JP2016211701A - Power transmission device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress abrasion at a fitting face between an inner race of a second bearing and a cylindrical salient part of a case.SOLUTION: In a non-load region C in which a load is not applied between a cylindrical salient part 50 and an inner race 54a of a second bearing 54, a radial gutter is formed between an external peripheral face 50b of the cylindrical salient part 50 and an internal peripheral face 54ai of the inner race 54a, a return hole 62 which is formed at the cylindrical salient part 50 is formed in a position which is overlapped on the non-load region C viewed from a first axial core C1 in a radial direction, and thereby, oil which has passed the return hole 62 is liable to be filled into the radial gutter compared with the case that the return hole 62 is formed at a position which is not overlapped on the non-load region C. The oil filled in the radial gutter is also supplied to a load region in which a load is applied between the cylindrical salient part 50 and the inner race 54a by a turn of the inner race 54a with respect to the cylindrical salient part 50. Therefore, a fitting face B is liable to be lubricated over an entire periphery, and abrasion at the fitting face B can be suppressed.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a vehicular power transmission device including a rotating shaft, a case that supports the rotating shaft via a first bearing, and a rotating body that is supported by the case via a second bearing.

  A rotating shaft and a cylindrical protrusion that extends in the axial direction of the rotating shaft, and supports the rotating shaft in a relatively rotatable manner via a first bearing disposed on the inner peripheral surface of the cylindrical protruding portion. A non-rotatable case, and a rotating body that is disposed around the axis of the rotating shaft and supported by the case so as to be relatively rotatable via a second bearing disposed on the outer peripheral surface of the cylindrical protrusion. A vehicular power transmission device is well known. For example, this is the power transmission device (transaxle) described in Patent Document 1. In such a vehicle power transmission device, each member such as a gear and a bearing accommodated in the case is lubricated with oil. For example, the first bearing is lubricated by causing oil to flow out from a lubricating oil hole provided in the rotating shaft. The oil that has lubricated the first bearing is returned (discharged) to the lower part of the case through a return hole provided in the cylindrical protrusion of the case.

JP 2014-60857 A

  By the way, in the second bearing interposed between the rotating body and the cylindrical protruding portion of the case, the outer race is press-fitted into the rotating body, while the inner race is fitted to the outer peripheral surface of the cylindrical protruding portion of the case. In this case, the inner race may rotate relative to the cylindrical protruding portion of the case by dragging due to the rotation of the rotating body. In this case, wear may occur between the inner race and the outer peripheral surface of the cylindrical protrusion. Lubrication with oil is effective for such wear. However, although the oil passing through the return hole reaches the second bearing, the oil sufficient for lubrication does not always reach the fitting surface between the inner race and the outer peripheral surface of the cylindrical protrusion.

  The present invention has been made against the background of the above circumstances, and provides a vehicle power transmission device capable of suppressing wear on the fitting surface between the inner race of the second bearing and the cylindrical protruding portion of the case. There is to do.

  The gist of the first invention is that: (a) a rotating shaft rotatable around a first axis, and a cylindrical protrusion extending in the first axis direction, A non-rotatable case that supports the rotating shaft so as to be relatively rotatable via a first bearing disposed on a peripheral surface, and is disposed on the outer peripheral surface of the cylindrical projecting portion that is disposed around the first axis. A rotating body supported by the case so as to be relatively rotatable via a second bearing, and the rotating shaft supplies oil supplied to an internal hole provided along the first axial direction. Lubricating oil holes are provided to flow out to the inner peripheral surface side of the cylindrical projecting portion on which the bearing is disposed, and the cylindrical projecting portion causes the oil that has flowed out to the inner peripheral surface side to be on the second bearing side. The inner peripheral surface and the tip end portion of the cylindrical projecting portion in the first axial direction. A power transmission device for a vehicle provided with a return hole that communicates, wherein (b) the return hole is an inner side of the cylindrical projecting portion and the second bearing when viewed in the radial direction from the first axis. It exists in the position which overlaps with the non-load area | region where a load is not applied between races.

