JPH11294468A - Double row rolling bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate elements making the working of an outer ring troublesome by forming a cutout part on the end edge of the opposite side to the end edge in the axial direction of the other outer ring element within both end edges in the axial direction of one outer ring element, and providing a means for fixing the other outer ring element to a housing. SOLUTION: An outer ring 21 constituting a double row rolling bearing device 20 is constituted by combining together a pair of outer ring elements 22a, 22b. Within the outer ring elements 22a, 22b, the end edge on the opposite side to the one of the other outer ring element 22b end edge in the axial direction of both end edges in the axial direction of the one outer ring element 22a is formed with a cutout part 23 in the diametral direction so as to extend from the inner circumferential face of the outer ring 21 to the outer circumferential face. Because the cutout part 23 is formed simultaneously with the other part by forging to make an intermediate raw material, new process is unnecessary. The other outer ring element 22b is respectively integratedly formed with a fitting flange 24 as a fixing means on the outer circumferential face and a circumferential part 25 on the outer end part. Hereby, a bearing device of low price and high reliability can be provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The double-row rolling bearing device according to the present invention is used for rotatably supporting a pinion shaft constituting a differential gear provided in a drive system of an automobile in a casing.

[0002]

2. Description of the Related Art A differential gear is provided between a propeller shaft of an automobile and a driving shaft (accelerator shaft) of wheels to transmit power between the propeller shaft and the driving shaft and to change a course. The rotation speed difference between the left and right driving wheels is absorbed, and the direction of the power is further changed to perform final deceleration. In such a differential gear, a double-row rolling bearing device is incorporated to rotatably support a pinion shaft with respect to a housing. Conventionally, as a double row rolling bearing device used for such a portion, for example, Japanese Patent Application Laid-Open No. 9-152008,
JP-A-1505, JP-A-5-96551, JP-A-7-2
No. 666, European Patent Publication EP 0 409 564A2 and the like are known. FIG. 13 shows a double-row rolling bearing device 1 which has been conventionally incorporated in a differential gear for a large vehicle and actually used, and FIG.
Differential gears incorporating the double row rolling bearing device 1 are shown. First, these FIGS.
The conventional structure shown in FIG.

In the double row rolling bearing device 1, a pair of tapered roller bearings 3a and 3b are provided inside an intermediate housing 2, and the pair of tapered roller bearings 3a and 3b is used to mount a pair of tapered roller bearings 3a and 3b inside a housing 4 constituting a differential gear. The pinion shaft 5 (FIG. 14) is rotatably supported. Each of the tapered roller bearings 3a, 3b has an outer ring 7a, 7b having an outer ring raceway 6a, 6b on an inner peripheral surface, and an inner ring 9a, 9b having inner ring raceways 8a, 8b on an outer peripheral surface, respectively.
A plurality of rolling elements are provided between the outer raceways 6a, 6b and the inner raceways 8a, 8b. The above 1
Between the pair of inner rings 9a and 9b, a cylindrical inner ring spacer 1 is provided.
1 is pinched. On the other hand, the end faces of the pair of outer rings 7a and 7b facing each other are respectively connected to the intermediate housing 2.
Abut on the stepped portions 12a and 12b formed on the inner peripheral surface. Further, a mounting flange 13 is provided on the outer peripheral surface of the intermediate housing 2, and the intermediate housing 2 is provided on an intermediate portion in the axial direction.
The oil supply hole 14 which connects the inner and outer peripheral surfaces to each other is formed.

