JPH09105450A - Lubrication device for bearing of differencial gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent excessive lubrication oil from flowing at high speed traveling and shortcoming of lubrication oil at low speed traveling. SOLUTION: Baffle plates 15, 17 are provided at both ends of taper roller bearings 2, 2 for supporting pinion shaft 3. Each baffle plates 15, 17 prevents excessive lubrication oil flowing at the time of pinion shaft 3 rotating at high speed and prevent lubrication oil in each taper roller bearing from being swept away at low speed rotation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The lubricating device for a differential bearing according to the present invention relates to the lubrication of a bearing incorporated in a differential (differential device or final reduction gear) provided in a drive system of an automobile. In particular, the present invention aims to improve the durability of the bearing portion by maintaining the amount of lubricating oil supplied by such a lubricating device within an appropriate range.

[0002]

2. Description of the Related Art A differential is provided between a propeller shaft of an automobile and a drive shaft (accelerator shaft) of a wheel so that power is transmitted between the propeller shaft and the drive shaft and the course is changed. The difference in rotational speed between the left and right driving wheels is absorbed, and the direction of power is further changed to achieve final deceleration. Such a differential is configured as shown in FIG. 5, for example.

A pinion gear 4 fixed to an end of a pinion shaft 3 rotatably supported by a pair of tapered roller bearings 2 and 2 at one end of the differential case 1 and a rotatably supported inside the differential case 1. Drive shaft (not shown) by meshing with the ring gear 5
The rotational force of is transmitted to the pinion gear 4. Further, the rotational force of the pinion gear 4 is freely transmitted to the left and right drive shafts (not shown) supported by the differential case 1 by another tapered roller bearing via the ring gear 5. In the differential configured as described above, since each part rotates at high speed when the vehicle is running, it is necessary to lubricate the tapered roller bearings 2, 2 supporting the pinion shaft 3.

For this reason, conventionally, the lubricating oil accumulated in the bottom of the differential case 1 is sprung up to the upper part of the differential case 1 by the ring gear 5 which rotates when the vehicle is running, and the spoiled lubricating oil is further tapered. A lubricating device is used that continuously lubricates the tapered roller bearings 2 and 2 by feeding the lubricating oil that has passed through the bearings 2 and 2 and passed through the tapered roller bearings 2 and 2 back to the bottom of the differential case 1. ing. Ring gear 5 with the lower part immersed in the lubricating oil stored in the bottom of the differential case 1.
5 is rotated as indicated by an arrow a in FIG. 5, the lubricating oil is splashed up by the ring gear 5 and, as indicated by an arrow b in the figure, a portion between the two tapered roller bearings 2, 2. And further enters into each tapered roller bearing 2, 2. The lubricating oil that has entered the tapered roller bearings 2 and 2 is moved from the small diameter end (the left end in the case of the right bearing in FIG. 5) of the tapered roller bearings 2 and 2 to the large diameter end (also the right end) by the action of centrifugal force. ) (Pump action when the tapered roller bearing rotates), arrow c in the figure
As shown by, it is discharged from each of the tapered roller bearings 2 and and is returned to the bottom of the differential case 1. Hereinafter, by repeating this operation continuously, each tapered roller bearing 2,
Lubricate 2.

[0005]

However, in the lubricating device for a differential bearing which is constructed and operates as described above, the following disadvantages have conventionally occurred. That is,
When the vehicle travels at high speed, the pinion shaft 3 connected to the drive shaft rotates at high speed, and naturally the ring gear 5 also rotates at high speed. Therefore, the amount of lubricating oil that is sprung up by the ring gear 5 and is sent to the tapered roller bearings 2 and 2 as shown by the arrow b in FIG. 5 also increases.
On the other hand, even if the number of rotations of the pinion shaft 3 and the drive shaft increases,
The amount of lubricating oil required for stable operation of the tapered roller bearings 2 and 2 does not increase so much, and even if the amount of lubricating oil sent to each tapered roller bearing 2 and 2 increases as the ring gear 5 rotates at high speed, or If the amount is larger than that, it is wasted in terms of lubrication performance.

