JP2021017951A - Vehicle driving device - Google Patents

Abstract

To restrain a tilt of a rotor with respect to a rotating shaft, and restrain damage to a fitting part of the rotating shaft and a fitting part of a rotor shaft.SOLUTION: A vehicular driving device comprises a first input shaft 21, an electric motor comprising a rotor 43 fitted to the first input shaft 21 so as to be incapable of relatively rotating, a planetary gear mechanism 3 comprising a sun gear 31 capable of rotating integrally with the first input shaft 21, and an annular member 46 fitted to the first input shaft 21 so as to be incapable of relatively rotating. The rotor 43 comprises a rotor shaft 45 extending in an axial direction of the first input shaft 21 and fitted to an outer peripheral surface of the first input shaft 21 so as to be incapable of relatively rotating, and a rotor body 44 supported by the rotor shaft 45. The annular member 46 is fitted to the first input shaft 21 on one end side in an axial direction of a fitting part 452 of the rotor shaft 45. The sun gear 31 is fitted to the fitting part 452 of the rotor shaft 45 and an outer peripheral surface of the annular member 46 so as to be incapable of relatively rotating, and rotates integrally with the first input shaft 21.SELECTED DRAWING: Figure 3

Description

The present invention relates to a vehicle drive device that transmits power of an electric motor using a planetary gear mechanism.

As a technique of this kind, for example, a driving device for a hybrid vehicle described in Patent Document 1 below is known. The vehicle drive device described in Patent Document 1 includes an internal combustion engine and an electric motor as drive sources, and is configured to be able to transmit these powers to drive wheels by using a planetary gear mechanism.

Japanese Patent No. 5745807

By the way, in the vehicle drive device using the planetary gear mechanism as described above, the rotor shaft of the electric motor and the sun gear of the planetary gear mechanism are attached to the fitting portion (for example, the spline fitting portion) formed on the rotating shaft (for example, the input shaft). And may be fitted side by side in the axial direction. In this case, the axial length of the rotor shaft becomes relatively shorter than the axial length of the rotor, and the rotor tends to tilt with respect to the rotating shaft. When the rotor shaft is tilted, an unnecessary dynamic load acts on the fitting portion of the rotating shaft and the fitting portion of the rotor shaft, and these are easily damaged.

The vehicle drive device according to one aspect of the present invention includes a rotating shaft, an electric motor having a rotor that is non-rotatably fitted to the rotating shaft, a planetary gear mechanism having a sun gear that can rotate integrally with the rotating shaft, and a rotating shaft. It is provided with an annular member that fits so as not to rotate relative to each other. The rotor has a rotor shaft extending in the axial direction of the rotating shaft and fitting to the outer peripheral surface of the rotating shaft so as not to rotate relative to the outer peripheral surface of the rotating shaft, and a rotor body supported by the rotor shaft. The annular member fits into the rotating shaft on one side of the rotor shaft in the axial direction. The sun gear fits on the outer peripheral surfaces of the rotor shaft and the annular member so as not to rotate relative to each other, and rotates integrally with the rotating shaft.

According to the present invention, tilting of the rotor with respect to the rotating shaft can be suppressed, and damage to the fitting portion of the rotating shaft and the fitting portion of the rotor shaft can be suppressed.

The skeleton diagram of the vehicle drive device which concerns on embodiment of this invention. FIG. 5 is a cross-sectional view showing an electric motor and a planetary gear mechanism included in the vehicle drive device according to the present embodiment. FIG. 2 is a partially enlarged cross-sectional view showing a part of the rotor and planetary gear mechanism of the electric motor shown in FIG.

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 3. The vehicle drive device according to the embodiment of the present invention can be applied to a hybrid vehicle whose travel drive source is an internal combustion engine (engine) and an electric motor (motor or motor generator), an electric vehicle whose travel drive source is an electric motor, or the like. .. In the following, an example of a vehicle drive device applied to a hybrid vehicle using an internal combustion engine and an electric motor as a traveling drive source will be described. FIG. 1 is a skeleton diagram of a vehicle driving device 1 according to an embodiment of the present invention.