In order to rotatably support the pinion shaft 5 inside the housing 4 forming the differential gear by the double row rolling bearing device 1 as described above, FIG.
The intermediate housing 2 is fixed to the housing 4 by the mounting flange 13 as shown in FIG. Further, a pinion shaft 5 is fitted inside the pair of inner rings 9a and 9b, and a pinion 15 fixed to a portion near the inner end of the pinion shaft 5 (a portion near the left end in FIG. 14), and an outer end of the pinion shaft 5 The pair of inner rings 9a and 9b and the inner ring spacer 11 are sandwiched from both sides in the axial direction between the hub 16 and the hub 16 screwed and fixed to the outside (right end in FIG. 14). In this state, the pinion 15 meshes with a ring gear 17 rotatably supported in the housing 4. A portion protruding from the pinion 15 at the tip (the left end in FIG. 14) of the pinion shaft 5 is rotatably supported in the housing 4 by a rolling bearing such as a cylindrical roller bearing 18. The gap between the inner peripheral surface of the cylindrical portion 25 formed at the outer end of the intermediate housing 2 (the right end in FIGS. 13 and 14) and the outer peripheral surface of the hub 16 is closed by a seal ring 28. The outer surface of the seal ring 28 is covered with a slinger 29,
The inside and outside of the housing 4 are sealed.

[0005] The differential gear as described above transmits the rotation of the propeller shaft connected to the pinion shaft 5 to the ring gear 17 via the pinion shaft 5 and the pinion 15, and further transmits the rotation to the ring gear 17. ,
The wheels are rotationally driven via a drive shaft (not shown). When the vehicle advances, the ring gear 17 rotates in the clockwise direction in FIG. 14 and lifts up the lubricating oil (differential oil) accumulated at the bottom of the housing 4 and further splashes it around. The lubricating oil splashed to the surroundings in this manner passes through an oil supply passage 19 provided in a part of the housing 4 and an oil supply hole 14 provided in the intermediate housing 2, and the pair of tapered roller bearings 3 a. , 3b. The lubricating oil fed between the two tapered roller bearings 3a and 3b in this manner causes the two tapered roller bearings 3a and 3b to move from the small diameter side to the large diameter based on the pumping action of the two tapered roller bearings 3a and 3b. Pass on the radial side. As a result, these tapered roller bearings 3a, 3b are lubricated.

[0006]

In the case of the conventional structure shown in FIGS. 13 and 14, the intermediate housing 2 is provided between the housing 4 and the pair of tapered roller bearings 3a and 3b.
The cost and the installation space of the double-row rolling bearing device 1 increase. Further, when the intermediate housing 2 is formed by cutting, the yield of the material is deteriorated, and the machining operation is troublesome and causes an increase in cost. On the other hand, when the intermediate housing 2 is manufactured by casting, there is a case where the material is increased and the reliability is lacking, instead of being manufactured at low cost.

[0007] Of the above-mentioned publications, JP-A-9-15
2008, Japanese Utility Model Application Laid-Open No. 5-1505, 7-2
Japanese Patent Application Laid-Open No. 666-666 discloses an apparatus provided with the intermediate housing 2 as described above.
In the publication, EP 0 409 564 A2, an outer ring is directly supported and fixed to a housing of a differential gear without providing an intermediate housing. However, the work described in these publications is troublesome because an oil supply hole is formed at an axially intermediate portion of an integrated outer race having a double row of outer raceways on the inner peripheral surface. That is, the operation of forming a through hole in the outer race, which is made of a hard metal such as bearing steel and is much harder than that of the intermediate housing, is troublesome, the service life of the tool may be short, and the cost is particularly high.

On the other hand, Japanese Utility Model Laid-Open No. 4-111918 discloses a structure in which, of the outer races constituting a double row rolling bearing device, an outer raceway portion is made of steel or carbon steel, and the other portions are made of cast iron. Are listed. In the case of this conventional structure, since the oil supply hole is formed at the time of casting, it is possible to suppress an increase in cost due to the formation of the oil supply hole. However,
As the steel or carbon steel is heat-treated to harden the outer ring raceway, dimensional changes occur due to the graphitization of carbon in the cast iron. , Which also increases costs. Further, at the time of grinding for finishing a double row outer raceway existing on the inner race surface of the outer race, the cast iron portion of the outer race surface of the outer race must be used as a reference plane. When the reference surface of the finish processing of the inner surface with high hardness is used as the reference surface of the cast iron part with relatively low hardness and easy wear, the processing conditions such as the pressing force of the grinding stone and the processing time are greatly limited, and in some cases, May hinder the manufacturing operation of the double-row rolling bearing device including the outer ring. SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and has been devised in order to realize a double-row rolling bearing device which is inexpensive and has sufficient reliability by eliminating an element for complicating the processing of the outer ring.

