JPH07223452A - Oil reservoir structure of final reduction gear - Google Patents

Abstract

PURPOSE:To surely lubricate an upper bearing that is not immersed in oil. CONSTITUTION:In an oil reservoir structure for a bearing 3 that is smaller in diameter at one end near the ring gear 5a of an automobile final reduction gear than at the other end, an oil reservoir is formed by a roughly doughnut- shaped ring 6 provided on the ring gear 5a side of the bearing and by the carrier wall 1a of the final reduction gear, and an oil passage 1b is defined on the hanging surface of the roughly doughnut-shaped ring 6 that is not immersed in oil.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil sump structure for a bearing of a final reduction gear for an automobile.

[0002]

2. Description of the Related Art FIG. 4 shows a positional relationship between a final reduction gear of an automobile and other parts. Final speed reducer for automobile 11
Has a structure in which the driving force is transmitted through the engine 13, the transmission 10, and the propeller shaft 12. However, due to the layout of the drive system, when the vehicle body mounting angle of the final reduction gear device 11 becomes large or when the vehicle climbs up an inclined surface, oil accumulates behind the final reduction gear device 11 and lubricates the front bearing of the input shaft. May run short.

Therefore, in Japanese Utility Model Publication No. 63-5937, in order to prevent such insufficient lubrication, the differential carrier near the lower end of the front bearing has a weir projecting upward, and an oil reservoir is formed by the weir and the differential carrier. It was formed so that the lower part of the front bearing was dipped. This prior art is shown in FIG. 5, where there are 1 front bearing, 2 differential carriers and 3 weirs. With such a configuration, the oil in the oil reservoir is blocked by the weir 3 even when the input shaft of the final reduction gear has a predetermined inclination angle with respect to the traveling direction of the vehicle body, for example, when the vehicle body climbs an inclined surface. Therefore, the front bearing 1 continues to be immersed in the oil as it is without spilling from the oil sump, so that there is no shortage of lubrication in that part.

However, in the above technique, the weir 3
However, since it is formed integrally with the differential carrier 2, there is a problem that the weight increases, and there is a problem that a casting mold having a new weir must be manufactured.

Therefore, in Japanese Utility Model Laid-Open No. 56-44926, as a weir for an oil reservoir, it is light in weight and has a good workability to fit in a differential carrier, so that it is a member different from the differential carrier as shown in FIG. The lower part of the front bearing 2 was immersed by using a simple donut-shaped ring 1.

[0006]

However, in the configuration in which the donut-shaped ring is provided close to the front bearing, the oil scattered toward the upper front bearing which is not immersed in the oil hits the donut-shaped ring, and the oil is scattered. There is a risk of insufficient lubrication of the upper front bearing that has not been dipped in.

Particularly, when this front bearing has a diameter larger than the diameter closer to the ring gear, the rotation speed in the direction orthogonal to the diameter of the outermost peripheral portion on the small diameter side with respect to the rotation axis is the outermost peripheral portion on the large diameter side. Since the rotation speed is lower than the rotational speed in the direction orthogonal to the diameter of the rotation axis of the part, the air around the front bearing receives a force in the direction away from the outer periphery of the front bearing more strongly in the vicinity of the large diameter side than in the vicinity of the small diameter side. Therefore, the density of air near the small diameter side is higher than the density of air near the large diameter side, and as a result, the air pressure is high near the small diameter side and low near the large diameter side. As a result, the front bearing exerts an action of sucking air from the small diameter side to the large diameter side, that is, a pump action. Since the action area of the suction force due to this pump action is limited by the donut-shaped ring, it may not sufficiently act on the oil scattered toward the upper front bearing that is not immersed in the oil, and the lubrication of that part may be insufficient. There is.

[0008]

DISCLOSURE OF THE INVENTION The present invention solves the above problems by enlarging the working range of the suction force by the pump action. That is, in the present invention, in the oil sump structure for bearings, the diameter closer to the ring gear side of the automobile final reduction gear is smaller than the diameter of the other end, and the diameter closer to the ring gear side is the other end. An oil reservoir is formed by the substantially doughnut-shaped ring provided on the ring gear side of the bearing smaller than the diameter of the bearing and the differential carrier wall of the final reduction gear, and the oil is formed on the vertical bottom surface of the substantially donut-shaped ring on the oil non-immersed side. The passage is well-defined.

