JP2015052373A - Lubrication structure of power transmission device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly lubricate a bearing of a compound gear and a pinion gear by scattering of a lubricant discharged to the external from a rotating shaft, to an outer peripheral side by centrifugal force.SOLUTION: A lubricant flowing out from a radial oil passage 62 and scattering to an outer peripheral side by centrifugal force through a thrust bearing 34, is received by an oil receiver 64, and guided to a pinion lubricant passage 74 by a tapered cylindrical side wall portion 68, thus a pinion gear 22 can be properly lubricated by the lubricant. A part of the lubricant received by the oil receiver 64 escapes to the outer peripheral side from a plurality of through holes 72, so that a ball bearing 54 of a compound gear 52 can be properly lubricated by the lubricant.

Description

  The present invention relates to a lubricating structure for a power transmission device for a vehicle, and in particular, a lubricating structure for lubricating various parts by lubricating oil discharged to the outside from a supply oil passage provided on a rotating shaft to the outer peripheral side by centrifugal force. It is about improvement.

  (a) a composite gear integrally provided with a ring gear and an external gear of a planetary gear mechanism; (b) a rotating shaft disposed on the axis of the planetary gear mechanism; and (c) the rotating shaft. A carrier that is rotated integrally and supports a pinion gear meshing with the ring gear so as to be rotatable around a support shaft; and (d) the composite gear is supported so as to be rotatable outside the carrier in the axial direction. There is known a vehicle power transmission device having a bearing. The device described in Patent Document 1 is an example, and divides the power transmitted from the engine to the carrier through the rotating shaft into the sun gear and the ring gear via the pinion gear, and a motor generator is connected to the sun gear. The ring gear is provided with an output gear as the external gear. In this vehicular power transmission device, the pinion lubricant that opens to the side surface of the carrier when the lubricant discharged to the outside from the supply oil passage provided in the rotating shaft is blown to the outer peripheral side by centrifugal force. Supplyed to the path and the bearing, the pinion gear and the bearing are lubricated.

JP 2013-61046 A JP 2011-202775 A

  However, a sufficient amount of lubricating oil cannot be supplied to the pinion lubricating oil passage that is open on the side of the carrier simply by flying the lubricating oil to the outer peripheral side by centrifugal force. Lubrication may be insufficient. On the other hand, although not yet known, for example, it is conceivable to dispose a cylindrical oil receiver on the side surface of the carrier as described in Patent Document 2. However, in that case, there may be a shortage of lubricating oil for lubricating the composite gear bearing.

  The present invention has been made in the background of the above circumstances. The object of the present invention is to provide a bearing and a pinion gear of a composite gear by the lubricating oil discharged to the outside from the rotating shaft being blown to the outer peripheral side by centrifugal force. It is to be able to properly lubricate any of these.

  In order to achieve such an object, the present invention provides (a) a composite gear integrally including a ring gear and an external gear of a planetary gear mechanism, and (b) disposed on an axis of the planetary gear mechanism. A rotating shaft, (c) a carrier that is rotated integrally with the rotating shaft and supports a pinion gear that meshes with the ring gear so as to be rotatable about a support shaft, and (d) the composite gear is axially And (e) the lubricating oil discharged to the outside from the supply oil passage provided in the rotating shaft is centrifugal force. In the lubricating structure for lubricating the pinion gear and the bearing by being supplied to the pinion lubricating oil passage and the bearing that are opened to the side surface of the carrier by An oil receiver that extends in a cylindrical shape in the axial direction concentrically with the rotating shaft and receives the lubricating oil scattered to the outer peripheral side is provided on the side surface of the rotary shaft, and (g) the oil receiver The first guide portion for guiding the lubricating oil to the pinion lubricating oil passage, and the second guide portion for escaping to the outer peripheral side and supplying the first bearing portion to the bearing.