[0006] The fact that more lubricating oil than necessary is supplied to the tapered roller bearings 2 and 2 does not cause any particular problem. However, foreign substances such as abrasion powder of each component constituting the differential and an abrasive (which cannot be completely removed after finishing the surface of each component) are mixed in the lubricating oil. For this reason, the circulation of the lubricating oil more than necessary causes the foreign matter and the tapered roller bearings 2, 2 to that extent.
The chances of contact with the bearings increase, the wear of the tapered roller bearings 2 and 2 is promoted, the preload is reduced, and the gear engagement noise increases,
Not preferred. In addition, the foreign matter damages the raceway surfaces of the tapered roller bearings 2 and 2, and causes an increase in noise (race noise) and vibration generated from the bearings.

Conversely, when the automobile runs at a low speed, the amount of lubricating oil fed to each tapered roller bearing 2, 2 decreases with the rotation of the ring gear 5, and the pumping action causes the tapered roller bearings 2, 2 to rotate. When the amount of lubricating oil discharged is larger than the amount of lubricating oil supplied, the tapered roller bearing 2,
Lubricating oil in 2 becomes insufficient, which causes seizure of the bearing.

The lubricating device for a differential bearing according to the present invention eliminates any of the above inconveniences.

[0009]

In any of the lubricating devices for a differential bearing according to the present invention, as in the case of the conventional lubricating device described above, the lower part of the ring gear rotatably provided in the differential case is provided in the differential case. By soaking it in the lubricating oil stored in the bottom, this lubricating oil is splashed up to the upper part of the differential case, the pinion shaft is sent to the tapered roller bearing supported in this differential case, and the lubricating oil that has passed through the tapered roller bearing is It is configured to flow back to the bottom of the differential case.

Particularly, in the differential bearing lubricating device according to the present invention, in the differential bearing lubricating device according to the first aspect, among the opening portions at both ends of the tapered roller bearing serving as a flow path of lubricating oil. A baffle plate that limits the flow rate of lubricating oil is provided in the large diameter side opening of the inner ring that constitutes the tapered roller bearing, and the leading edge of this baffle plate is part of the bearing ring that constitutes the tapered roller bearing. It is provided in a state of being in close proximity.
Further, in the lubricating device for a differential bearing according to claim 2, a baffle plate for restricting the flow rate of the lubricating oil is provided in at least one of both end openings of the tapered roller bearing which serves as a flow path of the lubricating oil, The peripheral portion of the baffle plate is directly attached to the tapered roller bearing by engaging with the end portion of the bearing ring forming the tapered roller bearing.

[0011]

The lubricating operation of the differential bearing lubricating device of the present invention constructed as described above is the same as that of the conventional lubricating device described above. In particular, in the case of the lubricating device of the present invention, the ring gear rotates at high speed with high-speed running, and even when the amount of lubricating oil sent from this ring gear to each tapered roller bearing increases, due to the baffle plate, It is prevented that more lubricating oil than necessary is fed into each tapered roller bearing. Therefore, more lubricating oil than necessary is not sent to each tapered roller bearing, and it is possible to prevent the abrasion of each bearing from being promoted, and at the same time, to prevent an increase in race noise due to foreign matter.

Further, the baffle plate serves as a resistance to the lubricating oil flowing in the tapered roller bearing, and prevents the lubricating oil sent into the bearing from flowing away in a short time. Because of this,
Even when the amount of lubricating oil fed from the ring gear to each tapered roller bearing decreases as the vehicle runs at low speed, each bearing will not seize due to insufficient lubricating oil.

[0013]

1 to 3 show a first embodiment of the present invention. First, in FIG. 1, the lower part of the ring gear 5 rotatably provided in the differential case 1 is immersed in the lubricating oil stored in the bottom part of the differential case 1. Therefore, when the ring gear 5 rotates with the operation of the automobile, the lubricating oil attached to the ring gear 5 is splashed up to the upper part of the differential case 1.

A bearing holding portion 9 provided inside the differential case 1 is provided with a pair of tapered roller bearings 2 and 2 with a space therebetween. The pinion shaft 3 is rotatably supported by these double tapered roller bearings 2 and 2. The pinion shaft 3 penetrates one end of the differential case 1 in an oil-tight manner via a seal body, and is inserted into the differential case 1. Each of the tapered roller bearings 2 and 2 has an inner ring 1 fixed to the outer peripheral surface of the pinion shaft 3.
0 and an outer ring 11 fixed to the inside of the bearing holding portion 9, a plurality of tapered rollers 12 and 12, respectively, are attached to the cage 13.
It is mounted in the state of being positioned by. A spacer 14 is provided between the end faces of the inner races 10 and 10 of the tapered roller bearings 2 and 2 to position the bearings 2 and 2.