As shown in FIG. 1, the vehicle driving device 1 includes a transmission 2, an internal combustion engine ENG, and an electric motor 4. The transmission 2 according to the present embodiment is a parallel shaft transmission having 7 forward speeds and 1 reverse speed, and is a so-called dry dual clutch transmission (DCT).

The transmission 2 has a first input shaft 21 that is detachably coupled to the internal combustion engine ENG via the first clutch C1 for odd speeds and an internal combustion engine that can be disconnected and disconnected via the second clutch C2 for even stages. The second input shaft 22 coupled to the ENG, the output shaft 23 that outputs the rotational force of the first input shaft 21 or the second input shaft 22 to a differential mechanism (not shown), and the first input shaft 21 are coupled. A planetary gear mechanism 3 is provided.

The internal combustion engine ENG is detachably coupled to the first input shaft 21 via the first clutch C1 on one side of the first input shaft 21 in the axial direction. A spline fitting portion 211 is formed at the other end of the first input shaft 21 in the axial direction, and the planetary gear mechanism 3 and the electric motor 4 are coupled via the spline fitting portion 211.

The planetary gear mechanism 3 includes a sun gear 31 that rotates integrally with the first input shaft 21, a ring gear 32 that can be fixed to the case 20 of the transmission 2, a pinion gear 33 that meshes with the sun gear 31 and the ring gear 32, and a pinion gear. It is provided with a carrier 34 that supports the 33 in a rotating and revolving manner. The electric motor 4 includes a stator 40 and a rotor 43 arranged inside the stator 40 in the radial direction. The planetary gear mechanism 3 is arranged inside the rotor 43 in the radial direction. The planetary gear mechanism 3 and the electric motor 4 will be described in detail later.

The 3rd speed drive gear 53, the 7th speed drive gear 57, and the 5th speed drive gear 55 are concentrically arranged on the first input shaft 21 so as to be relatively rotatable. A 3-7 speed synchromesh mechanism 63 is provided so as to be slidable in the axial direction between the 3rd speed drive gear 53 and the 7th speed drive gear 57, and a 5th speed synchromesh mechanism 65 corresponds to the 5th speed drive gear. It is provided so that it can slide in the axial direction. A first-speed synchromesh mechanism 61 is provided between the ring gear 32 and the case 20 so as to be slidable in the axial direction.

By sliding the 3-7-speed synchromesh mechanism 63 or the 5-speed synchromesh mechanism 65 to synchronize the desired gear stage, the gear stage is connected to the first input shaft 21. Further, by switching the first synchromesh mechanism 61, the rotational driving force of the pinion gear 33 is transmitted to the output shaft 23 via the carrier 34. With these gears and the synchromesh mechanism provided in this way, a first transmission gear mechanism for realizing a shift stage in odd-numbered stages (1, 3, 5, 7 speeds) is configured.

The second input shaft 22 is arranged substantially parallel to the first input shaft 21, and is disconnected from the internal combustion engine ENG via the second clutch C2 arranged side by side with the first clutch C1 on one side in the axial direction. They are tangibly connected. An outer main shaft 24 arranged concentrically so as to form an outer cylinder of the first input shaft 21 is connected to the output side of the second clutch C2. The outer main shaft 24 is constantly engaged with the reverse shaft 26 and the second input shaft 22 via the idle shaft 25, and the rotational output of the second clutch C2 is transmitted to the reverse shaft 26 and the second input shaft 22.

A second-speed drive gear 52, a sixth-speed drive gear 56, and a fourth-speed drive gear 54 are arranged concentrically on the second input shaft 22 so as to be relatively rotatable. A 2-6 speed synchromesh mechanism 62 is provided between the 2nd speed drive gear 52 and the 6th speed drive gear 56 so as to be slidable in the axial direction, and a 4th speed synchromesh mechanism 64 corresponds to the 4th speed drive gear 54. Is provided so as to be slidable in the axial direction.

By sliding the 2-6-speed synchromesh mechanism 62 or the 4-speed synchromesh mechanism 64 to synchronize the desired gear stage, the gear stage is connected to the second input shaft 22. These gears and the synchromesh mechanism provided in this way constitute a second gear mechanism for realizing gears in even-numbered gears (2nd, 4th, and 6th gears).