[0009]

The double-row rolling bearing device of the present invention is provided with a double-row outer raceway on the inner peripheral surface by combining a pair of outer race elements, and is externally fitted to each of the outer raceways and the rotating shaft. By providing a plurality of rolling elements between the inner ring raceway and a plurality of rows of inner ring tracks provided on the outer peripheral surface of the inner ring, the rotating shaft is rotatably supported. In particular, in the double row rolling bearing device of the present invention, of the pair of outer ring elements, at least one of the pair of outer ring elements in the axial direction has the opposite side to the axial one end of the other outer ring element. A notch extending from the inner peripheral surface to the outer peripheral surface of the one outer race element is formed in the end edge in the diametrical direction. Further, a fixing means for fixing the outer ring element to the housing is provided on any one of the pair of outer ring elements.

[0010]

In the double row rolling bearing device of the present invention configured as described above, since the fixing means is provided on any of the outer ring elements, the double row rolling bearing is supported on a casing of a differential gear or the like. No intermediate housing is required. or,
Lubricating oil can be fed into the inside of the outer ring constituted by the pair of outer ring elements through a cutout formed at the edge of at least one of the outer ring elements. Since such a notch can be formed at the same time when the rough shape of the outer ring element is formed by forging, the forming operation is not particularly troublesome.

[0011]

FIG. 1 shows a first embodiment of the present invention. The outer race 21 constituting the double-row rolling bearing device 20 of the present invention is formed by combining a pair of outer race elements 22a, 22b, and has a double-row outer raceway 6a, 6b on the inner peripheral surface.
Having. Of such a pair of outer ring elements 22a and 22b, one (left side in FIG. 1) outer ring element 22a is formed with a groove-shaped cutout portion 23 for allowing lubricating oil to pass therethrough. That is, the other (rightward in FIG. 1) outer ring element 22a of both axial ends (left and right directions in FIG. 1) of the outer ring element 22a
1B (see FIG. 1) which faces one axial edge (the left edge in FIG. 1).
The notch 23 at the edge of the right side of the outer ring 21).
Is formed in the diametric direction so as to reach from the inner peripheral surface to the outer peripheral surface.

The outer ring element 22a having such a notch 23 is formed by forging hard metal such as high carbon chromium bearing steel such as SUJ 2 into an intermediate material, and then cutting and grinding the intermediate material. It is manufactured by subjecting it to necessary finishing such as processing, and processing it to the desired shape and dimensions. The notch 23 is formed simultaneously with other portions by forging to form the intermediate material. Therefore, a new process for forming the notch 23 is unnecessary. In addition, each of the outer ring elements 22 serving as a reference surface at the time of the finish processing is used.
Since the outer diameter surfaces of a and 22b are the above-mentioned hard metal, there is no restriction on processing conditions such as the pressing force of the grindstone and the processing time during the finishing processing.

On the other hand, the other outer ring element 22b does not have the notch 23 as described above, but instead has a mounting flange 24 as a fixing means on the outer peripheral surface, at the outer end (FIG. 1). Cylindrical portions 25 are formed integrally with each other (at the right end). Like the one outer ring element 22a, the other outer ring element 22b is formed by forging a hard metal into an intermediate material, and then finishing the intermediate material. Since the outer race 21 constituting the double-row rolling bearing device 20 of the present invention is constituted by combining a pair of outer race elements 22a and 22b, the outer race 21 having a double-row outer raceway by itself is machined. The force required for the forging process is smaller than that of. In particular, the pair of outer ring elements 22a,
22b is divided into two in the axial direction of the outer ring 21, which is the direction in which the force acts during forging, so that the effect of reducing the force is large. Furthermore, the volume of each of the outer ring elements 22a and 22b is small, and heat treatment such as quenching can be easily performed. For this reason, the outer race 21 constituting the double-row rolling bearing device 20 for the differential gear of the large-sized vehicle can be made of inexpensive SUJ 2 instead of expensive SUJ 3.