As the vehicle is driven, the pinion shaft 3 is
When the ring gear 5 is rotated by, the lubricating oil stored at the bottom of the differential case 1 is applied to the tapered roller bearings 2 and 2 and the bearings 2 and 2 as indicated by an arrow b in FIG.
It is fed from the open end of the small diameter side. Double tapered roller bearing 2,
Lubricating oil that has passed between the inner ring 10 and the outer ring 11 constituting the bearing 2 on the basis of the pumping action of the bearing, as shown by the arrow c in FIG. 2 and flow back to the bottom of the differential case 1.

Inner ring 1 constituting each tapered roller bearing 2, 2.
The inner peripheral edge of a ring-shaped baffle plate 15 is fixed to the outer peripheral surface of the large-diameter-side end portion of 0 and 10. The outer peripheral edge 15a of the baffle plate 15 is, as shown in FIG.
The oil flow path 18 is formed between the end face 11a and a by a gap of a suitable width. On the other hand, an outer peripheral edge portion of a ring-shaped baffle plate 17 is fixed to the inner peripheral edge portion of the outer ring 11, 11 constituting each tapered roller bearing 2, 2 on the side of the small diameter portion. As shown in FIG. 2, the inner peripheral side edge 17a of the baffle plate 17 is brought close to the end edge portion 10a of the inner ring 10 so that an oil having a proper width is provided between the inner peripheral side edge 17a and the inner peripheral side edge 17a. The flow path 16 is formed.

The lubricating action itself of the lubricating device for a differential bearing of the present invention constructed as described above is substantially the same as that of the conventional lubricating device described above. That is, when the ring gear 5 whose lower portion is immersed in the lubricating oil stored in the bottom of the differential case 1 is rotated as shown by the arrow a in FIG. 1, the lubricating oil is splashed up by the ring gear 5. Then, as indicated by an arrow b in the figure, the taper roller bearings 2 and 2 are fed into the portion between the inner ring 10 and the outer ring 11 which form the tapered roller bearings 2 and 2, and lubricate the respective tapered roller bearings 2 and 2.

The lubricating oil that has entered the tapered roller bearings 2 and 2 is directed from the small diameter end to the large diameter end of the tapered roller bearings 2 and 2 by the pumping action of the centrifugal force that accompanies the rotation of the inner rings 10 and 10. Flowing. Then, as shown by an arrow c in the figure, the fluid is discharged from each tapered roller bearing 2, 2 and returns to the bottom of the differential case 1. Hereinafter, by repeating this operation continuously, each tapered roller bearing 2, 2 is lubricated.

Particularly, in the case of the lubricating device of the present invention, the inner ring 10
The lubricating oil which flows between the outer ring 11 and lubricates the tapered roller bearings 2, 2 always has the edges 15 a, 17 of the baffle plates 15, 17.
a and the edge 10a of the inner race 10 or the end face 11 of the outer race 11
a. For this reason, when the ring gear 5 rotates at a high speed as the vehicle travels at a high speed, and the amount of the lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 increases as shown by an arrow b in FIG. Also,
Unnecessary lubricating oil is prevented from being fed into the tapered roller bearings 2,2. As a result, the wear of the bearings 2 and 2 is prevented from being promoted, and the race noise is prevented from increasing. Also, the preload of the bearing is not reduced and the gear meshing noise is not increased.

The flow passages 18 and 16 formed by the baffles 15 and 17 serve as a resistance against the flow of the lubricating oil in the tapered roller bearings 2 and 2, and thus the inner ring 10 and the outer ring of the bearings 2 and 2, respectively. It prevents that the lubricating oil sent in between 11 and 11 is washed out in a short time. For this reason, even when the amount of lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 and 2 decreases as the vehicle travels at a low speed, each of the bearings 2 and
2 does not cause seizure due to lack of lubricating oil.