Each drive gear of the first transmission gear mechanism and the second transmission gear mechanism meshes with the corresponding gears of the first driven gear 71, the second driven gear 72, and the third driven gear 73 provided on the output shaft 23. The output shaft 23 is rotationally driven by the meshing of each drive gear and each driven gear.

The first clutch C1 and the second clutch C2 are composed of a hydraulic differential type wet friction clutch. The first clutch C1 is configured to be freely switchable between a transmission state in which the driving force of the internal combustion engine ENG is transmitted to the first input shaft 21 and an open state in which the transmission of the driving force is cut off. The second clutch C2 is configured to be freely switchable between a transmission state in which the driving force of the internal combustion engine ENG is transmitted to the second input shaft 22 and an open state in which the transmission of the driving force is cut off.

Next, the planetary gear mechanism 3 and the electric motor 4 described above will be described in detail with reference to FIGS. 2 and 3. FIG. 2 is a cross-sectional view showing the electric motor 4 and the planetary gear mechanism 3 included in the vehicle drive device 1 according to the present embodiment, and FIG. 3 is a part of the rotor 43 and the planetary gear mechanism 3 of the electric motor 4 shown in FIG. It is a partially enlarged sectional view which shows.

As described above, with the planetary gear mechanism 3 arranged inside the rotor 43 of the electric motor 4 in the radial direction, the planetary gear mechanism 3 and the electric motor 4 are first input via the spline fitting portion 211 of the first input shaft 21. When coupling to the shaft 21, for example, the sun gear 31 of the planetary gear mechanism 3 and the rotor shaft 45 described later of the electric motor 4 are arranged in the axial direction and spline-fitted to the spline fitting portion 211.

When the sun gear 31 of the planetary gear mechanism 3 and the rotor shaft 45 of the electric motor 4 are aligned in the axial direction and spline-fitted, the axial length of the rotor shaft 45 is relative to the axial length of the rotor 43. It gets shorter. When the axial length of the rotor shaft 45 is shortened, the rotor shaft 45 is likely to tilt with respect to the first input shaft 21.

When the rotor shaft 45 is easily tilted, for example, the first input shaft 21 is bent by receiving the transmission torque from each drive gear constituting the first transmission gear mechanism, and the relative positions of the stator 40 and the rotor 43 are displaced. In that case, the rotor shaft 45 may be tilted with respect to the first input shaft 21 due to the magnetic reaction force (force to return to a stable position) generated in the rotor 43.

When the rotor shaft 45 is tilted, an excessive dynamic load acts on the fitting portion 452 of the rotor shaft 45 and the spline fitting portion 211 of the first input shaft 21, which may be damaged.

Therefore, in the present embodiment, the sun gear 31 of the planetary gear mechanism 3 is fitted to the outer peripheral surface of the fitting portion 452 of the rotor shaft 45 to be fitted to the spline fitting portion 211. As a result, the fitting portion 452 of the rotor shaft 45 can be lengthened in the axial direction, and the rotor 43 is less likely to tilt with respect to the first input shaft 21. In other words, the fitting portion between the first input shaft 21 and the rotor 43 can be brought closer to the center of gravity of the rotor 43, and the rotor 43 is less likely to tilt with respect to the first input shaft 21. Hereinafter, the planetary gear mechanism 3 and the electric motor 4 will be described in detail, focusing on the support structure of the planetary gear mechanism 3 and the electric motor 4 with respect to the first input shaft 21.

As shown in FIG. 2, the electric motor 4 includes a stator 40 and a rotor 43 arranged inside the stator 40 in the radial direction. The stator 40 has a stator core 41 formed in a substantially cylindrical shape extending in the axial direction, and a coil 42 having a plurality of layers (for example, U phase, V phase, W phase) mounted on the stator core 41. The stator 40 generates a magnetic field when a current flows through the coil 42.

