JPS592978Y2 - Lubricating device for vehicle reduction gear differentials - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a reduction differential for vehicles, and in particular to a lubricating device for a two-stage reduction type reduction differential in which the rotation of a ring gear transmitted by a pinion gear is reduced by a planetary gear and transmitted to a differential. Regarding.

Hereinafter, the structure and operation of the speed reduction differential device of the above type will be explained based on FIG. 1.

In the figure, a pinion drive gear 2 that is connected to an output shaft of a transmission (not shown) via a propulsion shaft and rotates by transmitting engine driving force has tapered bearings 2a and 2b.
The carrier cover 1b is pivotally supported by a sleeve 1b, and the sleeve is attached to the front end of the carrier cover 1a by a pole Hd.

The pinion drive gear 2 meshes with external teeth 3a of a ring gear 3 which is supported on the rear side wall of the carrier cover 1a via side bearings 11.12, and the rotation of the pinion drive gear 2 reduces the speed of the ring gear 3. Rotate.

The bearing cylinder part 3La of the left support case 3L, which is integrally fixed to the ring gear by bolts 31, is spline-coupled with an adjustment nut IIA for adjusting the preload of the side bearing 11, and is substantially fixed to the carrier cover 1a. The sun gear 4 assembled in this state is attached so as to float through the bearing cylinder 3La, and the planetary gear 5 that meshes with the teeth 4a of the sun gear 4 and the inner gear 3C of the ring gear 3 is attached to the side surface of the differential case 61. A plurality of planetary gears 5 are attached to a fixed shaft 7 via bearings 7a, and as the ring gear 3 rotates, the planetary gear 5 rotates around the shaft 7 and rotates around the sun gear 4 at a rotation speed that is lower than the rotation speed of the ring gear 3. revolve.

The differential cases 6l and 6r are integrally fixed by a pole 6a.

Inside the tough case 61.6r, which rotates as the planetary gear 5 revolves, a pair of side gears 81.8r are coaxially supported with the sun gear 4, and a cross-shaped spider shirt 10 has a shaft at a right angle thereto. Each inner side of the axle shirt 1 (not shown) meshes with the supported four pinion gears 9a, 9b (two in the figure) and is connected to the pair of side gears 81.8r to the left wheel and the right wheel, respectively. The ends are fitted and splined.

When the vehicle is running straight, the pinion gears 9a, 9
b does not rotate around the spider shaft 10, therefore, the pair of side gears 81 and 8r do not rotate around the spider shaft 10.
When the vehicle is turning, the pinion gears 9a and 9b rotate around the spider shirts 1-10, and the pair of side gears 81.
It is well known that a difference in rotational speed of 8 r is allowed.

Further, a cylindrical right support case 3R, which covers the differential cases 6l and 6r and is fixed to the right side of the ring gear 3 by a pole l-3r, is attached to one side wall at the rear of the carrier cover la via a side bearing 12. It is bearing.

Like the side bearing 11, the side bearing 12 is attached to the carrier cover 1a with a preload defined by the azimuth 1 to the nut 12A.

The carrier cover 1a and housing 1C are used to lubricate the sliding parts and meshing parts of bearings, gears, etc. of such a reduction differential.
The ring gear, pinion drive gear, support case, etc. are immersed in the oil stored at the bottom of the space A surrounded by We are trying to supply it.

Conventionally, an oil supply path to the lubricating main parts of the differential device and planetary gear 5 in a chamber surrounded by the non-gear 3 and the support cases 3L and 3R (hereinafter referred to as the gear chamber 13) is configured as follows.