Next, FIG. 4 shows a second embodiment of the present invention. In the case of the present embodiment, baffle plates 15, 15 forming a flow path 18 (FIG. 3) between the end surface 11 a of the outer ring 11 and the end surfaces of the inner rings 10, 10 and one end of the pinion shaft 3 are fixed. It is held between the pinion gear 4 and an end face of a companion flange 19 fixed to the other end of the pinion shaft 3. In addition, a baffle plate 17 that forms a flow path 16 (FIG. 2) between the inner ring 10 and the edge portions 10a, 10a (FIG. 2) of the inner rings 10, 10.
17 is sandwiched between the end faces of the outer races 11 and the bearing holding portions 9 provided in the differential case 1. Other configurations and operations are the same as those of the first embodiment described above, and therefore, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

In the above description, the flow paths 18 and 1 are
The baffles 15 and 17 for forming 6 are provided on both the inlet side and the outlet side of the portion between the inner ring 10 and the outer ring 11 which are the flow paths of the lubricating oil. It suffices if it is provided on at least one of the entrance side and the exit side. Further, such baffle plates 15 and 17 do not necessarily need to be provided on all tapered roller bearings provided in the differential, and may be provided on required tapered roller bearings according to the supply state of lubricating oil accompanying rotation of the ring gear 5. It may be provided.

[0023]

Since the lubricating device for a differential bearing of the present invention is constructed and operates as described above, the following effects can be obtained. When a car is traveling at high speeds, supplying more oil than necessary to the tapered roller bearings to promote wear of the tapered roller bearings, reduce preload on the bearings, increase gear meshing noise, or produce race noise. Inconvenience such as increase can be prevented. Conversely, seizure of the bearing due to lack of lubricating oil existing in the tapered roller bearing during low-speed running can be reliably prevented, and the durability of the differential can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of essential parts showing a first embodiment of a lubricating device of the present invention.

FIG. 2 is an enlarged view of part A in FIG.

[FIG. 3] Similarly, an enlarged view of a portion B.

FIG. 4 is a view showing a second embodiment of the present invention and corresponding to FIG. 1;

FIG. 5 is a sectional view of a main part of a conventional differential.

[Explanation of symbols]

 1 Differential Case 2 Tapered Roller Bearing 3 Pinion Shaft 4 Pinion Gear 5 Ring Gear 9 Bearing Holding Part 10 Inner Ring 10a End Edge 11 Outer Ring 11a End Face 12 Tapered Roller 13 Retainer 14 Spacer 15 Baffle Plate 15a Outer Edge 16 Flow Channel 17 Obstacle Plate 17a Inner peripheral side edge 18 Flow path 19 Companion flange

[Procedure amendment]

[Submission date] August 9, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

Lubricating device for differential bearing

[Claims]

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The lubricating device for a differential bearing according to the present invention relates to the lubrication of a bearing incorporated in a differential (differential device or final reduction gear) provided in a drive system of an automobile. In particular, the present invention aims to improve the durability of the bearing portion by maintaining the amount of lubricating oil supplied by such a lubricating device within an appropriate range.

[0002]

2. Description of the Related Art A differential is provided between a propeller shaft of an automobile and a drive shaft (accelerator shaft) of a wheel. This differential transmits power between the propeller shaft and the drive shaft, absorbs the rotational speed difference between the left and right drive wheels due to the course change, and further changes the direction of power for final deceleration. I am going to do it. Such a differential is configured as shown in FIG. 5, for example.

A pinion shaft 3 is rotatably supported at one end of a differential case 1 by a pair of tapered roller bearings 2 and 2. Then, the pinion gear 4 fixed to the end of the pinion shaft 3 and the differential case 1
By engaging with a ring gear 5 rotatably supported inside, the rotational force of a drive shaft (not shown) can be transmitted to the pinion gear 4. Further, the rotational force of the pinion gear 4 is freely transmitted to the left and right drive shafts (not shown) supported by the differential case 1 by another tapered roller bearing via the ring gear 5. In the differential configured as described above, since each part rotates at high speed when the automobile is running, it is necessary to lubricate the tapered roller bearings 2 and 2 supporting the pinion shaft 3.