The other outer ring element 22b is arranged concentrically with the one outer ring element 22a, and forms an outer ring 21 with its axial end faces abutting against each other, and a housing constituting a differential gear. 4 and is fitted and fixed. That is, the one outer ring element 2
2a is fixed to the inner half of the opening 26 (the left half in FIG. 1), and the notch 23 is positioned upward. The oil supply groove 27 provided in a part of the housing 4 is aligned. In this state, the inside of the housing 4 and the inner diameter side of the outer ring 21 communicate with each other via the oil supply groove 27 and the notch 23. The mounting flange 24 is connected and fixed to the outer surface of the housing 4 by mounting bolts (not shown).

On the other hand, a pair of inner races 9a and 9b constituting the double row rolling bearing device 20 together with the outer race 21 are externally fitted and fixed to the pinion shaft 5. And these two inner rings 9
Tapered rollers 10a and 10b, which are rolling elements, are provided between inner ring raceways 8a and 8b formed on the outer peripheral surfaces of the outer ring elements a and 9b and outer ring raceways 6a and 6b formed on the inner peripheral surfaces of the outer ring elements 22a and 22b. A plurality of the pinion shafts 5 are rotatably supported inside the outer ring 21. still,
The components other than the outer ring 21 including the supporting and fixing portions of the inner rings 9a and 9b with respect to the pinion shaft 5 are the same as the conventional structure shown in FIGS. Reference numerals are given, and duplicate description is omitted or simplified.

During the operation of the differential gear incorporating the double row rolling bearing device 20 of the present invention constructed as described above, the lubricating oil splashed around with the rotation of the ring gear 17 is supplied to the lubrication groove. Through the notch 27 and the notch 23, it is fed into the portion between the tapered rollers 10 a and 10 b arranged in a double row on the inner diameter side of the outer ring 21. The lubricating oil fed between the two rows of tapered roller bearings 10a and 10b in this manner is applied to the two rows of tapered rollers 10a and 10b.
Based on the pumping action accompanying the revolving motion of the a and 10b, it passes through these two rows of tapered rollers 10a and 10b, and lubricates the bearing part by these two rows of tapered rollers 10a and 10b.

The oil supply groove 27 or the notch 23
In the middle of the process, a filter member having a large number of voids continuous with each other, such as a sintered metal, a nonwoven fabric, a felt, etc., is incorporated, and is included in the lubricating oil which is repelled by the ring gear 17 and sent to the space. To collect foreign matter such as iron powder. With this configuration, it is possible to prevent the rolling surfaces of the tapered rollers 10a and 10b, the outer raceways 6a and 6b, and the inner raceways 8a and 8b from being damaged at an early stage due to foreign matter being caught in the double row. The durability of the rolling bearing device 20 can be improved. Also, by changing the porosity (transmittance) of the filter member, the amount of lubricating oil fed into the space can be adjusted. In this case, a material having a certain degree of rigidity, such as sintered metal, is used as the filter member, and the filter member is configured to stretch between the pair of outer ring elements 22a and 22b. For example, by changing the axial thickness of the filter member, the internal clearance of the double row rolling bearing device 20 can be adjusted. However, in this case, it is necessary to arrange the filter members substantially uniformly in the circumferential direction.
If the filter member is made of a sintered metal, the filter member itself can be subjected to an appropriate heat treatment to achieve the required strength and wear resistance. On the other hand, if the filter member is made of a soft material such as a nonwoven fabric or felt, the attachment and detachment work of the filter member can be easily performed.

In the case of the double-row rolling bearing device 20 according to the present invention which is constructed and operates as described above, the differential bearing 20 can be used without using the intermediate housing 2 as in the conventional structure shown in FIGS. Opening 26 in gear housing 4
Can be assembled. That is, one outer ring element 22a
Is attached to the inner half of the opening 26 and the inner end of the other outer ring element 22b to the outer end of the opening 26, and is formed on the outer peripheral surface of the other outer ring element 22b. The flange 24 is directly connected and fixed to the inner surface of the housing 4 by a mounting bolt (not shown). Since the intermediate housing is omitted, the cost and the installation space of the double row rolling bearing device can be reduced.