The oil adhering to the peripheral wall of the support case 3R and being scraped up is transferred to the support case 3 via an oil catcher, etc.
The oil is conveyed to the cavity 14 of the gear nozzle cover 1a formed on the side of the front end of the gear nozzle R, and communicated with the cavity 14 to the inside of the support case 3R through an oil introduction hole 3Ra formed on the right side wall of the support case 3R. supplied to

A part of the oil supplied into the support case 3R flows into the differential case 61.6r from the oil introduction hole 6r1 formed in the differential case 6r, and flows into the side gear 81.8.
After lubricating the teeth of the pinion gears 9 a and 9 b, the annular space 1 in which the planetary gear 5 is disposed flows from the oil outflow hole 612 formed in the partition wall 611 of the differential case 61.
5, and a portion reaches the annular space 15 through the gap between the outer wall of the differential case 61.6r and the support case 3R.

The oil conveyed into the space 15 is transferred to the bearing portion 7a between the planetary gear 5 and the shaft 7, and to the planetary gear 5.
After lubricating the teeth that mesh with sun gear 4,
It flows into the gap 16 between the outer circumferential wall and the inner circumferential wall of the ring gear 3, and some of it flows through the bearing 11 of the left support case 3L, and some of it flows into the sun gear 4 and the adjustment nut 11.
The oil is returned to the oil reservoir at the bottom of space A through the gap between the splines that fit with space A.

However, in such an oil path, the introduction of oil into the support case 3R is sufficiently allowed through the oil introduction hole 3Ra, whereas the oil outflow through the narrow gap between the bearing 11 and the spline fitting part is only a leak. Because the oil is not sufficiently maintained in the gear chamber 13 for a long time and is not circulated properly, the temperature rises significantly due to stirring of each rotating member in the narrow space inside the gear chamber 13, reducing the lubrication performance. Ta.

Also, most of the oil in the tough case 61.6r flows directly into the annular space 15 through the oil outflow hole 612.
The sliding surface of the washer 17 fitted between the tooth-forming side end wall of the sun gear 4 and the partition wall 611 of the differential case 61, the side gear 81, and the differential case 61.
This has the disadvantage that oil is difficult to be supplied to important parts for lubrication, such as the sliding contact surface of the bearing, making it difficult to provide good lubrication.

The present invention was devised in view of these conventional drawbacks, and attempts to eliminate the above drawbacks by forming an oil path through which oil flows out through the gap between the inner circumferential surface of the sun gear and the outer circumferential surface of the axle shaft. The present invention provides a lubrication device for a reduction gear differential.

The present invention will be described in detail below based on embodiments shown in the drawings.

However, in the configuration shown in FIG. 2 and subsequent figures showing an embodiment of the present invention, the same components as those shown in FIG. 1 will be described with the same reference numerals.

In FIG. 2, a communication hole 4b that communicates the inner and outer circumferential surfaces of the sun gear 4 is formed in a stepped portion that connects the small diameter portion of the sun gear 4 and the large diameter portion where the teeth are formed.

The communication hole 4b communicates with a gap 16 between the outer peripheral surface of the sun gear 4 and the inner peripheral surface of the ring gear 3.

In this configuration, the oil introduced into the gear chamber 13 reaches the annular space 15 in which the planetary gear 5 is disposed through the same path as in the conventional example, and flows into the gap 16.

A part of the oil that has flowed into the gap 16 passes through the gap between the bearing 11 and the spline as described above and is fanned out to the oil pool at the bottom of the space A, but a part of the oil flows through the communication hole 4b.
It flows out to the inner peripheral surface of the large diameter part of the sun gear 4, filling the gap 19 between the inner peripheral surface and the axle shaft 18, and the sliding contact surface of the washer 17 and the sliding contact surface of the bearing part between the side gear 81 and the differential case 61. The opening end surface of the sun gear 4 and the adjustment nut I
The oil flows down the outer end surface of IA and returns to the oil reservoir at the bottom of space A.