For this reason, conventionally, a lubricating device has been used in which the lubricating oil stored in the bottom of the differential case 1 is splashed up to the upper part of the differential case 1 by a ring gear 5 that rotates when the vehicle is running. In this lubricating device, the lubricating oil splashed up by the ring gear 5 is sent to the tapered roller bearings 2 and 2, and the lubricating oil that has passed through the tapered roller bearings 2 and 2 is returned to the bottom of the differential case 1 so that each conical roller bearing 2 is returned. The roller bearings 2 and 2 are continuously lubricated. That is, when the ring gear 5 whose lower part is immersed in the lubricating oil stored in the bottom of the differential case 1 is rotated as shown by the arrow a in FIG. 5, the lubricating oil is splashed up by the ring gear 5. Then, as indicated by an arrow b in the figure, it is fed into the space between the two tapered roller bearings 2 and 2, and further enters into each tapered roller bearing 2 and 2. The lubricating oil that has entered the tapered roller bearings 2 and 2 is moved from the small diameter end (the left end in the case of the right bearing in FIG. 5) of the tapered roller bearings 2 and 2 to the large diameter end (also the right end) by the action of centrifugal force. ) Flow (pump action when the tapered roller bearing rotates). Then, as shown by an arrow c in the figure, the fluid is discharged from each tapered roller bearing 2, 2 and returns to the bottom of the differential case 1.
Hereinafter, by repeating this operation continuously, each tapered roller bearing 2, 2 is lubricated.

[0005]

However, in the lubricating device for a differential bearing which is constructed and operates as described above, the following disadvantages have conventionally occurred. That is,
When the vehicle travels at high speed, the pinion shaft 3 connected to the drive shaft rotates at high speed, and naturally the ring gear 5 also rotates at high speed. Therefore, the amount of lubricating oil that is sprung up by the ring gear 5 and is sent to the tapered roller bearings 2 and 2 as shown by the arrow b in FIG. 5 also increases.
On the other hand, even if the rotation speeds of the pinion shaft 3 and the drive shaft become faster, the amount of lubricating oil required for stable operation of the tapered roller bearings 2 and 2 does not increase so much, and each tapered roller bearing is rotated with the high speed rotation of the ring gear 5. Even if the amount of lubricating oil fed to the bearings 2 and 2 increases, a certain amount or more is wasted in terms of lubricating performance.

[0006] The fact that more lubricating oil than necessary is supplied to the tapered roller bearings 2 and 2 does not cause any particular problem. However, foreign substances such as abrasion powder of each component constituting the differential and an abrasive (which cannot be completely removed after finishing the surface of each component) are mixed in the lubricating oil. Therefore, the circulation of the lubricating oil more than necessary is as much as the foreign matter and the tapered roller bearings 2, 2
This increases the chances of contact with the tapered roller bearing 2,
2 is accelerated, preload is reduced, and gear meshing noise is increased, which is not preferable. In addition, the foreign matter damages the raceway surfaces of the tapered roller bearings 2 and 2, and causes an increase in noise (race noise) and vibration generated from the bearings.

Conversely, when the automobile runs at a low speed, the amount of lubricating oil fed to each tapered roller bearing 2, 2 decreases with the rotation of the ring gear 5, and the pumping action causes the tapered roller bearings 2, 2 to rotate. When the amount of lubricating oil discharged is larger than the amount of lubricating oil supplied, the tapered roller bearing 2,
Lubricating oil in 2 becomes insufficient, which causes seizure of the bearing. The lubricating device for a differential bearing of the present invention eliminates any of the above-mentioned inconveniences.

[0008]

In any of the lubricating devices for a differential bearing according to the present invention, as in the case of the conventional lubricating device described above, the lower part of the ring gear rotatably provided in the differential case is provided in the differential case. By soaking it in the lubricating oil stored in the bottom, this lubricating oil is splashed up to the upper part of the differential case, the pinion shaft is sent to the tapered roller bearing supported in this differential case, and the lubricating oil that has passed through the tapered roller bearing is It is configured to flow back to the bottom of the differential case.

Particularly, in the lubricating device for a differential bearing according to the present invention, in the lubricating device for a differential bearing according to claim 1, among the opening portions at both ends of the tapered roller bearing which serve as a flow path of lubricating oil. A baffle plate that limits the flow rate of lubricating oil is provided in the large diameter side opening of the inner ring that constitutes the tapered roller bearing, and the leading edge of this baffle plate is part of the bearing ring that constitutes the tapered roller bearing. It is provided in a state of being in close proximity.

Further, in the lubricating device for a differential bearing according to a second aspect of the present invention, at least one of the opening portions at both ends of the tapered roller bearing, which serves as a passage for the lubricating oil, is an obstacle for limiting the flow amount of the lubricating oil. The plate is directly attached to the tapered roller bearing by engaging the peripheral portion of the baffle plate with the end portion of the bearing ring which constitutes the tapered roller bearing.

