JP2015052374A - Lubrication structure of power transmission device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure a sufficient amount of lubricant scattering to an outer peripheral side by centrifugal force and received by an oil receiver, even when a boss portion is disposed on a housing.SOLUTION: As an outer diameter D1 of a first race 36 at a carrier 16 side of a thrust bearing 34 is larger than a radial dimension D2 of a boss portion 39 disposed on a first housing 24, a lubricant passing through the thrust bearing 34 flows not only to the boss portion 39 side but also to the first race 36 side by viscosity, and scatters to an outer peripheral side from an outer peripheral edge of the first race 36 to be received by an oil receiver 64, thus the amount of lubricant supplied to a pinion lubricant passage 74 is increased.

Description

  The present invention relates to a lubricating structure for a power transmission device for a vehicle, and in particular, the lubricating oil discharged to the outside from a supply oil passage provided on a rotating shaft is received by an oil receiver by being blown to the outer peripheral side by centrifugal force. The present invention relates to an improvement of a lubricating structure for lubricating a pinion gear.

  (a) a rotating shaft disposed at the axis of the planetary gear mechanism, (b) a carrier fixed integrally with the rotating shaft and rotatably supporting the pinion gear, and (c) a shaft In the direction, the carrier or the rotary shaft is disposed between a portion where the carrier is fixed and the housing, and the rotary shaft and the carrier are rotatable around the axis. There is known a vehicular power transmission device having a thrust bearing that defines an axial position of the vehicle. 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 external output gear. And in this vehicle power transmission device, the lubricating oil discharged to the outside from the supply oil passage provided in the rotating shaft is blown to the outer peripheral side by centrifugal force through the thrust bearing, so that the side surface of the carrier The pinion gear is lubricated by being supplied to the open pinion lubricating oil passage. On the other hand, Patent Document 2 describes a technique in which a tapered cylindrical oil receiver is provided on a side surface of a carrier, and lubricating oil that has been blown to the outer peripheral side is efficiently received and introduced into a pinion lubricating oil path.

JP 2013-61046 A JP 2011-202775 A

  However, even when the oil receiver is provided in this way, the lubricating oil cannot always be sufficiently introduced into the pinion lubricating oil path, and the pinion lubricating performance as expected may not be obtained. In other words, if the housing supporting one race of the thrust bearing is provided with a boss part on the outer peripheral side of the race, the lubricating oil that has passed through the thrust bearing will travel along the boss part due to viscosity to the housing. The amount of lubricating oil that flows to the outer peripheral side along the periphery, scatters from the thrust bearing to the outer peripheral side, and is received by the oil receiver is insufficient.

  The present invention has been made in the background of the above circumstances, and the object of the present invention is to provide a lubricating oil that is blown to the outer peripheral side by centrifugal force and received by an oil receiver even when a boss portion is provided in the housing. The purpose is to ensure a sufficient amount.

In order to achieve such an object, the present invention provides (a) a rotating shaft disposed on the axis of a planetary gear mechanism, and (b) a pinion gear that is integrally fixed to the rotating shaft and rotates a pinion gear. A carrier that is supported, and (c) in the axial direction, disposed between the carrier or a portion of the rotating shaft where the carrier is fixed and a housing, and the rotating shaft and the carrier. A thrust bearing that defines the axial position of the shaft in a state where the shaft is rotatable around the shaft center, and (d) externally from a supply oil passage provided on the rotation shaft. The lubricating oil discharged to the outer periphery is blown to the outer peripheral side by centrifugal force through the thrust bearing, and is received by the oil receiver provided on the side surface of the carrier and supplied to the pinion lubricating oil path. (E) a first race on the carrier side of the thrust bearing is disposed on an inner peripheral side portion of the oil receiver in the axial direction, and is provided on the opposite side of the lubricating structure for lubricating the pinion gear. The housing supporting two races is provided with a boss portion protruding toward the carrier side on the outer peripheral side portion than the second race, and (f) the outer diameter of the first race is The diameter is larger than the diameter of the portion where the boss is provided.
In addition, the diameter dimension of the part provided with the boss part is a diameter dimension at the maximum projecting position of the boss part projecting toward the carrier side. In the first race, at least the projecting dimension of the boss part proceeds toward the outer peripheral side. It only has to reach the position where it starts to decrease.