  In this way, the non-load region where no load is applied between the cylindrical protruding portion of the case and the inner race of the second bearing is the outer peripheral surface of the cylindrical protruding portion of the case and the inner race of the second bearing. There is a gap (radial play) between the inner peripheral surface, and the return hole provided in the cylindrical protrusion of the case is provided at a position overlapping the non-load area when viewed in the radial direction from the first axis. Compared with the case where the return hole is provided at a position where it does not overlap the non-load region, the oil that has passed through the return hole is easily filled in the radial play. The oil filled in the radial play is a load region where a load is applied between the cylindrical protruding portion of the case and the inner race of the second bearing due to the rotation of the inner race of the second bearing with respect to the cylindrical protruding portion of the case. (In other words, there is no radial backlash between the outer peripheral surface of the cylindrical protrusion of the case and the inner peripheral surface of the inner race of the second bearing, so that no oil is directly supplied to the fitting surface, and wear occurs. It is also supplied to easy areas). Accordingly, the fitting surface between the outer peripheral surface of the cylindrical protruding portion of the case and the inner race of the second bearing is easily lubricated over the entire periphery. Therefore, wear on the fitting surface between the inner race of the second bearing and the cylindrical protruding portion of the case can be suppressed.

  Here, the second invention is that in the vehicle power transmission device according to the first invention, a plurality of the return holes are provided. In this way, the oil that has passed through the return hole is more easily filled into the radial play. Accordingly, the fitting surface between the outer peripheral surface of the cylindrical protruding portion of the case and the inner race of the second bearing is more easily lubricated over the entire periphery.

  According to a third aspect of the present invention, in the vehicle power transmission device according to the first aspect, the cylindrical projecting portion communicates with a position in the middle of the return hole, and the inner race of the second bearing is provided. A through hole extending in the radial direction to the inner peripheral surface is provided. In this way, the oil that has passed through the return hole is more easily filled into the radial play. Accordingly, the fitting surface between the outer peripheral surface of the cylindrical protruding portion of the case and the inner race of the second bearing is more easily lubricated over the entire periphery.

  According to a fourth aspect of the invention, in the vehicle power transmission device according to the first aspect of the invention, the cylindrical protrusion is continuous with the end of the return hole at the tip in the first axial direction. In addition, a notch extending in the radial direction to the inner peripheral surface of the inner race of the second bearing is provided. In this way, the oil that has passed through the return hole is more easily filled into the radial play. Accordingly, the fitting surface between the outer peripheral surface of the cylindrical protruding portion of the case and the inner race of the second bearing is more easily lubricated over the entire periphery.

  According to a fifth aspect of the present invention, there is provided the vehicle power transmission device according to the first aspect, wherein the engine is disposed around the first shaft center and connected to the first electric motor and the rotary shaft. And a planetary gear mechanism having a ring gear formed on an inner peripheral surface of the rotating body, and an outer peripheral surface of the rotating body disposed around a second axis parallel to the first axis. And a driven gear for transmitting power from a second electric motor that is arranged around a third axis parallel to the first axis and that is engaged with the drive gear formed on the first gear. It is a region opposite to the driven gear side on the inner peripheral surface of the inner race of the bearing. In this case, the return hole provided in the cylindrical projecting portion of the case is provided in a region opposite to the driven gear side, so that the oil that has passed through the return hole is provided compared to the return hole provided in the region on the driven gear side. Is easy to fill the radial backlash.

It is a figure explaining schematic structure of the power transmission device for vehicles to which the present invention is applied. It is sectional drawing which shows the structure of the transmission part arrange | positioned around the 1st axis center, and its periphery among the power transmission devices for vehicles of FIG. It is the external view which looked at the 1st case simple substance from the 1st electric motor side to the engine side in the 1st axis direction. It is a figure for demonstrating the load sphere direction of a 2nd bearing. FIG. 3 is a cross-sectional view showing a configuration of a transmission unit disposed around a first axis and its surroundings, which is an embodiment different from FIG. 2. FIG. 3 is a cross-sectional view showing a configuration of a transmission unit disposed around a first axis and its surroundings, which is an embodiment different from FIG. 2. FIG. 4 is an external view of the first case alone viewed from the first electric motor side to the engine side in the first axial direction, and is an embodiment different from FIG. 3.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a diagram illustrating a schematic configuration of a vehicle power transmission device 12 (hereinafter referred to as a power transmission device 12) provided in a hybrid vehicle 10 (hereinafter referred to as a vehicle 10) to which the present invention is applied. In FIG. 1, a vehicle 10 includes a power transmission device 12, an engine 14 as a main driving force source, driving wheels 16, a first electric motor MG1, and a second electric motor MG2 as a sub driving power source. . The power transmission device 12 is provided in a power transmission path between the engine 14 and the drive wheel 16 and is accommodated in a non-rotatable case 18 that is a non-rotating member attached to the vehicle body.