[0011]

The lubricating operation of the differential bearing lubricating device of the present invention constructed as described above is the same as that of the conventional lubricating device described above. In particular, in the case of the lubricating device of the present invention, the ring gear rotates at high speed with high-speed running, and even when the amount of lubricating oil sent from this ring gear to each tapered roller bearing increases, due to the baffle plate, It is prevented that more lubricating oil than necessary is fed into each tapered roller bearing. Therefore, more lubricating oil than necessary is not sent to each tapered roller bearing, and it is possible to prevent the abrasion of each bearing from being promoted, and at the same time, to prevent an increase in race noise due to foreign matter.

Further, the baffle plate serves as a resistance to the lubricating oil flowing in the tapered roller bearing, and prevents the lubricating oil sent into the bearing from flowing away in a short time. Because of this,
Even when the amount of lubricating oil fed from the ring gear to each tapered roller bearing decreases as the vehicle runs at low speed, each bearing will not seize due to insufficient lubricating oil.

Further, in the case of the lubricating device for a differential bearing according to the first aspect of the invention, since the leading edge of the baffle plate is brought close to a part of the bearing ring forming the tapered roller bearing, the lubricating oil is used. The area and properties of the labyrinth flow path for restricting the flow of can be set as desired. That is, the surface of the bearing ring is, for example, compared to the inner surface of the differential case,
Since the surface shape and dimensions are accurately regulated, the flow rate of the lubricating oil flowing inside the tapered roller bearing can be regulated as desired by adjusting the area and properties of the labyrinth passage.

Further, in the case of the lubricating device for a differential bearing according to a second aspect of the invention, the peripheral portion of the baffle plate is engaged with the end portion of the bearing ring which constitutes the tapered roller bearing, whereby the tapered roller is formed. Since it is mounted directly on the bearing, the work of incorporating the baffle plate and the tapered roller bearing into the differential becomes easy.

[0015]

1 to 3 show a first embodiment of the present invention in which the invention described in claim 1 and the invention described in claim 2 are combined. First, in FIG. 1, the lower part of the ring gear 5 rotatably provided in the differential case 1 is immersed in the lubricating oil stored in the bottom part of the differential case 1. Therefore, the ring gear 5
When the is rotated, the lubricating oil attached to the ring gear 5
It is flipped up to the top of the differential case 1.

A pair of tapered roller bearings 2 and 2 are provided in the bearing holders 9 and 9 provided inside the differential case 1. The pinion shaft 3 is rotatably supported by these double tapered roller bearings 2 and 2. The pinion shaft 3 penetrates one end of the differential case 1 in an oil-tight manner through a seal body, and is inserted into the differential case 1. Each of the tapered roller bearings 2, 2 has a plurality of tapered rollers 12, 12 between an inner ring 10 fixed on the outer peripheral surface of the pinion shaft 3 and an outer ring 11 fixed on the inner side of the bearing holder 9. It is mounted in a state of being positioned by the retainer 13. Also, the above-mentioned both tapered roller bearings 2, 2
A spacer 14 is provided between the end faces of the inner rings 10, 10 of
Both bearings 2 and 2 are positioned.

As the vehicle is driven, the pinion shaft 3 is used.
When the ring gear 5 is rotationally driven by, the lubricating oil stored in the bottom portion of the differential case 1 is transferred to the tapered roller bearings 2 and 2 and the bearings 2 and 2 as shown by an arrow b in FIG.
It is fed from the small diameter side opening end of 2. Lubricating oil that has passed between the inner ring 10 and the outer ring 11 forming the two tapered roller bearings 2 and 2 based on the pumping action of the bearings, as shown by an arrow c in FIG. It flows out from the radial side open ends to the outside of the bearings 2, 2. Then, it returns to the bottom of the differential case 1.

Inner ring 1 constituting each tapered roller bearing 2, 2.
The inner peripheral edge of a ring-shaped baffle plate 15 is fixed to the outer peripheral surface of the large-diameter-side end portion of 0 and 10. As shown in FIG. 3, the outer peripheral edge 15a, which is the leading edge of the baffle plate 15, is brought close to the end surface 11a of the outer ring 11, which is a part of the bearing ring, and is appropriately provided between the end surface 11a and the end surface 11a. The oil passage 18 is formed by the labyrinth gap having a wide width. On the other hand, the outer peripheral edge of a ring-shaped baffle plate 17 is fixed to the inner peripheral edge of the outer ring 11, 11 constituting each of the tapered roller bearings 2, 2 at the small diameter side end. Inner peripheral side edge 1 which is the tip edge of this baffle plate 17
7a is also a part of the bearing ring, as shown in FIG.
An oil passage 16 is formed near the end edge portion 10a of the inner ring 10 by a labyrinth gap having an appropriate width with the inner peripheral edge 17a.