  In such a lubricating structure of the vehicle power transmission device, the lubricating oil scattered to the outer peripheral side due to the centrifugal force is received by the oil receiver and guided to the pinion lubricating oil passage through the first guide portion. The pinion gear is properly lubricated. Further, since a part of the lubricating oil received by the oil receiver is released to the outer peripheral side through the second guide portion, the composite gear bearing is appropriately lubricated by the lubricating oil. That is, the lubrication performance of the pinion gear and the bearing that are lubricated by the lubricating oil discharged from the supply oil passage and scattered to the outer peripheral side by centrifugal force is balanced with the oil receiver having the first guide portion and the second guide portion. Can do it.

It is sectional drawing of the power transmission device for vehicles to which this invention was applied. It is sectional drawing which expands and shows the principal part of the power transmission device for vehicles of FIG. 1, and is a figure explaining the lubrication structure which lubricates a pinion gear and a ball bearing. It is a figure explaining the other Example of this invention, and is sectional drawing corresponding to FIG. It is sectional drawing which expands and shows the part in which the oil receiver of the Example of FIG. 3 was provided. It is sectional drawing which expands and shows the part in which the oil receiver of the Example of FIG. 1 was provided, and is the figure which showed the state which the oil receiver floated from the side surface of the carrier with the centrifugal force hydraulic pressure of the lubricating oil of a counterbore part. .

  The present invention is preferably applied to, for example, a power split device that splits power transmitted from an engine to a carrier via a rotary shaft into a sun gear and a ring gear via a pinion gear. Is provided with an output gear as an external gear. The carrier may be integrally fixed to the rotary shaft by press-fitting or the like, but may be connected so as not to be relatively rotatable by spline fitting or the like. The composite gear that integrally includes the ring gear and the external gear may be constituted by a single member, but may be a member in which a plurality of members are integrally joined by press-fitting or welding.

  The oil receiver that extends in a cylindrical shape in the axial direction from the side surface of the carrier is preferably, for example, a tapered cylindrical shape having a smaller diameter toward the tip side, but a cylindrical oil receiver having a substantially constant diameter or a flat shape with a short axial dimension. An oil receiver can also be employed. The side wall of the tapered cylindrical shape or the like functions as a first guide part that directly guides the lubricating oil to the pinion lubricating oil path. As the second guide part that escapes to the outer peripheral side, for example, a through hole, a notch, or a slit provided in the side wall Etc. are appropriate. As the first guide portion, for example, a groove protruding to the outer peripheral side corresponding to the opening of the pinion lubricating oil passage may be provided, and the lubricating oil may be guided to the pinion lubricating oil passage through the groove.

  The pinion lubricating oil path is provided, for example, at the shaft center of a support shaft that rotatably supports the pinion gear, and the support shaft is integrally fixed to the carrier so as to penetrate the carrier, whereby the opening is formed. Although exposed on the side of the carrier, a pinion lubricating oil passage may be provided in the carrier. In the opening of the pinion lubricating oil passage, for example, a counterbore hole having a diameter larger than that of the pinion lubricating oil passage is provided. In this case, the oil receiver is integrally attached to the outer peripheral side of the counterbore hole. At the same time, in order to prevent the oil receiver from being deformed or lifted by the centrifugal hydraulic pressure of the lubricating oil staying in the counterbore, it is desirable to provide the oil receiver with a protruding portion that enters the counterbore. It is also possible to omit the counterbore.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified for explanation, and the dimensional ratios, shapes, etc. of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a cross-sectional view of a vehicle power transmission device 10 to which the present invention is applied. This vehicle power transmission device 10 is a power split device for a hybrid vehicle, and is composed mainly of a single pinion type planetary gear mechanism 12. Has been. The planetary gear mechanism 12 includes a carrier 16 that is integrally fixed to the input shaft 14 by press fitting, welding, or the like, a sun gear 18, and a ring gear 20. The sun gear 18 and the ring gear 20 are rotatable with respect to the carrier 16. Is engaged with a pinion gear 22 disposed on the surface. The input shaft 14 corresponds to a rotating shaft, and is supported by the first housing 24, the second housing 26, and the like so as to be rotatable around the axis O through a plurality of bearings, and the power of the engine 28 is transmitted. And rotated around the axis O. The axis O of the input shaft 14 corresponds to the axis of the planetary gear mechanism 12, and the sun gear 18 and the ring gear 20 are disposed around the axis O so as to be rotatable. The first housing 24 and the second housing 26 are integrally connected to each other by a bolt or the like (not shown).