  The power transmission device 12 includes a damper 20 coupled to the engine 14, an input shaft 22 serving as a rotation shaft coupled to the damper 20, a transmission unit 24 coupled to the input shaft 22, and a rotation constituting a part of the transmission unit 24. The counter driven gear 30 as a driven gear that meshes with the counter drive gear 28 as the drive gear formed on the outer peripheral surface 26b of the output member 26 as a body, and the driven shaft 32 that fixes the counter driven gear 30 in a relatively non-rotatable manner. The provided final gear 34 (final gear 34 having a smaller diameter than the counter driven gear 30), the differential gear 36 that meshes with the final gear 34 via the differential ring gear 36a, and the reduction gear that meshes with the counter driven gear 30 and is connected to the second electric motor MG2. 38 (Counted A reduction gear 38 having a diameter smaller than that of the gear 30), a pump drive shaft 40 connected to the input shaft 22 so as not to be relatively rotatable by spline fitting, and the input shaft 22 being rotated by the engine 14 via the pump drive shaft 40. And an oil pump 42 that is driven by the motor. In the power transmission device 12 configured as described above, the power of the engine 14 and the power of the second electric motor MG2 are transmitted to the counter driven gear 30, and the counter driven gear 30 sequentially passes through the final gear 34, the differential gear 36, the axle, and the like. Is transmitted to the drive wheel 16.

  The power transmission device 12 is suitably used for an FF (front engine / front drive) type vehicle. The power transmission device 12 has four parallel axes. Specifically, it is the axis of the input shaft 22 that is rotatably arranged, and the first axis C1 and the driven shaft in which the engine 14, the transmission unit 24, and the first electric motor MG1 are arranged around the axis. A third axis about which the counter driven gear 30 and the final gear 34 are arranged, and a second electric motor MG2 and a reduction gear 38 are arranged around the axis. C4 has a fourth axis C4 in which a differential gear 36 is disposed around the axis. Thus, in the power transmission device 12, the shaft length is shortened by arranging the engine 14, the transmission unit 24, the first electric motor MG1, and the second electric motor MG2 on different axes.

  The transmission unit 24 includes a planetary gear mechanism 44 as a power distribution mechanism that distributes the power transmitted from the engine 14 via the input shaft 22 to the first electric motor MG1 and the output member 26. The planetary gear mechanism 44 includes a known single pinion type planetary gear device including a sun gear S, a pinion gear P, a carrier CA that supports the pinion gear P so as to be capable of rotating and revolving, and a ring gear R that meshes with the sun gear S via the pinion gear P. It functions as a differential mechanism that generates a differential action. In the planetary gear mechanism 44, the sun gear S is connected to the first electric motor MG1, the carrier CA is connected to the engine 14 via the input shaft 22, and the ring gear R is formed on the inner peripheral surface 26a of the output member 26. In the planetary gear mechanism 44 configured as described above, the first electric motor MG1 is generated by the power of the engine 14 distributed to the first electric motor MG1, and the generated electric power is stored or the second electric motor MG2 is stored by the electric power. Driven. Thus, the transmission unit 24 functions as an electric differential unit (electric continuously variable transmission) that controls the gear ratio by controlling the operating state of the first electric motor MG1.

  The oil pump 42 supplies hydraulic oil (oil) used for lubrication and cooling of each part of the power transmission device 12 such as the differential gear 36, the reduction gear 38, the planetary gear mechanism 44, and a ball bearing.

  FIG. 2 is a cross-sectional view showing the configuration of the transmission unit 24 arranged around the first axis C1 and its surroundings in the same plane in the power transmission device 12 of FIG. In FIG. 2, the transmission unit 24 and the first electric motor MG <b> 1 are accommodated in the case 18. The case 18 forms a gear chamber 46 that houses the transmission unit 24, the counter driven gear 30, and the like, and a motor chamber 48 that houses the first electric motor MG1 and the second electric motor MG2. The case 18 includes a bottomed cylindrical first case 18a that mainly forms the gear chamber 46, a cylindrical second case 18b that includes a partition that partitions the gear chamber 46 and the motor chamber 48, and the like. The first case 18a and the second case 18b are connected to each other.