The rotor 43 includes a rotor body 44 and a rotor shaft 45 that supports the rotor body 44. The rotor main body 44 is formed in a substantially cylindrical shape so as to extend in the axial direction, and has a rotor core 441 arranged to face the inner peripheral surface of the stator core 41 and a magnet 442 mounted on the rotor core 441. The rotor 43 is rotationally driven by the magnetic field generated in the stator 40 repelling or attracting the magnet 442 of the rotor body 44.

The rotor shaft 45 connects the support portion 451 that supports the rotor body 44, the fitting portion 452 that fits into the spline fitting portion 211 of the first input shaft 21, and the support portion 451 and the fitting portion 452. It has a part 453 and. The support portion 451 is formed in a substantially cylindrical shape so as to extend in the axial direction. The fitting portion 452 is formed in a substantially cylindrical shape which is arranged concentrically with the first input shaft 21. The connecting portion 453 is formed so that the other end portion of the support portion 451 in the axial direction and the substantially central portion of the fitting portion 452 in the axial direction can be connected to each other.

As shown in FIG. 3, on the inner peripheral surface of the fitting portion 452, the first spline fitting portion 454 that can be fitted to the spline fitting portion 211 formed at the other end of the first input shaft 21. Is formed. The rotor shaft 45 and the first input shaft 21 are a first spline fitting portion 454 formed on the inner peripheral surface of the fitting portion 452 and a spline fitting portion 211 formed on the outer peripheral surface of the first input shaft 21. Is spline-fitted so that it cannot rotate relative to each other, so that it rotates integrally. The first spline fitting portion 454 of the fitting portion 452 and the spline fitting portion 211 of the first input shaft 21 are coupled and rotate integrally with a slight clearance (for example, 0 to 34 μm).

On the outer peripheral surface of the fitting portion 452, a second spline fitting portion 455 that can be fitted with the spline fitting portion 311 described later formed on the inner peripheral surface of the sun gear 31 is formed on one side in the axial direction. There is. The second spline fitting portion 455 is formed from a portion to which the connecting portion 453 is connected to one end portion. The rotor shaft 45 and the sun gear 31 spline the second spline fitting portion 455 formed on the outer peripheral surface of the fitting portion 452 and the spline fitting portion 311 formed on the inner peripheral surface of the sun gear 31 so as not to rotate relative to each other. By fitting, it rotates integrally. The second spline fitting portion 455 of the fitting portion 452 and the spline fitting portion 311 of the sun gear 31 are coupled and rotate integrally with a slight clearance (for example, 0 to 34 μm).

In this way, the rotor shaft 45 (fitting portion 452) and the sun gear 31 are not fitted in the spline fitting portion 211 formed on the first input shaft 21 in the axial direction, but rather in the fitting portion. By spline fitting the sun gear 31 to the second spline fitting portion 455 formed on the outer peripheral surface of the 452, the fitting portion 452 can be extended to one side in the axial direction. For example, the length substantially the same as the axial length of the sun gear 31 can be lengthened in the axial direction.

In the present embodiment, the annular member 46 described later is arranged at one end of the fitting portion 452 in the axial direction, and the axial length of the fitting portion 452 is the axial length of the sun gear 31. The length is shorter than the length by the axial length of the annular member 46. That is, the axial length of the fitting portion 452 corresponds to the axial length of the sun gear 31 and the annular member 46.

As described above, the annular member 46 is arranged at one end of the fitting portion 452 in the axial direction. That is, the annular member 46 is arranged side by side with the fitting portion 452 in the axial direction. The annular member 46 is formed in a substantially annular shape having a thickness in the axial direction, and abuts on one end portion of the fitting portion 452 in the axial direction to regulate the axial movement of the fitting portion 452. The axial length of the annular member 46 is shorter than the axial length of the sun gear 31, for example, having a length of half or less of the axial length of the sun gear 31.

On the inner peripheral surface of the annular member 46, a first spline fitting portion 461 that can be fitted to the above-mentioned spline fitting portion 211 formed on the first input shaft 21 is formed. The first spline fitting portion 461 is formed over the entire axial direction of the inner peripheral surface. The annular member 46 and the first input shaft 21 are a first spline fitting portion 461 formed on the inner peripheral surface of the annular member 46 and a spline fitting portion 211 formed on the outer peripheral surface of the first input shaft 21. By spline fitting with and in a relative non-rotatable manner, they rotate integrally.