FIG. 2 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the notch 2
The mounting flange 24 is provided on the outer peripheral surface of the end of one of the outer ring elements 22a (the left side in FIG. 2) on which the third element 3 is formed. And
The mounting flange 24 is fixedly connected to an inner peripheral edge of an opening 26 provided in the housing 4 of the differential gear by a bolt (not shown). According to this,
An oil supply passage 19 is provided in a part of the housing 4 that matches the notch 23. The other configurations and operations are the same as those of the first example described above, and therefore, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

Next, FIGS. 3 and 4 show third and fourth examples of the embodiment of the present invention. In each of these examples, the tip of the pinion shaft 5 does not protrude from the pinion 15, and the cylindrical roller bearing 18 (FIGS. 1 and 2) that supports the tip of the pinion shaft 5 is omitted. Other configurations and operations are the same as those of the above-described first example or the above-described second example.

Next, FIG. 5 shows a fifth embodiment of the present invention.
An example is shown. In the case of this example, one side (left side of FIG. 5)
Cutouts 23, 23 are formed at two circumferential positions on the end face of the outer ring element 22a. The method of assembling to the differential gear, and the operation in the assembled state,
This is the same as in the first or third example described above.

Next, FIG. 6 shows a sixth embodiment of the present invention.
An example is shown. In the case of this example, one side (the left side of FIG. 6)
Notch portions are not formed in the outer ring element 22a, but are formed at two circumferential positions on the end face of the other (right side in FIG. 6) outer ring element 22b. Other configurations and operations are the same as those of the fifth example.

FIG. 7 shows a seventh embodiment of the present invention.
An example is shown. In the case of this example, one (left side of FIG. 7)
A stepped recess 30 is formed over the entire circumference in a portion of the outer peripheral surface of the outer ring element 22a that matches the outer diameter side opening of the notch 23. Since such a recess 30 is formed, when the double row rolling bearing 20 is assembled to the opening 26 (FIGS. 1 and 2) of the housing 4 of the differential gear, the notch 23 and the oil supply groove 27 (FIG. 3) Alternatively, the lubricating oil that has passed through the oil supply groove 27 or the oil supply path 19 can be sent to the notch portion 23 without making the phase with the oil supply path 19 (FIGS. 2 and 4) coincide. Other configurations and operations are the same as those in any of the above-described first to fourth examples. Therefore, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

Next, FIG. 8 shows an eighth embodiment of the present invention.
An example is shown. In the case of this example, one (left side of FIG. 8)
In the outer peripheral surface of the outer ring element 22a, a stepped concave portion 30 is formed at a portion matching the outer diameter side opening of the cutout portion 23, and a stepped concave portion 31 is formed at a portion matching the inner diameter side opening, respectively. It is formed over. Of these, the concave portion 31 on the inner diameter side is
The lubricating oil that has passed through the notch portion 23 from the outer diameter side to the inner diameter side is distributed over the entire circumference, and has a function of uniformly flowing the lubricating oil over the entire circumference of the tapered roller bearings 3a and 3b. Other configurations and operations are the same as those of the above-described seventh example, and therefore, the same parts are denoted by the same reference numerals, and overlapping description will be omitted. In this example and the above-described seventh example, the recess 3
The outer ring elements forming the 0 and 31 and the outer ring elements forming the notch 23 may be different. Further, in the case of this example, the outer ring element forming the recess 30 and the outer ring element forming the recess 31 may be different.

Next, FIG. 9 shows a ninth embodiment of the present invention.
An example is shown. In the case of this example, the other (the right side in FIG. 9) outer ring element 22b having the mounting flange 24 formed on the outer peripheral surface thereof
A step 32 is formed at the outer diameter side half of the end face of
Then, the end of one outer ring element 22a is externally fitted to align the two outer ring elements 22a and 22b with each other. Other configurations and operations are the same as those of the above-described eighth example, and therefore, the same parts are denoted by the same reference numerals, and overlapping description will be omitted.