  The first case 18a is provided with a cylindrical projecting portion 50 on the radially inner peripheral side extending inward of the case in the direction of the first axis C1 (that is, on the gear chamber 46 side). In the first case 18a, a first bearing 52 is disposed on the inner peripheral surface 50a of the cylindrical projecting portion 50, and a second bearing 54 is disposed on the outer peripheral surface 50b of the cylindrical projecting portion 50. The first case 18a supports the input shaft 22 on the inner peripheral surface 50a of the cylindrical protrusion 50 via the first bearing 52 so as to be relatively rotatable. The first case 18a supports the output member 26 on the outer peripheral surface 50b of the cylindrical protruding portion 50 via the second bearing 54 so as to be relatively rotatable.

  As described above, in the power transmission device 12, members such as gears and bearings constituting the power transmission device 12 are lubricated with oil supplied from the oil pump 42. In order to prevent this oil from leaking out of the case 18, for example, a gap between the input shaft 22 and the outer end of the inner peripheral surface 50 a of the first case 18 a (tubular protrusion 50) is sealed with an oil seal 56. Yes. While the oil seal 56 is fixed to the first case 18a, the oil seal 56 rotates relative to the input shaft 22. Therefore, the oil seal 56 may be worn between the input shaft 22 and cause oil leakage. Therefore, in the power transmission device 12 of the present embodiment, a configuration is adopted in which the oil seal 56 is lubricated with oil that has lubricated the first bearing 52 disposed in the vicinity of the oil seal 56.

  Specifically, on the input shaft 22, oil supplied to an internal hole 58 provided along the direction of the first axis C <b> 1 is supplied with the inner peripheral surface 50 a of the cylindrical protrusion 50 in which the first bearing 52 is disposed. A lubricating oil hole 60 is provided to flow out to the side. Further, the cylindrical protrusion 50 is provided with a return hole 62 through which oil that has flowed out to the inner peripheral surface 50a side flows out to the second bearing 54 side. The return hole 62 communicates the inner peripheral surface 50a and the distal end portion 50c in the direction of the first axis C1 of the cylindrical projecting portion 50, which is the side surface of the cylindrical projecting portion 50 inside the case (that is, the gear chamber 46 side). It is provided to do. As indicated by an arrow A, the oil supplied to the inner hole 58 of the input shaft 22 and discharged from the lubricating oil hole 60 lubricates the first bearing 52 and then travels through the input shaft 22 to the oil seal 56. It reaches and lubricates between the input shaft 22 and the oil seal 56. This oil is returned (discharged) to the lower portion of the case 18 through a return hole 62 provided in the cylindrical protrusion 50.

  Here, in the second bearing 54, for example, the inner race 54a is fitted to the outer peripheral surface 50b of the cylindrical protrusion 50, and the outer race 54b is the end of the inner peripheral surface 26a of the output member 26 on the cylindrical protrusion 50 side. The structure is press-fitted into. Therefore, the inner race 54a is the fixed side, and the outer race 54b is the rotation side. In such a structure, the inner race 54 a is not completely fixed to the outer peripheral surface 50 b of the cylindrical protrusion 50, and the cylindrical protrusion is caused by dragging due to the rotation of the outer race 54 b accompanying the rotation of the output member 26. 50 may rotate relative to the outer peripheral surface 50b. In this case, wear may occur between the inner race 54 a and the outer peripheral surface 50 b of the cylindrical protrusion 50. For such wear, it is effective to lubricate with oil discharged through the return hole 62 provided in the cylindrical protrusion 50. However, although oil that has passed through the return hole 62 reaches the second bearing 54, oil that is sufficient for lubrication reaches the fitting surface B between the inner race 54 a and the outer peripheral surface 50 b of the cylindrical protrusion 50. Not exclusively.