[0009]

[Function] Since the oil that is scattered toward the upper front bearing that is not immersed in oil is not blocked by other members, it reaches the upper front bearing that is not immersed in oil through the oil passage. . At this time, since the action area of the suction force due to the pump action of the front bearing is not limited by other members, the suction force due to the pump action is not scattered in the oil and is scattered to the upper front bearing. The oil sufficiently works, and the oil reaches the large end side of the front bearing, and the lubrication of the portion is surely performed.

[0010]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a partial sectional view showing a final reduction gear for an automobile, which is arranged on a rear wheel drive shaft.

In FIG. 1, 1 is a differential carrier, 2 is a drive pinion, 3 is a front bearing, 4 is a rear bearing, 5 is a differential case, 6 is an oil storage ring, and 7 is a step for preventing the oil storage ring from falling off.

The differential carrier 1 is made of cast metal, and rotatably houses and supports the drive pinion 2 and the differential case 5, respectively.

The drive pinion 2 receives the power from an engine (not shown) and transmits the power to the differential case 5, and comprises a pinion shaft 2a and a pinion gear 2b. The pinion shaft 2a is rotatably supported by the differential carrier 1 via a pair of bearings 3 and 4. Further, the pinion gear 2b meshes with a ring gear 5a fixed to the differential case 5.

The pair of bearings 3 and 4 are rotatably supported on the differential carrier 1, and more specifically, rollers having a plurality of tapered rollers between two races of an inner race and an outer race. This is a bearing, and the suction force generated by the pump action is generated from near the small diameter side to near the large diameter side. Of these bearings, 3 is located in the front of the vehicle and therefore 4 is called a rear bearing because it is located in the rear of the vehicle. 3a is an outer race of a front bearing, 4a is an outer race of a rear bearing, 3b is an inner race of a front bearing, and 4b is an inner race of a rear bearing. The outer races 3a and 4a are both fitted to the differential carrier 1, and the inner races 3b and 4b are both fitted to the drive pinion 2.

The differential case 5 includes a ring gear 5a fixed to the outside of the case, a cross-shaped pinion shaft 5b fitted and supported by the differential case 5, a pinion gear 5c-and a pinion gear 5c-rotatably supported by the pinion shaft 5b, respectively. A pair of side gears 5d that mesh with each other
And 5e are stored. The pair of side gears 5d and 5e are respectively spline-fitted to the left and right drive shafts on the rear wheel side (not shown) so as to drive the drive pinion 2, the ring gear 5a, the differential case 5,
The power transmitted via the pinion shaft 5b and the pinion gear 5c is transmitted to the left and right rear wheels.

The oil storage ring 6 is provided on the rear end ring gear side of the front bearing 3 on the side of the pinion gear 2b and forms an oil reservoir together with the wall surface 1a of the differential carrier 1. The material of the oil storage ring 6 is an iron plate, more specifically, a high tensile cold rolled steel plate. Further, the oil storage ring 6 is manufactured by scissoring and pressing a flat iron plate between a cylindrical upper die and a cup die. At this time, the cylindrical upper mold has a cross-sectional shape when cut in a direction parallel to the flat iron plate, in which a part of a donut-shaped circle is cut out. The oil storage ring 6 is press-fitted into the differential carrier 1 on the ring gear 5a side of the front bearing 3 so that the outer peripheral portion of the oil storage ring 6 abuts the outer race 3a. The oil storage ring drop-out prevention step 7 prevents the oil storage ring 6 press-fitted into the differential carrier 1 from falling off toward the ring gear 5a.

As shown in FIG. 2, the oil storage ring 6 has a semi-circular cutout in the upper portion which is not immersed in oil to define an oil passage to the upper front bearing 3. The oil storage ring 6 is located behind the front bearing 3 and is press-fitted into the wall surface 1 a of the differential carrier 1.

In FIG. 2, the oil storage ring 6
The upper half is open. That is, a donut-shaped circle is partially cut out, and a positioning protrusion 8 is provided above the oil storage ring 6.

Further, as shown in FIG. 3, the differential carrier 1 has positioning protrusions 8 of the oil storage ring 6.
Is provided with a recess 9.

Next, the operation of the above configuration will be described.

Power from an engine (not shown) is transmitted to the ring gear 5a by the drive pinion 2. When the ring gear 5a rotates, the differential case 5 fixed to the ring gear 5a also rotates. The rotation of the ring gear 5a scoops up the oil in the differential carrier 1 and scatters it forward. At this time, the oil also collects in the front part of the differential carrier 1 and the lower front bearing 3 is immersed in the collected oil. . Even if the vehicle body tilts under some driving condition, for example, when climbing an inclined surface, the donut-shaped oil storage ring 6 provided behind the lower front bearing 3 that is immersed in oil functions as a weir, so Does not spill down from the oil reservoir,
The lower front bearing 3, which is immersed in oil, is always immersed in oil and sufficiently lubricated.