FIG. 10 shows a tenth embodiment of the present invention. In the case of this example, a pair of inner rings 9
a, 9b are provided on the inner peripheral surfaces of the inner peripheral surfaces near the butting ends.
3, 33 are formed over the entire circumference. The pair of inner rings 9a and 9b are non-separably coupled to each other by a locking ring 34 locked in the locking grooves 33. In the case of the present embodiment as described above, the components of the double row rolling bearing device 20 are not separated before the housing is assembled to the housing, so that parts management and assembling work can be simplified. Other configurations and operations are described in FIG.
Are the same as in the case of the fifth example shown in FIG. 5, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

FIG. 11 shows an eleventh embodiment of the present invention. In the case of the present example, locking grooves 33a, 33a are formed over the entire circumference at portions near the butted ends of the outer peripheral surfaces of the pair of outer ring elements 22a, 22b. The pair of outer ring elements 22a, 22a are fixed by the locking rings 34a locked in the locking grooves 33a, 33a.
b are connected non-separably. Also in the case of this example, the components of the double-row rolling bearing device 20 do not separate even before being assembled to the housing. Other configurations and operations are the same as those of the fifth example shown in FIG. 5 described above, and therefore, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

Next, FIG. 12 shows a twelfth embodiment of the present invention. In the case of this example, a step-shaped relatively wide concave portion 3 is formed on the outer peripheral surface of the outer ring element 22b (the right side in FIG.
0a is formed over the entire circumference. And this recess 3
An annular filter member 35 is provided in Oa. Foreign matter in the lubricating oil sent to the inner diameter side of the outer ring 21 through the cutout portion 23 is collected by the filter member 35, so that the durability of the double row rolling bearing device can be improved. Other configurations and operations are the same as those of the above-described seventh example, and therefore, the same reference numerals are given to the same parts, and the overlapping description will be omitted.

[0029]

Since the present invention is constructed and operates as described above, it can contribute to the realization of a double row rolling bearing device which is inexpensive and has sufficient reliability.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first example of an embodiment of the present invention.

FIG. 2 is a sectional view showing the second example.

FIG. 3 is a sectional view showing a third example.

FIG. 4 is a sectional view showing a fourth example.

FIG. 5 is a sectional view showing the fifth example.

FIG. 6 is a sectional view showing a sixth example.

FIG. 7 is a sectional view showing a seventh example.

FIG. 8 is a sectional view showing the eighth example.

FIG. 9 is a sectional view showing a ninth example;

FIG. 10 is a sectional view showing the tenth example.

FIG. 11 is a sectional view showing the eleventh example.

FIG. 12 is a sectional view showing a twelfth example;

FIG. 13 is a sectional view showing an example of a conventional structure.

FIG. 14 is a cross-sectional view similarly showing a state of being assembled to a differential gear.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Double row rolling bearing device 2 Intermediate housing 3a, 3b Tapered roller bearing 4 Housing 5 Pinion shaft 6a, 6b Outer raceway 7a, 7b Outer race 8a, 8b Inner raceway 9a, 9b Inner race 10a, 10b Tapered roller 11 Inner race spacer 12a, 12b Step 13 Mounting flange 14 Oil supply hole 15 Pinion 16 Hub 17 Ring gear 18 Cylindrical roller bearing 19 Oil supply path 20 Double row rolling bearing device 21 Outer ring 22a, 22b Outer ring element 23 Notch 24 Mounting flange 25 Cylindrical part 26 Opening 27 Oil supply Groove 28 Seal ring 29 Slinger 30, 30a Recess 31 Recess 32 Step 33, 33a Lock groove 34, 34a Lock ring 35 Filter member

Claims (1)

[Claims] A pair of outer ring elements are combined to provide a double row of outer raceways on an inner peripheral surface, and each of these outer raceways and a double row of inner raceways provided on an outer peripheral surface of an inner race fixedly fitted to a rotating shaft. In a double row rolling bearing device that rotatably supports the rotating shaft by providing a plurality of rolling elements between them, the axial direction of at least one outer ring element of the pair of outer ring elements A cutout extending from the inner peripheral surface to the outer peripheral surface of the one outer ring element is formed in a diametrical direction on an end edge of the both end edges that is opposite to one axial end edge of the other outer ring element. And a fixing means for fixing the outer ring element to the housing in any one of the pair of outer ring elements.