  Therefore, in the power transmission device 12 of the present embodiment, as shown in FIG. 3, the return hole 62 has a cylindrical protruding portion 50 (particularly, the cylindrical protruding portion 50 as viewed in the radial direction from the first axis C1). Between the outer peripheral surface 50b) and the inner race 54a of the second bearing 54 (in other words, the fitting surface B) is provided at a position overlapping the non-load region C where no load is applied (that is, the non-load region). C is provided at a position overlapping with C in the circumferential direction). 3 shows the first case 18a alone (that is, the first case 18a in a state where the input shaft 22, the first and second bearings 52, 54, etc. are not assembled) in the direction of the first axis C1 on the first motor MG1 side. It is the external view seen from the engine 14 side. In FIG. 3, the positive x direction is forward of the vehicle 10, and the positive y direction is downward of the vehicle 10. In the power transmission device 12 of the present embodiment, the arrangement of the shaft centers C1-C4 is as illustrated in FIG. 3 (note that FIG. 1 is a diagram developed in a plane). In the power transmission device 12, the non-load region C includes a counter driven gear 30 side disposed around the second axis C2 on the inner peripheral surface 54ai (in other words, the fitting surface B) of the inner race 54a of the second bearing 54. Is the opposite area. In the non-load region C, a gap (radial backlash) is formed on the fitting surface B between the inner race 54a of the second bearing 54 and the cylindrical protrusion 50, so that it is provided at a position overlapping the non-load region C in the circumferential direction. This gap is easily filled with oil that has passed through the return hole 62. As a result, due to the relative rotation of the inner race 54a with respect to the outer peripheral surface 50b of the cylindrical projecting portion 50, the load zone side where the load is applied to the fitting surface B is easily efficiently lubricated. Therefore, the return hole 62 has both a function of discharging oil and a lubrication position that is effective in wear resistance of the second bearing 54. The return hole 62 may be provided at a position overlapping the non-load region C in the circumferential direction. However, when the non-load region C is in the lower direction of the vehicle 10 as in this embodiment, the oil seal 56 and the input are provided. From the viewpoint of storing oil on the sliding surface with the shaft 22, it is desirable not to form it in the direction directly below the vehicle 10 or in the vicinity thereof.

  FIG. 4 is a diagram for explaining the direction of the load zone of the second bearing 54 when the engine 14 is driven. 4A, in the same manner as FIG. 3, the counter drive gear 28, the counter driven gear 30, the final gear 34, the diff ring gear 36a, and the reduction gear 38 are arranged from the first electric motor MG1 side in the direction of the respective axes C1-C4. It is the external view seen to 14 side. In FIG. 4A, the positive x direction is the forward direction of the vehicle 10, the positive y direction is the downward direction of the vehicle 10, and the positive z direction (not shown) is the left hand (LH) direction of the vehicle 10 (the positive direction of the thrust force). is there. FIG. 4B is a diagram showing the meshing reaction force during acceleration with arrows in the mutual connection relationship of the gears 28, 30, 34, 36 a, 38 and the planetary gear mechanism 44. In FIG. 4, the output member 26 meshes with the counter driven gear 30 with external teeth (that is, the counter drive gear 28), and meshes with the pinion gear P of the planetary gear mechanism 44 with internal teeth (that is, the ring gear R). The meshing reaction force is generated in the counter drive gear 28, and the second bearing 54 assembled to the output member 26 receives a load, for example, in the direction of arrow D in FIG. When a load is generated as indicated by an arrow D in FIG. 4, the upper side of the vehicle 10 that is pressed by the load is a load zone, and the lower side of the vehicle 10 is a non-load zone.

  As described above, due to the meshing of the gear, a component force such as a load in the tangential direction, a load in the axial direction, and a load in the thrust direction corresponding to the torsion angle is generated in the gear. The side that is pressed against is the load zone, and the side that is not pressed is the non-load zone. The direction in which the gear is pressed varies depending on, for example, the rotational direction of the gear, the gear diameter, the distance between a plurality of bearings that support a certain rotating member, the position of the gear, and the like. In the hardware configuration of the power transmission device 12 of the present embodiment, the area on the counter driven gear 30 side on the fitting surface B is a load zone and there is a non-load area C in the lower direction of the vehicle 10 (see FIG. 3). Is merely an example, and the relationship between the load zone (non-load zone) and the gear pair (counter drive gear 28, counter driven gear 30) is not uniquely determined and is determined for each vehicle (power transmission device) by a hardware configuration.