  A plurality of (for example, three) support shafts 30 are integrally fixed to the carrier 16 in parallel with the axis O by press-fitting, welding, or the like, and the pinion gear 22 is supported by a pair of needle bearings 32. The shaft 30 is rotatably arranged. The carrier 16 is provided with a through hole, and the support shaft 30 is integrally fixed to the carrier 16 with the axial end surface thereof being substantially flush with the side surface of the carrier 16 through the through hole. Has been. The carrier 16 is provided on both sides in the axial direction across the pinion gear 22, and both end portions of the support shaft 30 are fixed to the carrier 16. The carriers 16 on both sides are integrally formed with each other, and the carrier 16 on the right side of the drawing, that is, the engine 28 side, is integrally fixed to the input shaft 14. The input shaft 14 is integrally provided with a flange-like portion 14f, and the carrier 16 is fitted and fixed integrally on the outer peripheral side of the flange-like portion 14f. A thrust bearing 34 is disposed between the flange-shaped portion 14f and the first housing 24, and their axial positions are defined in a state where the input shaft 14 and the carrier 16 are rotatable around the axis O. ing.

  The sun gear 18 is disposed on the outer peripheral side of the input shaft 14 via a needle bearing or the like so as to be relatively rotatable, and is connected to the motor generator MG via a transmission member 40 that is connected so as not to be relatively rotatable by spline fitting or the like. It is connected. Thrust bearings 42 and 44 are disposed between the sun gear 18 and the flange-shaped portion 14f and between the sun gear 18 and the second housing 26, respectively, so that the sun gear 18 can rotate around the axis O. The axial position is defined in the state.

  The ring gear 20 is integrally provided with an output gear 50 as an external gear, and the ring gear 20 and the output gear 50 constitute a composite gear 52. The output gear 50 is engaged with, for example, a counter gear provided on a counter shaft (not shown) disposed in parallel with the input shaft 14, and power is further transmitted from the counter shaft to the driving wheel side via a differential gear device or the like. Is transmitted. The compound gear 52 protrudes to the outside of the carrier 16 in the axial direction, and the shaft center O is formed by the first housing 24 and the second housing 26 via a pair of ball bearings 54 and 56 outside the carrier 16. It is supported so that it can rotate around. These ball bearings 54 and 56 are disposed on the inner peripheral side of the end portion in the axial direction of the composite gear 52 having a cylindrical shape.

  A supply oil passage 60 is provided in the shaft center O of the input shaft 14, and lubricating oil is supplied from an oil pump (not shown). The thrust bearing 34 is lubricated by the lubricating oil discharged from the radial oil passage 62 communicating with the supply oil passage 60, and the lubricating oil circulated through the thrust bearing 34 to the outer peripheral side is further caused by centrifugal force. By being blown to the outer peripheral side, it is received by the oil receiver 64 attached to the side surface of the carrier 16, and the pinion gear 22 and the ball bearing 54 are lubricated. The ball bearing 54 corresponds to a bearing lubricated by the lubricating oil supplied from the supply oil passage 60 via the oil receiver 64.