A second spline fitting portion 462 that can be fitted with a spline fitting portion 311 described later, which is formed on the inner peripheral surface of the sun gear 31, is formed on the outer peripheral surface of the annular member 46. The second spline fitting portion 462 is formed over the entire axial direction of the outer peripheral surface. The annular member 46 and the sun gear 31 make the second spline fitting portion 462 formed on the outer peripheral surface of the annular member 46 and the spline fitting portion 311 formed on the inner peripheral surface of the sun gear 31 relatively non-rotatable. By fitting the spline, it rotates integrally.

Further, the annular member 46 is spline-fitted with the inner peripheral surface in a state of being press-fitted into the inner peripheral surface of the sun gear 31, and is fixed in this state. That is, the second spline fitting portion 462 of the annular member 46 and the spline fitting portion 311 of the sun gear 31 are the first spline fitting portion 454 of the fitting portion 452 and the spline fitting portion 211 of the first input shaft 21. , And unlike the second spline fitting portion 455 of the fitting portion 452 and the spline fitting portion 311 of the sun gear 31, they are coupled and rotate integrally with almost no clearance.

For example, when the planetary gear mechanism 3 and the rotor 43 are assembled to the first input shaft 21, the rotor 43 is assembled after the sun gear 31 of the planetary gear mechanism 3 is assembled to the first input shaft 21, but the sun gear 31 of the planetary gear mechanism 3 is assembled. When fitting to the outer peripheral surface of the fitting portion 452 of the rotor shaft 45, this becomes difficult as it is. Therefore, by assembling the annular member 46 to the first input shaft 21 in advance, the planetary gear mechanism 3 and the rotor 43 are fitted even when the sun gear 31 of the planetary gear mechanism 3 is fitted to the outer peripheral surface of the fitting portion 452 of the rotor shaft 45. Can be easily assembled to the first input shaft 21. In particular, it becomes easy to form a gap and align the phase when assembling the rotor 43. At this time, the annular member 46 is loosely assembled to the first input shaft 21 from the viewpoint of assembling property to the first input shaft 21.

A cotter 47 formed in a substantially annular shape is arranged at the other end of the fitting portion 452 in the axial direction. The cotter 47 is fitted in a recess 47h formed in the first input shaft 21 and abuts on the other end of the fitting portion 452 in the axial direction to regulate the axial movement of the fitting portion 452. ing. The cotter 47 is fixed by a holding member 48a such as a retainer and an annular support member 28b.

As shown in FIG. 2, the planetary gear mechanism 3 includes a sun gear 31 that rotates integrally with the first input shaft 21 and the electric motor 4, a ring gear 32 that can be fixed to the case 20 of the transmission 2, and the sun gear 31 and the ring gear. A pinion gear 33 that meshes with the 32 and a carrier 34 that supports the pinion gear 33 so as to rotate and revolve.

The sun gear 31 is located substantially in the center of the planetary gear mechanism 3, and is a second spline fitting portion 455 formed on the fitting portion 452 of the rotor shaft 45 and a second spline fitting portion 462 formed on the annular member 46. It is an external gear that spline fits into the gear. As described above, the inner peripheral surface of the sun gear 31 is formed with a spline fitting portion 311 that can be fitted to the fitting portion 452 of the rotor shaft 45 and the second spline fitting portions 455 and 462 of the annular member 46. ing.

The fitting portion 452 and the annular member 46 of the sun gear 31 and the rotor shaft 45 are the spline fitting portion 311 formed on the inner peripheral surface of the sun gear 31 and the fitting portion 452 of the rotor shaft 45 and the outer circumference of the annular member 46. By spline-coupling the second spline fitting portions 455 and 462 formed on the surface so that they cannot rotate relative to each other, they rotate integrally.