  As described above, according to the present embodiment, the non-load region C where no load is applied between the cylindrical protrusion 50 of the first case 18a and the inner race 54a of the second bearing 54 is the cylindrical protrusion. 50 is formed between the outer peripheral surface 50b of the inner race 54a and the inner peripheral surface 54ai of the inner race 54a, and the return hole 62 provided in the cylindrical projecting portion 50 is viewed from the first axis C1 in the radial direction. By providing it at a position that overlaps with the non-load region C, compared with providing the return hole 62 at a position that does not overlap with the non-load region C, the oil that has passed through the return hole 62 is easily filled into the radial play. The oil filled in the radial backlash is a load region in which a load is applied between the cylindrical protrusion 50 and the inner race 54a by the rotation of the inner race 54a with respect to the cylindrical protrusion 50 (that is, the cylindrical protrusion 50). Since there is no radial backlash between the outer peripheral surface 50b and the inner peripheral surface 54ai of the inner race 54a, the oil is not supplied directly to the fitting surface B and is also supplied to a region where wear easily occurs. Therefore, the fitting surface B between the outer peripheral surface 50b of the cylindrical protrusion 50 and the inner race 54a is easily lubricated over the entire periphery. Therefore, wear on the fitting surface B between the inner race 54a and the cylindrical protrusion 50 can be suppressed.

  Further, according to the present embodiment, in the hardware configuration of the power transmission device 12, the non-load region C is a region opposite to the counter driven gear 30 side on the inner peripheral surface 54ai of the inner race 54a. By providing it in the region opposite to the counter driven gear 30 side, the oil that has passed through the return hole 62 is more easily filled in the radial play compared to providing the return hole 62 in the region on the counter driven gear 30 side.

  Next, another embodiment of the present invention will be described. In the following description, parts common to the embodiments are denoted by the same reference numerals and description thereof is omitted.

  FIG. 5 is a cross-sectional view showing the structure of the transmission unit 24 arranged around the first axis C1 and its surroundings, which is an embodiment different from FIG. In FIG. 5, the cylindrical protrusion 50 communicates with a position in the middle of the return hole 62 in addition to the return hole 62, so that the inner peripheral surface 54 ai (in other words, the fitting surface) of the inner race 54 a of the second bearing 54. A through hole 64 extending in the radial direction up to B) is provided. In the through hole 64, a chamfer 64a is formed at an end portion on the inner peripheral surface 54ai side of the inner race 54a on the side from which oil flows out.

  As described above, according to the present embodiment, since the cylindrical protrusion 50 is provided with the through hole 64 in addition to the return hole 62, the oil that has passed through the return hole 62 is more easily filled into the radial play. Become. Therefore, the fitting surface B is more easily lubricated over the entire circumference. Further, since the chamfer 64a is formed in the through hole 64, the oil is easily drawn by the inner race 54a.

  FIG. 6 is a cross-sectional view showing the configuration of the transmission unit 24 arranged around the first axis C1 and its surroundings, which is an embodiment different from FIG. In FIG. 6, the cylindrical projecting portion 50 is continuous with the end of the return hole 62 on the side from which oil flows out at the front end portion 50 c in the direction of the first axis C <b> 1. A notch 66 extending in the radial direction to the peripheral surface 54ai (in other words, the fitting surface B) is provided.

  As described above, according to the present embodiment, the cylindrical projecting portion 50 passes through the return hole 62 because the notch 66 is provided continuously at the end portion of the return hole 62 at the distal end portion 50c. Oil is more easily filled into the radial play. Therefore, the fitting surface B is more easily lubricated over the entire circumference.

  FIG. 7 is an external view of the first case 18a alone viewed from the first motor MG1 side to the engine 14 side in the first axis C1 direction, and is an embodiment different from FIG. In FIG. 7, a plurality (two in this embodiment) of the return holes 62 are provided in the cylindrical protrusion 50 at a position overlapping the non-load region C when viewed in the radial direction from the first axis C1. The return hole 62 is provided at a position where the oil filled in the radial play is more likely to spread around the entire circumference of the fitting surface B in consideration of the forward direction and the reverse direction of the vehicle 10. In the embodiment of FIG. 7, the through hole 64 extending from the return hole 62 to the fitting surface B shown in the second embodiment is provided.