  FIG. 2 is an enlarged view of the lubricating structure portion, and the white arrow represents the flow of lubricating oil. The oil receiver 64 includes a flat annular mounting portion 66 that is brought into close contact with the outer peripheral side surface of the carrier 16, a side wall portion 68 that extends in a cylindrical shape in the axial direction from the inner peripheral edge of the mounting portion 66, A tip flange portion 70 is provided so as to slightly protrude from the tip end of the side wall portion 68 toward the inner peripheral side, and the attachment portion 66 is attached so as to be in close contact with the carrier 16 by caulking or the like (not shown). The side wall 68 has a tapered cylindrical shape with a smaller diameter on the tip side, and the lubricating oil received by the side wall 68 flows to the large diameter side of the tapered cylindrical shape, that is, the carrier 16 side by centrifugal force, A pinion lubricating oil passage 74 provided at the shaft center of the support shaft 30 is supplied to the pinion gear 22 through a radial oil passage 76 to lubricate the needle bearing 32 and further flow out to the outside, and the sun gear 18 and the ring gear 20. Lubricate the meshing part. A counterbore 78 having a diameter larger than that of the pinion lubricant path 74 is provided in the opening of the pinion lubricant path 74, and the oil receiver 64 is configured such that the mounting portion 66 blocks a part of the counterbore hole 78. Are attached to the outer peripheral portion of the carrier 16. The tapered cylindrical side wall portion 68 corresponds to a first guide portion.

  The cylindrical side wall 68 of the oil receiver 64 is provided with a through hole 72 at an axial intermediate portion, and a part of the received lubricating oil flows out from the through hole 72 to the outer peripheral side. Used to lubricate the ball bearing 54. The through holes 72 correspond to the second guide portion, and a plurality of through holes 72 are provided at equiangular intervals around the axis O. The number, size, position, etc. of the through holes 72 flow into the pinion lubricating oil passage 74. The lubricating performance for lubricating the pinion gear 22 and the lubricating performance for flowing out from the through hole 72 to the outer peripheral side and lubricating the ball bearing 54 are determined in a balanced manner.

  In such a lubricating structure of the vehicle power transmission device 10, the lubricating oil that flows out from the radial oil passage 62 and scatters to the outer peripheral side by centrifugal force through the thrust bearing 34 is received by the oil receiver 64, and the first guide Since it is guided to the pinion lubricating oil passage 74 by the tapered cylindrical side wall portion 68 as the portion, the pinion gear 22 is appropriately lubricated by the lubricating oil. Further, since a part of the lubricating oil received by the oil receiver 64 is released to the outer peripheral side from the plurality of through holes 72 functioning as the second guide portion, the ball bearing 54 of the composite gear 52 is appropriately caused by the lubricating oil. Lubricated. That is, the through hole 72 is provided in the tapered cylindrical side wall portion 68 to provide the lubricating performance of the pinion gear 22 and the ball bearing 54 that are lubricated by the lubricating oil that has flowed out of the radial oil passage 62 and scattered to the outer peripheral side by centrifugal force. The oil receiver 64 can achieve both in a balanced manner.

  In addition, a part of the lubricating oil received by the oil receiver 64 in this way is released from the through hole 72 to the outer peripheral side, so that it is prevented that the lubricating oil is excessively supplied to the pinion gear 22 side and the loss is deteriorated. At the same time, excessive centrifugal force hydraulic pressure due to a large amount of lubricating oil acts on the oil receiver 64 to prevent the oil receiver 64 from being deformed or the caulking portion from being damaged.

  Next, another embodiment of the present invention will be described. In the following embodiments, parts that are substantially the same as those in the above embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 3 is a cross-sectional view corresponding to FIG. 2, and an oil receiver 80 is different from that of the embodiment. 4 is an enlarged view of the vicinity of the oil receiver 80. The oil receiver 80 includes the mounting portion 66 and a side wall portion 68 provided with a plurality of through holes 72. The receiver 64 is the same as the receiver 64 except that a plurality of projecting portions 82 are provided corresponding to the counterbore holes 78 of the plurality of pinion lubricating oil passages 74 and that the tip flange portion 70 is not provided. . The protruding portion 82 is provided so as to enter the counterbore 78, but is provided at a position offset toward the outer peripheral side in the radial direction centering on the axis O. Further, the side wall 68 provided continuously from the inner peripheral side of the projecting portion 82 has an intersection S between the axial extension line of the inner peripheral surface and the bottom of the counterbore 78 of the pinion lubricating oil passage 74. It is provided so as to be located on the inner peripheral side with respect to the outer end edge. In the present embodiment, the position of the side wall portion 68 and the taper angle are determined so that the intersection point S is located at the same position as the center of the pinion lubricating oil passage 74 or on the outer peripheral side.

