the flywheel 46, the friction material 67 is sandwiched between the plates 69A and 69B together with the friction plate 71 and the disc spring 72. The damper part 61 and the limiter part 62 are assembled.

  For this reason, if the assembly accuracy of the damper unit 61 and the limiter unit 62 is poor, the damper unit 61 is displaced from the normal mounting position in the radial direction of the damper unit 61 with respect to the limiter unit 62, and the input shaft 28 is displaced. When rotating, the damper device 27 with the torque limiter rotates eccentrically in a direction orthogonal to the axial direction of the input shaft 28.

  At this time, the eccentric load of the damper device 27 with the torque limiter is transmitted to the input shaft 28, and this eccentric load is transmitted from the needle bearing 55 to the hollow support portion 25 c, and the reaction force of the ring gear 23 R is transmitted via the ball bearing 53. Is transmitted to the annular support portion 25b.

On the other hand, in the present embodiment, a ring gear is provided between the needle bearing 55 that supports the input shaft 28 on the hollow support portion 25c of the case 25, and the annular support portion 25b of the case 25 formed on the outer peripheral portion of the hollow support portion 25c. The rotational center of the ball bearing 53 that supports the inner peripheral portion of the 23R is separated in the axial direction of the input shaft 28.
For this reason, in FIG. 3, when the eccentric load of the damper device 27 with the torque limiter is applied to the input shaft 28 in the clockwise direction, for example, the eccentric load (arrow P3) received by the hollow support portion 25c via the needle bearing 55. And the reaction force (indicated by arrow P4) of the ring gear 23R received by the annular support portion 25b via the ball bearing 53 can be dispersed in the axial direction of the input shaft 28, and the hollow support portion 25c and the annular support portion 25b can be dispersed. Can be suppressed.

In addition, by positioning the needle bearing 55 in the axial direction center of the rotation center axis on the axis of the wall 25d of the case 25, the axial center of the needle bearing 55 and the wall 25d of the case 25 are moved in the axial direction. It can be prevented from being eccentric.
For this reason, it is possible to suppress the conventional rotational moment M1 (indicated by phantom lines) from being applied to the hollow support portion 25c and the annular support portion 25b due to the eccentric load of the damper device 27 with the torque limiter, and the hollow support portion 25c. And it can control that annular support part 25b changes.

  Thus, in this Embodiment, since it can suppress that the hollow support part 25c and the cyclic | annular support part 25b deform | transform, it prevents that the meshing | engagement of the planetary gear mechanism which comprises the power distribution device 22 deteriorates. It is possible to prevent the NV performance and durability of the transaxle from being deteriorated.

  Moreover, since it can suppress that the hollow support part 25c deform | transforms, while being able to support the input shaft 28 to the hollow support part 25c stably, the intensity | strength of the hollow support part 25c and the annular support part 25b is raised. Therefore, it is possible to reduce the weight of the transaxle and prevent an increase in the manufacturing cost of the transaxle.

  In the present embodiment, the annular support portion 25b is projected along the axial direction of the input shaft 28 from the wall portion 25d so as to be separated from the needle bearing 55 in the axial direction of the input shaft 28. The ball bearing 53 can be separated from the needle bearing 55 in the axial direction of the input shaft 28 while the bearing 55 is positioned on the axis of the wall portion 25d.

  In the present embodiment, the motor generator M1 having the motor shaft 31 coaxial with the input shaft 28 coupled to the crankshaft 26 of the engine 21 and the motor generator having the motor shaft 33 provided in parallel with the motor shaft 31 are provided. M2 and a planetary gear mechanism constituting the power distribution device 22 is driven via a sun gear 23S rotatably attached to the motor generator M1, a carrier 23C connected to the input shaft 28, and a gear train 36. The ring gear 23R is coupled to the shaft 37 and the motor generator M2. The ring gear 23R is provided integrally with the counter drive gear 35. The counter drive gear 35 is connected to the motor shaft 33 of the motor generator M2 via the gear train 36. And connected to the drive shaft 37 Constructed.

  In this embodiment, since the meshing of the planetary gear mechanism can be prevented from deteriorating, the engine 21, motor generator M1, motor generator M2, and drive shaft 37 are connected via the power distribution device 22. Power can be transmitted smoothly.

  In the present embodiment, the ring gear 23R and the counter drive gear 35 are integrally provided, so that the transaxle can be reduced in size.

  The embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

  As described above, the power transmission device according to the present invention suppresses the deformation of the hollow support portion and the annular support portion when the eccentric load of the damper mechanism is applied to the input shaft, thereby preventing the meshing of the planetary gear mechanism. The effect is that the deterioration of NV performance and durability due to deterioration can be prevented, and the ring gear of the planetary gear mechanism is the same as the input shaft through which power is transmitted from the internal combustion engine via a damper device with a torque limiter. It is useful as a power transmission device or the like supported by the case through a bearing.

21 Engine (Internal combustion engine)
22 Power distribution device (power transmission mechanism)
23C carrier 23R ring gear 23S sun gear 25 case 25b annular support part 25c hollow support part 25d wall part 27 damper device with a torque limiter (damper mechanism)
28 Input shaft (input shaft)
28A Protruding portion 31 Motor shaft (first rotating shaft)
33 Motor shaft (second rotary shaft)
37 Drive shaft (drive shaft, predetermined component)
53 Ball bearing (second bearing)
55 Needle bearing (first bearing)
61 Damper unit 62 Limiter unit MG1 Motor generator (first electric motor)
MG2 motor generator (second electric motor, predetermined component)

Claims (3)

An input shaft rotatably supported by a hollow support portion of a case of the power transmission device via a first bearing;
A damper portion attached to a projecting portion of the input shaft projecting outward from the hollow support portion, and absorbing a fluctuation torque generated between the input shaft and an output shaft of the internal combustion engine by an elastic force; and the output shaft; A damper mechanism that is interposed between the damper parts and has a limiter part that rotates relative to the damper part when the fluctuation torque exceeds a predetermined value;
A planetary gear mechanism having a ring gear that is provided so as to surround the input shaft and transmits power transmitted from the output shaft to the input shaft to a predetermined component of the power transmission device;
The case includes a wall portion having an axis extending in a direction substantially orthogonal to the input shaft from an outer peripheral portion of the hollow support portion, and an annular support portion in which an inner peripheral portion of the ring gear is provided on the wall portion A power transmission device rotatably supported via a second bearing,
The rotation center axis of the first bearing and the second bearing is separated in the axial direction of the input shaft, and the axial center of the rotation center axis of the first bearing is on the axis of the wall portion A power transmission device characterized by being positioned.   The said annular support part protrudes along the axial direction of the said input shaft from the said wall part so that it may space apart in the axial direction of the said input shaft with respect to the said 1st bearing. Power transmission device. A first electric motor having a first rotating shaft coaxial with the input shaft; and a second electric motor having a second rotating shaft provided in parallel with the first rotating shaft;
The planetary gear mechanism includes a sun gear attached to the first rotating shaft, a carrier connected to the input shaft, and the ring gear connected to the axle and the second electric motor via a power transmission unit. Have
The ring gear is provided integrally with a counter drive gear, and the counter drive gear is coupled to the second rotating shaft and the axle via the power transmission unit. The power transmission device described in 1.

Images