  As described above, according to the present embodiment, since the plurality of return holes 62 are provided, the oil that has passed through the return holes 62 is more easily filled into the radial play. Therefore, the fitting surface B is more easily lubricated over the entire circumference.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the above-described second embodiment, the chamfer 64a is formed in the through hole 64, but the chamfer 64a may not be formed. Further, in the notch 66 in the above-described third embodiment, a chamfer similar to the chamfer 64a may be formed at the end portion on the inner peripheral surface 54ai side of the inner race 54a of the second bearing 54.

  In the above-described embodiment, the planetary gear mechanism 44 is a single pinion type planetary gear device, but is not limited thereto. For example, the planetary gear mechanism 44 may be a double pinion type planetary gear device or a differential mechanism including a plurality of planetary gear devices. Further, instead of the planetary gear mechanism 44, the differential mechanism may be configured by a known differential gear device having a bevel gear.

  In the above-described embodiment, the invention has been described using the power transmission device 12 that is preferably used for the FF vehicle. However, the present invention is applied to a power transmission device that is used for other vehicles such as the RR method. Can also be applied as appropriate.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

12: Vehicle power transmission device 14: Engine 18: Case 22: Input shaft (rotating shaft)
26: Output member (rotating body)
26a: inner peripheral surface 26b: outer peripheral surface 28: counter drive gear (drive gear)
30: Counter driven gear (driven gear)
44: planetary gear mechanism S: sun gear CA: carrier R: ring gear 50: cylindrical protrusion 50a: inner peripheral surface 50b: outer peripheral surface 50c: tip 52: first bearing 54: second bearing 54a: inner race 54ai: inner Peripheral surface 58: Internal hole 60: Lubricating oil hole 62: Return hole 64: Through hole 66: Notch C: Non-load area C1: First axis C2: Second axis C3: Third axis MG1: First 1 electric motor MG2: 2nd electric motor

Claims (5)

The rotating shaft has a rotating shaft rotatable around a first axis and a cylindrical protrusion extending in the first axis direction, and the rotation is performed via a first bearing disposed on an inner peripheral surface of the cylindrical protrusion. A non-rotatable case that supports the shaft so as to be relatively rotatable, and a second bearing that is disposed around the first shaft center and that is disposed on the outer peripheral surface of the cylindrical protruding portion. An inner peripheral surface of the cylindrical projecting portion in which the first bearing is provided with oil supplied to an inner hole provided along the first axial direction. An oil hole for lubrication that flows out to the side is provided, and the cylindrical projecting portion allows the oil that has flowed out to the inner peripheral surface side to flow out to the second bearing side, and the cylindrical projecting portion Vehicle provided with a return hole that communicates with the tip end portion of the first axial direction The power transmission device,
The return hole is provided at a position overlapping a non-load region where no load is applied between the cylindrical projecting portion and the inner race of the second bearing when viewed in the radial direction from the first axis. A power transmission device for a vehicle.   The vehicle power transmission device according to claim 1, wherein a plurality of the return holes are provided.   2. The cylindrical projection is provided with a through hole that communicates with a position in the middle of the return hole and extends in a radial direction to an inner peripheral surface of an inner race of the second bearing. The vehicle power transmission device according to claim 1.   The cylindrical projecting portion is provided with a notch extending in the radial direction to the inner peripheral surface of the inner race of the second bearing at the distal end portion in the first axial direction, continuously to the end portion of the return hole. The vehicle power transmission device according to claim 1, wherein the vehicle power transmission device is provided. A planetary gear disposed around the first axis and having a sun gear to which the first electric motor is connected, a carrier to which the engine is connected via the rotating shaft, and a ring gear formed on the inner peripheral surface of the rotating body. Mechanism,
Arranged around a second axis parallel to the first axis, meshed with a drive gear formed on the outer peripheral surface of the rotating body, and arranged around a third axis parallel to the first axis A driven gear to which power from the second electric motor is transmitted,
2. The vehicle power transmission device according to claim 1, wherein the non-load region is a region opposite to the driven gear side on the inner peripheral surface of the inner race of the second bearing.

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