In this way, the gap 19 between the inner peripheral surface of the small diameter portion of the sun gear 4 and the axle shaft 18 is sufficiently larger than the gap inside the bearing 11 and the gap between the sun gear 4 and the adjustment nut 11A, so the amount of oil flowing out increases. gear room 1
The oil circulation within the gear chamber 13 becomes smoother, suppressing the rise in oil temperature within the gear chamber 13, and improving the lubrication performance throughout the main lubrication parts, which were previously difficult to supply oil to. Oil is smoothly supplied to important parts for lubrication, such as the sliding surface of the washer 17 and the sliding surface P of the side gear 81 and the tough case 61, thereby achieving good lubrication.

FIG. 3 shows another embodiment of the present invention, in which the sun gear 4
A communication hole 4C that communicates with the outer peripheral surface is formed in the small diameter portion of the sun gear 4.

Of course, even with such a configuration, the same function as that of the above embodiment can be obtained, and the point is that the communication hole communicates with the gap between the inner circumferential surface of the ring gear and the outer circumferential surface of the sun gear to communicate the inner and outer circumferential surfaces of the sun gear. All you have to do is set it up.

As explained above, according to the present invention, the oil is introduced into the gear chamber surrounded by the ring gear and the support case, passes through the main lubrication parts in the gear chamber, and reaches the gap between the inner circumferential surface of the ring gear and the outer circumferential surface of the sun gear. Flows into the gap between the sun gear inner circumferential surface and the axle shaft outer circumferential surface through a communication hole provided to communicate the inner and outer circumferential surfaces of the sun gear, and flows smoothly to the outside of the gear room through the gap. Good oil circulation is achieved, suppressing oil temperature rise and improving lubrication performance.

In addition, it is possible to smoothly supply oil to important lubricating parts such as the sliding contact surface of the washer interposed between the sun gear and the differential case and the sliding contact surface between the differential case and the side gear, which were places where oil was difficult to supply in the past. It has excellent features such as being able to provide good lubrication.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view showing the internal structure of a conventional two-stage reduction type reduction differential, and FIG. 2 is a cross-sectional view showing an embodiment of the two-stage reduction type reduction differential according to the present invention. FIG. 3 is a sectional view showing the structure of a sun gear according to another embodiment of the present invention. 1a...Carrier cover, 1C...Housing, A...Space, 2...Pinion drive gear, 3...Ring gear, 4.・・・
...Sun gear, 4 b, 4 C... Communication hole, 5... Planetary gear, 61.6 r...
... differential case, 7 ... shirt), 3L, 3
R...Support case, 13...Gear chamber, 16...Gap, 18...Axle shaft, 19...Gap.

Claims (2)

[Scope of utility model registration request] (1) A pinion drive gear that rotates when engine driving force is transmitted, a ring gear that rotates while meshing with the pinion drive gear, a cylindrical sun gear that is fixed concentrically with the ring gear, and an internal tooth of the ring gear. a planetary gear that meshes with the sun gear and revolves around its axis; a differential case that supports the planetary gear and rotates as the planetary gear revolves; a support case that covers the outside of the differential case and is fixed to the ring gear; and each of the rotating components. In a vehicular deceleration differential device, which comprises a carrier cover that rotatably encloses an axle, and a housing that pivotally supports an axle, and in which oil is stored at the bottom of a space surrounded by the carrier cover and the housing. , a communication hole communicating between the inner circumferential surface and the outer circumferential surface of the sun gear is bored in communication with the gap between the inner circumferential surface of the ring gear and the outer circumferential surface of the sun gear, and a part of the oil in the gap is transferred to the communication hole. and a lubricating device for a reduction gear differential for a vehicle, characterized in that the oil is returned to a reservoir at the bottom of the space through a gap between the inner circumferential surface of the sun gear and the outer circumferential surface of an axle shaft passing through the sun gear. . (2) The sun gear has a large diameter part with teeth and a small diameter part that is supported by the housing, and the communication hole is bored in the stepped part connecting the large diameter part and the small diameter part or in the small diameter part. A lubricating device for a vehicle speed reduction differential according to claim 1 of the registered utility model.