As described above, the spline fitting portion 311 of the sun gear 31 and the second spline fitting portion 455 of the fitting portion 452 of the rotor shaft 45 are coupled with a slight clearance (for example, 0 to 34 μm). And rotate together. On the other hand, the spline fitting portion 311 of the sun gear 31 and the second spline fitting portion 462 of the annular member 46 are coupled to each other in a state where the annular member 46 is press-fitted and rotate integrally.

The ring gear 32 is an internal gear that is located radially outside the planetary gear mechanism 3 and meshes with the pinion gear 33 outside the pinion gear 33. The ring gear 32 is configured to be fixed to the case 20 of the transmission 2 via the 1-speed synchromesh mechanism 61. Further, a synchronizer hub 61a of the 1-speed synchromesh mechanism 61 is connected to the ring gear 32, and the synchronizer hub 61a is supported on the outer periphery of the first input shaft 21 via a bearing 20a so as to be relatively rotatable. .. That is, the ring gear 32 is supported so as to be relatively rotatable on the outer circumference of the first input shaft 21 via the bearing 20a.

The pinion gear 33 has a pinion gear main body 331 that meshes with the sun gear 31 and the ring gear 32, and a pinion shaft 332 that rotatably supports the pinion gear main body 331. The pinion gear body 331 is an external gear that meshes with the sun gear 31 and the ring gear 32, and the pinion shaft 332 is fixed to the carrier 34. The carrier 34 is connected to a third speed drive gear 53 arranged on the first input shaft 21.

The above-mentioned 1-speed synchromesh mechanism 61 is provided between the ring gear 32 and the case 20 of the transmission 2 so as to be slidable in the axial direction, and the carrier 34 is the 3-speed drive gear 53 as described above. It is connected to (see FIG. 1). By sliding the 1-speed synchromesh mechanism 61 to fix the ring gear 32 to the case 20, the rotational driving force of the pinion gear 33 is transferred to the output shaft via the carrier 34, the 3-speed drive gear 53, and the first input shaft 21. It becomes possible to transmit to 23 (see FIG. 1).

As a result, the rotation of the first input shaft 21 is changed by the gear ratio for the first speed determined by the combination of the gear ratio of the planetary gear mechanism 3 and the gear ratio of the third speed drive gear 53, and is output via the output shaft 23. Will be done. At this time, since the 3-7 speed synchromesh mechanism 63 is in the neutral position, the 3-7 speed synchromesh mechanism 63 does not engage with the 3rd speed drive gear 53. When the 2nd to 7th gears on the higher speed side than the 1st gear are selected, the 1st gear synchromesh mechanism 61 is off and the rotational driving force of the pinion gear 33 is not transmitted.

As described above, the planetary gear mechanism 3 according to the present embodiment is configured as a single pinion type. The planetary gear mechanism may be composed of, for example, a double pinion type having a carrier that supports a pair of pinion gears in a rotating and revolving manner. In this case, for example, the ring gear may be connected to the third drive gear, and the carrier may be fixed to the case by the first-speed synchromesh mechanism.

According to this embodiment, the following effects can be obtained.
(1) The vehicle drive device 1 includes a first input shaft 21, an electric motor 4 having a rotor 43 that fits the first input shaft 21 so as not to rotate relative to the first input shaft 21, and a sun gear 31 that can rotate integrally with the first input shaft 21. It includes a planetary gear mechanism 3 and an annular member 46 that is fitted to the first input shaft 21 so as not to rotate relative to each other. The rotor 43 has a rotor shaft 45 extending in the axial direction of the first input shaft 21 and fitting to the outer peripheral surface of the first input shaft 21 so as not to rotate relative to the outer peripheral surface, and a rotor body 44 supported by the rotor shaft 45. The annular member 46 is fitted to the first input shaft 21 at one end side in the axial direction of the fitting portion 452 of the rotor shaft 45, and the sun gear 31 is the outer circumference of the fitting portion 452 of the rotor shaft 45 and the annular member 46. It fits on the surface so that it cannot rotate relative to the surface and rotates integrally with the first input shaft 21.

With this configuration, the fitting portion 452 of the rotor shaft 45 can be lengthened in the axial direction, and the rotor 43 is less likely to tilt with respect to the first input shaft 21. Therefore, it is possible to prevent the spline fitting portion 211 of the first input shaft 21 and the first spline fitting portion 454 of the fitting portion 452 of the rotor shaft 45 from being damaged.