On the other hand, the oil scraped up by the ring gear 5a which rotates integrally with the pinion shaft 2a scatters upward and goes through the oil passage 1b to the upper front bearing 3 which is not immersed in the oil. At this time, the oil passes through the cutout portion of the donut-shaped oil storage ring 6, that is, the cutout portion 1c for the oil passage without being blocked by other members, and the oil receives the suction force by the pumping action of the front bearing 3, It reaches the upper front bearing 3 which is not immersed in oil.
As a result, the upper front bearing 3 which is not immersed in oil is also sufficiently lubricated.

As described above, with a simple structure in which a part of a donut-shaped circle is cut out to define the oil passage, the range of action of the suction force by the pump action can be expanded and an excellent lubricating effect can be obtained. .

Further, the present invention is not limited to this embodiment, and at least one or more holes are formed in various embodiments, for example, the upper part of the oil storage ring 6, as long as the gist of the invention is not impaired. Also included are those. In this case, since the conventional donut-shaped oil storage ring is simply provided with holes, the strength of the oil storage ring itself is maintained. Further, as shown in FIG. 7, by providing a step toward the front bearing side at a portion functioning as an oil damming portion below the oil storage ring, the oil can be stored up to a higher position. As shown in 8,
In addition to the configuration shown in FIG. 7, the cutout portion is formed small, and the step difference of the portion functioning as an oil damming portion is further expanded to increase the oil holding capacity.

Further, in the description of the present embodiment, the tapered roller bearing is used as the front bearing, but any element having a pumping action by the suction force may be used, and deep groove type, angular type and self-aligning type radials may be used. Ball bearings, thrust ball bearings, self-aligning roller bearings may be used.

[0027]

According to the present invention, by expanding the working range of the suction force due to the pumping action of the front bearing, the oil which is not immersed in the oil and is scattered toward the upper front bearing is immersed in the oil through the oil passage. Since it reaches the upper front bearing which is not installed, the lubrication of the relevant part is surely performed.

[Brief description of drawings]

FIG. 1 is a diagram showing a configuration of the present invention.

FIG. 2 is a diagram showing an embodiment of the present invention.

FIG. 3 is a diagram showing a shape of an oil storage ring according to an embodiment of the present invention.

FIG. 4 is a diagram showing a positional relationship with other components of the final reduction gear of the automobile.

FIG. 5 is an enlarged view of a conventional front bearing oil reservoir.

FIG. 6 is a view showing a shape of a conventional oil storage ring.

FIG. 7 is a diagram showing a shape of an oil storage ring according to an embodiment of the present invention.

FIG. 8 is a diagram showing a shape of an oil storage ring according to an embodiment of the present invention.

[Explanation of symbols]

1 ... Differential carrier 1a ... Differential carrier wall surface 1b ... Oil passage 1c ... Notch for oil passage 2 ... Drive pinion 2a ... Pinion shaft 2b ... Pinion gear 3 ... Front bearing 3a ・ ・ ・ Outer race 3b ・ ・ ・ Inner race 4 ・ ・ ・ Rear bearing 4a ・ ・ ・ Outer race 4b ・ ・ ・ Inner race 5 ・ ・ ・ Diff case 5a ・ ・ ・ Ring gear 5b ・ ・ ・ Pinion shaft 5c ・..Pinion gear 5d ・ ・ ・ Side gear 5e ・ ・ ・ Side gear 6 ・ ・ ・ Oil storage ring 7 ・ ・ ・ Oil storage ring fall prevention step 8 ・ ・ ・ Oil storage ring positioning protrusion 9 ・ ・ ・ Oil storage ring positioning Concave 10 ・ ・ ・ Transmission 11 ・ ・ ・ End Speed device 12 ・ ・ ・ Propeller shaft 13 ・ ・ ・ Engine

Claims (1)

[Claims] 1. An oil sump structure for a bearing, the diameter of which is closer to the ring gear side of the final reduction gear for an automobile than the diameter of the other end, and a substantially donut-shaped ring and a final ring provided on the ring gear side of the bearing. An oil sump is formed by the carrier wall of the speed reducer, and an oil passage is defined in the vertical lower surface of the substantially donut-shaped ring on the oil non-immersed side. Construction.