  In such a lubrication structure for a vehicle power transmission device, since the outer diameter of the first race on the carrier side of the thrust bearing is larger than the boss portion provided in the housing, the lubrication that has passed through the thrust bearing The oil flows not only to the boss part side but also to the first race side due to viscosity, and is received by the oil receiver by being scattered from the outer peripheral edge of the first race to the outer peripheral side and supplied to the pinion lubricating oil passage. Increase the amount of lubricating oil. Thereby, a predetermined pinion lubrication performance can be ensured.

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 lubricating structure which lubricates a pinion gear. It is a figure explaining the background art used as the premise of this invention in which the outer diameter of a pair of race of a thrust bearing is substantially equal, It is sectional drawing corresponding to FIG. It is sectional drawing explaining the incorrect assembly | attachment of a thrust bearing in the background art of FIG. It is sectional drawing explaining another example of the incorrect assembly | attachment of a thrust bearing.

  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 external gear. The carrier is integrally fixed to the rotary shaft by press fitting, welding, or the like. The carrier can be fixed to the outer peripheral surface of the rotating shaft, but a flange-like portion may be integrally provided on the rotating shaft, and the carrier may be fixedly fitted to the outer peripheral side of the flange-like portion. . When the carrier is fixed on the outer peripheral surface of the rotating shaft, a thrust bearing may be disposed between the carrier and the housing. When the carrier is fixed on the outer peripheral side of the flange-shaped portion, the flange shape A thrust bearing may be disposed between the part and the housing.

  An oil receiver is provided on the side surface of the carrier so as to extend in a cylindrical shape in the axial direction concentrically with the rotating shaft. The oil receiver is preferably a tapered cylindrical shape having a smaller diameter toward the tip side, for example. A cylindrical oil receiver having a substantially uniform diameter or a flat oil receiver having a short axial dimension can also be employed. 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.

  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 external output gear 50, 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 to the outer peripheral side through the thrust bearing 34 is further caused by centrifugal force. By being blown to the outer peripheral side, the pinion gear 22 is lubricated by being received by a cylindrical oil receiver 64 attached to the side surface of the carrier 16 concentrically with the input shaft 14. A part of the lubricating oil flowing to the outer peripheral side through the thrust bearing 34 passes through the outer side of the oil receiver 64, that is, the right side in FIG. 1 and scatters to the outer peripheral side to be used for lubricating the ball bearing 54. .

  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 thrust bearing 34 includes a first race 36 on the carrier 16 side, that is, the flange-like portion 14f side, a second race 38 on the first housing 24 side, and a number of rollers 37 disposed therebetween. A number of rollers 37 are held by the first race 36. The first race 36 is disposed on the inner peripheral side portion of the oil receiver 64 in the axial direction. The first housing 24 that supports the second race 38 is provided with a boss portion 39 that protrudes toward the carrier 16 on the outer peripheral side of the second race 38. The diameter D1 is larger than the diameter D2 of the portion where the boss portion 39 is provided. That is, the outer diameter D1 of the first race 36, the outer diameter D3 of the second race 38, and the diameter dimension D2 of the boss portion 39 have a relationship of D1> D2> D3. These outer diameters D1, D3 and diameter dimension D2 are diameter dimensions centered on the axis O, and the diameter dimension D2 of the boss part 39 is at the maximum projecting position of the boss part 39 projecting toward the carrier 16 side. Diameter dimension. The outer diameter D1 of the first race 36 is sufficiently larger than the diameter dimension D2, and the protrusion dimension of the boss portion 39 decreases as it goes toward the outer peripheral side, and is larger than the diameter dimension at a position where it becomes 1/2. In the present embodiment, the outer peripheral edge of the first race 36 has reached a position completely beyond the boss portion 39.