For example, when the fitting portion 452 of the rotor shaft 45 is spline-fitted to the first input shaft 21 with a slight clearance (0 to 34 μm) (for example, not press-fitted), the fitting portion 452 is spline-fitted to the first input shaft 21. When a gear reaction force (a force acting by receiving a transmission torque on the first input shaft) acts from each of the arranged drive gears, the first input shaft 21 bends in a direction intersecting the axial direction. When the first input shaft 21 is bent, the rotor 43 spline-fitted to the other end of the first input shaft 21 is tilted.

When the rotor 43 is tilted, the relative position of the rotor body 44 with respect to the stator 40 shifts. When the relative position of the rotor body 44 with respect to the stator 40 shifts, the magnetic reaction force (attracting force between the rotor body 44 and the stator 40) that causes the rotor body 44 to return to a position that is magnetically stable with respect to the stator 40 becomes the rotor 43. Acts on.

At this time, since the first input shaft 21 is in a bent state due to the gear reaction force, when a magnetic reaction force acts on the rotor 43, the rotor 43 is in a state of being tilted with respect to the first input shaft 21. When the rotor 43 is tilted, an excessive dynamic load acts on the first spline fitting portion 454 of the fitting portion 452 of the rotor shaft 45 and the spline fitting portion 211 of the first input shaft 21. When an excessive dynamic load acts on these fitting portions, for example, the spline fitting portion may be twisted to generate a rattling noise, wear, or cause unnecessary damage.

In the present embodiment, the fitting portion 452 of the rotor shaft 45 can be extended in the axial direction by the above configuration. Therefore, even if a magnetic reaction force acts on the rotor 43, for example, the rotor 43 with respect to the first input shaft 21. Is less likely to tilt, and it is possible to prevent an excessive dynamic load from acting on the above-mentioned spline fitting portion. Therefore, for example, the surface pressure at the above-mentioned spline fitting portion is reduced, and the generation of rattling noise can be reduced. Further, for example, the wear and tear at the spline fitting portion described above can be reduced, and the durability can be improved, so that the product life can be extended.

Further, for example, by extending the fitting portion 452 of the rotor shaft 45 in the axial direction, the above-mentioned spline fitting portion can be brought closer to the position of the center of gravity of the rotor 43, so that the rotor 43 is less likely to tilt.

Further, for example, when the planetary gear mechanism 3 and the electric motor 4 are assembled to the first input shaft 21, the sun gear 31 of the planetary gear mechanism 3 is assembled to the first input shaft 21, and then the rotor 43 of the electric motor 4 is assembled. By arranging the member 46 on one side of the fitting portion 452 of the rotor shaft 45 and assembling the sun gear 31 to the annular member 46, the sun gear 31 can be assembled before the rotor 43 even in the above configuration. It will be possible. In particular, the sun gear 31 can be assembled to the first input shaft 21 (annular member 46) in a state where a gap is formed and the phase is matched when the rotor 43 is assembled. This facilitates the assembly of the rotor 43 after the sun gear 31 has been assembled to the first input shaft 21 (annular member 46).

Further, for example, by making the sun gear 31 and the annular member 46 separate parts, the spline fitting portion 311 formed on the inner peripheral surface of the sun gear 31 can be broached. For example, when the sun gear 31 and the annular member 46 are integrated, the spline fitting portion of the sun gear cannot be broached due to the presence of the annular member, but as in the present embodiment, the sun gear 31 and the annular member 46 cannot be broached. By making the annular member 46 a separate part, broaching of the spline fitting portion 311 of the sun gear 31 becomes possible. As a result, it is possible to suppress an increase in the processing cost of the sun gear 31, and it is possible to suppress the manufacturing cost of the vehicle drive device 1. Further, by broaching the spline fitting portion 311, mass production of the sun gear 31 becomes possible.