The lubricating operation itself of the lubricating device for a differential bearing of the present invention configured as described above is substantially the same as that of the conventional lubricating device described above. That is, when the ring gear 5 whose lower portion is immersed in the lubricating oil stored in the bottom of the differential case 1 is rotated as shown by the arrow a in FIG. 1, the lubricating oil is splashed up by the ring gear 5. Then, as indicated by an arrow b in the figure, the taper roller bearings 2 and 2 are fed into the portion between the inner ring 10 and the outer ring 11 which form the tapered roller bearings 2 and 2, and lubricate the respective tapered roller bearings 2 and 2.

The lubricating oil that has entered the tapered roller bearings 2 and 2 is directed from the small diameter end of the tapered roller bearings 2 and 2 to the large diameter end by the pumping action of the centrifugal force that accompanies the rotation of the inner rings 10 and 10. Flowing. Then, as shown by an arrow c in the figure, the fluid is discharged from each tapered roller bearing 2, 2 and returns to the bottom of the differential case 1. Hereinafter, by repeating this operation continuously, each tapered roller bearing 2, 2 is lubricated.

In particular, in the case of the lubricating device of the present invention, the inner ring 10
The lubricating oil which flows between the outer ring 11 and lubricates the tapered roller bearings 2, 2 always has the edges 15 a, 17 of the baffle plates 15, 17.
a and the edge 10a of the inner race 10 or the end face 11 of the outer race 11
a. For this reason, when the ring gear 5 rotates at a high speed as the vehicle travels at a high speed, and the amount of the lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 increases as shown by an arrow b in FIG. Also,
Unnecessary lubricating oil is prevented from being fed into the tapered roller bearings 2,2. As a result, the wear of the bearings 2 and 2 is prevented from being promoted, and the race noise is prevented from increasing. Also, the preload of the bearing is not reduced and the gear meshing noise is not increased.

The flow passages 18 and 16 formed by the baffles 15 and 17 serve as a resistance against the flow of lubricating oil in the tapered roller bearings 2 and 2, and thus the inner ring 10 and the outer ring of the bearings 2 and 2 are prevented. It prevents that the lubricating oil sent in between 11 and 11 is washed out in a short time. For this reason, even when the amount of lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 and 2 decreases as the vehicle travels at a low speed, each of the bearings 2 and
2 does not cause seizure due to lack of lubricating oil.

In the illustrated embodiment, each baffle plate 1 is
The outer peripheral side end edge 15a and the inner peripheral side end edge 17a, which are the front end edges of 5, 5 and 17, are the end surfaces 11a of the outer ring 11 or the inner ring 10 which are a part of the races forming the tapered roller bearings 2, 2. Since it is close to the edge portion 10a of the above, the areas and properties of the flow paths 18, 16 which are labyrinth flow paths for restricting the flow of the lubricating oil can be made as desired. That is, the surface shapes and dimensions of the surfaces of the outer ring 11 and the inner ring 10 are regulated more accurately than the inner surface of the differential case 1, for example. Therefore, the flow paths 18 and 16 that are labyrinth flow paths.
It is possible to regulate the flow rate of the lubricating oil flowing inside the tapered roller bearings 2 and 2 as desired by controlling the area and properties of the above. Further, the baffles 15 and 17 are directly attached to the tapered roller bearings 2 and 2 in which the inner ring 10 and the outer ring 11 are incorporated by engaging the peripheral portions of the baffles 15 and 17 with the ends of the inner ring 10 or the outer ring 11. Because these are installed, these baffles 1
The work of assembling the 5, 17 and the tapered roller bearings 2, 2 between the differential case 1 and the pinion shaft 3 forming the differential becomes easy. Of course, parts management can be simplified.