  In such a lubricating structure of the vehicle power transmission device 10, the outer diameter D1 of the first race 36 on the carrier 16 side of the thrust bearing 34 is larger than the diameter D2 of the boss portion 39 provided in the first housing 24. Because of the diameter, the lubricating oil that has passed through the thrust bearing 34 flows not only to the boss portion 39 side but also to the first race 36 side due to viscosity, and is scattered from the outer peripheral edge of the first race 36 to the outer peripheral side. As a result, the amount of lubricating oil received by the oil receiver 64 and supplied to the pinion lubricating oil passage 74 increases. In particular, in this embodiment, since the outer peripheral edge of the first race 36 reaches a position completely beyond the boss portion 39, the amount of lubricating oil flowing toward the outer peripheral side along the first race 36 rather than the boss portion 39 side. And the oil amount necessary for lubricating the pinion gear 22 and the oil amount necessary for lubricating the ball bearing 54 are appropriately divided. Thereby, a predetermined pinion lubrication performance can be ensured, and the lubrication performance of the pinion gear 22 and the ball bearing 54 can be balanced and balanced.

  In addition, since the outer diameter D1 of the first race 36 is larger than the outer diameter D3 of the second race 38, it is possible to appropriately prevent erroneous assembly by managing the height position of the outer diameter of the race when assembling them. Can be prevented.

  Incidentally, FIG. 3 is a diagram for explaining a lubricating structure which is a premise of the present invention in which the thrust bearing 80 in which the outer diameter D1 of the first race 82 is substantially equal to the outer diameter D3 of the second race 38 is used. In this case, the lubricating oil that has passed through the thrust bearing 80 tends to flow to the first housing 24 side through the boss portion 39 due to viscosity as indicated by an arrow Q. For this reason, the amount of lubricating oil scattered from the thrust bearing 80 as it is to the outer peripheral side and received by the oil receiver 64 decreases, and there is a possibility that the amount of lubricating oil used to lubricate the pinion gear 22 may be insufficient.

  Further, since the outer diameter D1 of the first race 82 and the outer diameter D3 of the second race 38 are substantially equal, it cannot be distinguished by the height position management of the race outer diameter, as shown in FIG. 4 and FIG. Incorrect assembly may occur. FIG. 4 shows a case where the first race 82 and the second race 38 are assembled in the opposite directions, and FIG. 5 shows a case where the first race 82 is assembled in the reverse direction.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this is an embodiment to the last, and this invention is implemented in the aspect which added various change and improvement based on the knowledge of those skilled in the art. Can do.

  10: Vehicle power transmission device 12: Planetary gear mechanism 14: Input shaft (rotating shaft) 14f: Flange-shaped part 16: Carrier 22: Pinion gear 24: First housing (housing) 34: Thrust bearing 36: First race 38: Second race 39: Boss portion 60: Supply oil passage 64: Oil receiver 74: Pinion lubricating oil passage O: Axis center D1: Outer diameter of the first race D2: Diameter dimension of the boss portion

Claims (1)

A rotating shaft disposed on the axis of the planetary gear mechanism;
A carrier that is integrally fixed to the rotating shaft and that rotatably supports the pinion gear;
In the axial direction, the carrier or the rotary shaft is disposed between a portion where the carrier is fixed and the housing, and the rotary shaft and the carrier can rotate around the axis. A thrust bearing that defines the axial position of
The lubricating oil discharged to the outside from the supply oil passage provided on the rotating shaft is blown to the outer peripheral side by centrifugal force through the thrust bearing, and is provided on the side surface of the carrier. In the lubricating structure that is received by the received oil receiver and supplied to the pinion lubricating oil path, and lubricates the pinion gear,
The first race on the carrier side of the thrust bearing is disposed on the inner peripheral side portion of the oil receiver in the axial direction, and the housing supporting the second race on the opposite side includes the second race. A boss part protruding toward the carrier side is provided on the outer peripheral side part than the race,
The lubrication structure for a vehicle power transmission device, wherein an outer diameter of the first race is larger than a diameter of a portion where the boss portion is provided.

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