(2) The annular member 46 is fixed to the sun gear 31 on one side of the fitting portion 452 of the rotor shaft 45 in a state of being press-fitted. As a result, when the planetary gear mechanism 3 and the electric motor 4 are assembled to the first input shaft 21, the first input shaft 21 (circle) of the sun gear 31 in a state where the formation of a gap and the phase alignment when assembling the rotor 43 are adjusted. Assembling to the ring member 46) becomes easy.

(3) The rotor shaft 45 includes a support portion 451 that supports the rotor body 44, a fitting portion 452 that fits into the first input shaft 21, and a connection portion 453 that connects the support portion 451 and the fitting portion 452. Have. The connecting portion 453 is connected to the fitting portion 452 at a substantially central portion in the axial direction of the fitting portion 452. As a result, for example, the fitting portion 452 is connected to the connecting portion 453 near the position of the center of gravity of the rotor 43, so that the rotor 43 is less likely to tilt.

(4) The planetary gear mechanism 3 is arranged inside the rotor body 44 in the radial direction. As a result, the vehicle drive device having the planetary gear mechanism 3 and the electric motor 4 can be miniaturized.

In the above embodiment, an example of a vehicle driving device 1 applied to a hybrid vehicle having an internal combustion engine ENG and an electric motor 4 as a traveling drive source has been described, but the present invention is not limited thereto. For example, it may be a vehicle drive device applied to an electric vehicle using an electric motor as a traveling drive source. Further, the electric motor may have a motor generator, and may have a configuration having a plurality of electric motors.

In the above embodiment, the vehicle drive device includes a transmission 2 having a planetary gear mechanism 3, an internal combustion engine ENG, and an electric motor 4, but the present invention is not limited thereto. The vehicle drive device may include a rotating shaft, an electric motor, and a planetary gear mechanism.

In the above embodiment, the rotor shaft 45 has a support portion 451 and a fitting portion 452 and a connecting portion 453, and the connecting portion 453 is connected to a substantially central portion in the axial direction of the fitting portion 452. Not limited to. For example, the connecting portion may be configured to be connected to the other end of the fitting portion.

The above description is merely an example, and the present invention is not limited to the above-described embodiments as long as the features of the present invention are not impaired.

1 Vehicle drive, 2 Transmission, 3 Planetary gear mechanism, 4 Electric, 21 1st input shaft (rotary shaft), 22 2nd input shaft, 23 Output shaft, 31 Sun gear, 32 Ring gear, 33 Pinion gear, 34 Carrier , 40 stator, 43 rotor, 45 rotor shaft, 46 ring member, 211 first fitting part, 311 spline fitting part, 452 fitting part, 454 first fitting part, 455 second fitting part, 461st 1 spline fitting part, 462 2nd spline fitting part

Claims (4)

An electric motor having a rotating shaft and a rotor that fits the rotating shaft in a relative non-rotatable manner, a planetary gear mechanism having a sun gear that can rotate integrally with the rotating shaft, and a ring that fits in the rotating shaft in a relative non-rotatable manner Equipped with parts,
The rotor has a rotor shaft extending in the axial direction of the rotating shaft and fitting to the outer peripheral surface of the rotating shaft so as not to rotate relative to the rotor shaft, and a rotor body supported by the rotor shaft.
The annular member is fitted to the rotating shaft on one side in the axial direction of the rotor shaft.
The vehicle drive device is characterized in that the sun gear fits on the outer peripheral surfaces of the rotor shaft and the annular member so as not to rotate relative to each other and rotates integrally with the rotating shaft. In the vehicle drive device according to claim 1,
A vehicle driving device characterized in that the annular member is fixed to one side of the rotor shaft in a state of being press-fitted into the sun gear. In the vehicle drive device according to claim 1 or 2.
The rotor shaft has a support portion that supports the rotor body, a fitting portion that fits the rotating shaft, and a connecting portion that connects the support portion and the fitting portion.
The vehicle driving device is characterized in that the connecting portion is connected to the fitting portion at a substantially central portion in the axial direction of the fitting portion. In the vehicle drive device according to any one of claims 1 to 3.
The vehicle driving device is characterized in that the planetary gear mechanism is arranged inside the rotor body in the radial direction.

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