Next, FIG. 4 corresponds to claim 1 only,
7 shows a second embodiment of the present invention. In the case of the present embodiment, baffle plates 15 and 15 forming a flow path 18 (FIG. 3) between the outer race 11 and the end face 11a are fixed to the end faces of the inner races 10 and 10 and one end of the pinion shaft 3. Companion flange 19 fixed to the other end of the pinion gear 4 or the pinion shaft 3.
It is sandwiched between the end faces of the. Further, the flow path 16 (FIG. 2) is provided between the inner ring 10, 10 and the edge portions 10a, 10a (FIG. 2).
The baffle plates 17 and 17 that form the bearings 9 are provided on the end faces of the outer rings 11 and 11 and the bearing holding portion 9 provided in the differential case 1.
It is sandwiched between 9 and. The construction and operation are the same as those of the first embodiment except that the baffles 15 and 17 are not directly attached to the inner ring 10 or the outer ring 11, and therefore, the same parts are designated by the same reference numerals. Then, the overlapping description is omitted.

In the above description, the flow paths 18, 1
The baffles 15 and 17 for forming 6 are provided on both the inlet side and the outlet side of the portion between the inner ring 10 and the outer ring 11 which are the flow paths of the lubricating oil. It suffices if it is provided on at least one of the entrance side and the exit side. Further, such baffle plates 15 and 17 do not necessarily need to be provided on all tapered roller bearings provided in the differential, and may be provided on required tapered roller bearings according to the supply state of lubricating oil accompanying rotation of the ring gear 5. It may be provided.

[0025]

Since the lubricating device for a differential bearing of the present invention is constructed and operates as described above, the following effects (1) to (4) can be obtained. When a car is traveling at high speeds, supplying more oil than necessary to the tapered roller bearings to promote wear of the tapered roller bearings, reduce preload on the bearings, increase gear meshing noise, or produce race noise. Inconvenience such as increase can be prevented. Conversely, seizure of the bearing due to lack of lubricating oil existing in the tapered roller bearing during low-speed running can be reliably prevented, and the durability of the differential can be improved. If the tip edge of the baffle plate is brought close to a part of the bearing ring forming the tapered roller bearing, the area and properties of the labyrinth passage for restricting the flow of the lubricating oil can be made as desired, and the tapered roller bearing It is possible to regulate the flow rate of the lubricating oil that flows inside the engine as desired. By engaging the peripheral edge of the baffle plate with the end of the bearing ring that constitutes the tapered roller bearing, the baffle plate and the tapered roller bearing are directly attached to the tapered roller bearing. Become.

[Brief description of the drawings]

FIG. 1 is a sectional view of essential parts showing a first embodiment of a lubricating device of the present invention.

FIG. 2 is an enlarged view of part A in FIG.

[FIG. 3] Similarly, an enlarged view of a portion B.

FIG. 4 is a view similar to FIG. 1, showing a second embodiment of the present invention.

FIG. 5 is a sectional view of a main part of a conventional differential.

[Description of reference numerals] 1 differential case 2 tapered roller bearing 3 pinion shaft 4 pinion gear 5 ring gear 9 bearing holding portion 10 inner ring 10a end edge portion 11 outer ring 11a end surface 12 tapered roller 13 retainer 14 spacer 15 baffle outer edge 15a 16 flow path 17 baffle plate 17a inner peripheral side edge 18 flow path 19 companion flange

Claims (2)

[Claims] 1. A pinion shaft is constructed by immersing a lower portion of a ring gear rotatably provided in a differential case in lubricating oil stored in a bottom portion of the differential case, so that the lubricating oil is splashed up to an upper portion of the differential case. In a tapered roller bearing that supports this differential case, and the lubricating oil that has passed through the tapered roller bearing is returned to the bottom of the differential case. A baffle plate that limits the flow amount of the lubricating oil is provided in the opening on the large diameter side of the inner ring that constitutes the tapered roller bearing among the opening portions on both ends, and the leading edge of this baffle plate is the raceway that constitutes the tapered roller bearing. A lubricating device for a differential bearing, characterized in that it is provided in the state of being close to a part of the ring. 2. A pinion shaft is provided by immersing a lower portion of a ring gear rotatably provided in a differential case into lubricating oil stored in a bottom portion of the differential case, so that the lubricating oil is splashed up to an upper portion of the differential case. In a tapered roller bearing that supports this differential case, and the lubricating oil that has passed through the tapered roller bearing is returned to the bottom of the differential case. A baffle plate that restricts the flow rate of the lubricating oil is provided in at least one of the opening portions at both ends, and the peripheral edge portion of the baffle plate is engaged with the end portion of the raceway ring that constitutes the tapered roller bearing. Lubrication device for differential bearings, characterized by being mounted directly on the