  According to such an oil receiver 80, since the protruding portion 82 is provided so as to enter the counterbore 78, the oil receiver 80 is deformed by the centrifugal force hydraulic pressure of the lubricating oil staying in the counterbore 78. It is advantageous in terms of strength. That is, for example, in the case of the oil receiver 64, as shown in FIG. 5, the centrifugal force hydraulic pressure P of the lubricating oil staying in the counterbore 78 causes a large force to act on the mounting portion 66 in the direction of rising from the carrier 16. There is a possibility that the caulking portion fixing the attachment portion 66 is damaged or the attachment portion 66 is deformed and floats up from the side surface of the carrier 16, and the lubricating oil leaks and the lubrication performance of the pinion gear 22 is impaired. On the other hand, in this embodiment, the amount of lubricating oil staying in the counterbore 78 is reduced by the amount of the protrusion 82 intruding, so that the centrifugal hydraulic pressure P is reduced and the mounting portion 66 is lifted from the carrier 16. This prevents the lubricant from leaking out.

  Further, in this embodiment, the intersection S between the extension line of the inner peripheral surface of the side wall 68 and the bottom of the counterbore 78 is the same as the outer end edge of the pinion lubricating oil passage 74, so that it is located on the inner peripheral side. Therefore, the lubricating oil received by the side wall portion 68 is smoothly introduced into the pinion lubricating oil passage 74. In particular, in this embodiment, the intersection S is located on the inner peripheral side of the pinion lubricating oil passage 74 or on the inner peripheral side thereof, and on the outer peripheral side of the pinion lubricating oil passage 74 or on the outer peripheral side thereof. Since the position of the side wall portion 68 and the taper angle are determined, the lubricating oil is introduced into the pinion lubricating oil passage 74 more smoothly.

  As mentioned above, although the Example of this invention was described in detail based on drawing, these are one Embodiment to the last, This invention is implemented in the aspect which added the various change and improvement based on the knowledge of those skilled in the art. be able to.

  10: Vehicle power transmission device 12: Planetary gear mechanism 14: Input shaft (rotary shaft) 16: Carrier 20: Ring gear 22: Pinion gear 30: Support shaft 50: Output gear (external gear) 52: Compound gear 54: Ball bearing (Bearing) 60: Supply oil passage 64, 80: Oil receiver 68: Side wall portion (first guide portion) 72: Through hole (second guide portion) 74: Pinion lubricating oil passage O: Shaft center

Claims (1)

A composite gear integrally including a ring gear and an external gear of a planetary gear mechanism;
A rotating shaft disposed on the axis of the planetary gear mechanism;
A carrier that is rotated integrally with the rotary shaft and supports a pinion gear meshing with the ring gear so as to be rotatable around a support shaft;
A bearing that rotatably supports the composite gear in an axial direction outside the carrier;
A pinion lubricating oil passage that opens to the side surface of the carrier when lubricating oil discharged to the outside from a supply oil passage provided on the rotating shaft is blown to the outer peripheral side by centrifugal force And a lubricating structure that is supplied to the bearing and lubricates the pinion gear and the bearing,
On the side surface of the carrier, an oil receiver that extends in a cylindrical shape in the axial direction concentrically with the rotating shaft and receives the lubricating oil scattered to the outer peripheral side is provided,
The oil receiver has a first guide portion that guides the received lubricating oil to the pinion lubricating oil passage, and a second guide portion that escapes to the outer peripheral side and supplies the lubricant to the bearing. Lubrication structure.

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