JPH09189325A - Thrust roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent application of an excessive radial load on a holder regardless of eccentricity of a casing supporting an outer wheel and a shaft supporting an inner wheel. SOLUTION: An inside clearance 19a between an inner circumferential surface of a holder 3 and an outer peripheral surface of an inside flange 9 is made large enough to absorb eccentricity. In the case when whirling motion due to eccentricity is caused, the holder 3 and the inner wheel 5 are displaced in the radial direction in a range of the inside clearance 19a. A locking ring 20 is fixed on the inside flange 9, and separation of the holder 3 and the inner wheel 5 is prevented by a circular wheel part 22 of this locking ring 20.

Description

Detailed Description of the Invention

[0001]

INDUSTRIAL APPLICABILITY The thrust roller bearing (including a needle bearing) according to the present invention is mounted on a rotating part of an automobile transmission, a car cooler compressor or the like and is used to support a thrust load.

[0002]

2. Description of the Related Art For example, a thrust roller bearing 1 as shown in FIG. 4 is mounted on a rotating portion of a transmission or a car cooler compressor to support a thrust load applied to a rotating shaft or the like. The thrust roller bearing 1 includes a plurality of rollers 2 arranged in a radial direction, a cage 3 made of a circular ring as a whole to hold the plurality of rollers 2 rotatably, and a plurality of rollers 2. Left and right (left and right depend on the drawing; they do not represent the left and right positions in use; the same throughout this specification) The outer ring 4 and the inner ring 5 are sandwiched from both sides.
Each of the outer ring 4 and the inner ring 5 is formed in a ring shape from a metal plate having a sufficient hardness. The outer ring 4 among them is a circular ring-shaped outer ring race part 6 and this outer ring race part 6
And a cylindrical outer flange 7 formed over the entire circumference at the outer peripheral edge thereof. On the other hand, the inner ring 5 includes an inner ring race portion 8 having a circular ring shape, and an inner flange 9 formed on the inner peripheral edge of the inner ring race portion 8 over the entire circumference.

The cage 3 is formed by combining metal plates, each of which has a U-shaped cross section and is formed in a ring shape as a whole, in the middle, and the same number of pockets 10 as the rollers 2 are arranged in the radial direction. ing. An outer locking portion 11 is formed at the distal end edge of the outer flange 7 by partially bending the entire circumference or a plurality of portions in the circumferential direction inward in the diametrical direction. The engagement between the outer locking portion 11 and the outer peripheral edge of the retainer 3 prevents separation of the retainer 3 from the outer ring 4. On the other hand, an inner locking portion 12 is formed on the distal end edge of the inner flange 9 by bending the entire circumference or a plurality of portions in the circumferential direction outward in the diametric direction. The engagement between the inner locking portion 12 and the inner peripheral edge of the retainer 3 prevents separation of the retainer 3 from the inner ring 5. Therefore, the above-mentioned members forming the thrust roller bearing 1 are not separated.

A thrust roller bearing 1 constructed as described above
For example, as shown in FIG. 4, the outer flange 7 formed on the outer peripheral edge of the outer ring 4 is fitted in the holding portion 14 of the casing 13 and is attached to the rotating portion where the thrust load is generated. In this state, the outer race portion 6 of the outer race 4 contacts the step portion 15 of the holding portion 14, and the inner race portion 8 of the inner ring 5 contacts the step portion 17 of the shaft 16.
As a result, the shaft 16 is rotatably supported with respect to the casing 13, and the thrust load acting between the two members 16 and 13 is supported. An outer gap 18 is provided between the outer peripheral surface of the cage 3 and the inner peripheral surface of the outer flange 7, and an inner gap is provided between the inner peripheral surface of the cage 3 and the outer peripheral surface of the inner flange 9. The gaps 19 are respectively interposed. Due to the existence of these gaps 18 and 19, the cage 3 can be slightly displaced in the diametrical direction with respect to the outer ring 4 and the inner ring 5. Therefore, even when the shaft 16 is eccentric with respect to the casing 13, the eccentricity is absorbed and the rotation of the two members 13, 16 is allowed.

[0005]

In the case of the conventional thrust roller bearing 1 constructed and operated as described above, the eccentric amount of the shaft 16 with respect to the casing 13 increases (the eccentric amounts are the outer gap 18 and the inner gap 19). Will be larger than the width dimension of
And this eccentricity cannot be absorbed. When the eccentricity cannot be completely absorbed, the outer peripheral surface or the inner peripheral surface of the cage 3 becomes
The outer peripheral surface of the outer flange 7 or the outer peripheral surface of the inner flange 9 interferes with each other, and the interfering peripheral surfaces rub against each other strongly, and an excessive radial load is applied to the cage 3. As a result, the amount of heat generated in the thrust roller bearing portion becomes large, which may cause a failure such as seizure or cause damage to the cage 3.

In order to prevent the interference that causes the above-mentioned inconvenience, it is conceivable to increase the width dimension of the outer gap 18 and the inner gap 19. However, when such a method is adopted with the structure shown in FIG. 4, it is impossible to prevent the cage 3 holding the roller 2 from being separated from the outer ring 4 and the inner ring 5. As a result, the casing 13 and the shaft 16
The work of incorporating the thrust roller bearing 1 between and is complicated. In view of such circumstances, the thrust roller bearing of the present invention is intended to provide a structure capable of absorbing a larger amount of eccentricity while preventing troublesome assembling work.

[0007]

The thrust roller bearing of the present invention, like the conventional thrust roller bearing described above, has a plurality of rollers arranged in the radial direction and a plurality of rollers formed in the shape of a ring. A cage that holds the rollers rotatably, an outer ring composed of a ring-shaped outer ring race and a cylindrical outer flange formed over the entire circumference at the outer peripheral edge of the outer ring race, and a ring-shaped outer ring. The inner race includes an inner race portion and an inner flange formed on the inner peripheral edge of the inner race portion over the entire circumference. Then, the plurality of rollers are sandwiched between the outer race portion and the inner race portion.

Particularly, in the thrust roller bearing of the present invention, the outer gap between the outer peripheral surface of the cage and the inner peripheral surface of the outer flange, the inner peripheral surface of the cage and the outer periphery of the inner flange. At least one of the inner space and the inner space is larger than the eccentric amount between the member supporting the outer ring and the member supporting the inner ring. Along with this, a locking portion is provided on at least one of the outer flange and the inner flange, over a gap larger than the eccentric amount. Then, based on the engagement between the locking portion and the peripheral portion of the cage, the outer ring or the inner ring having the flange is prevented from being separated from the cage.

[0009]

The operation of the thrust roller bearing of the present invention having the above-described structure is the same as that of a conventional thrust roller bearing. Particularly, in the case of the thrust roller bearing of the present invention, at least one of the outer clearance and the inner clearance is in contact with and supports a member such as a casing that abuts and supports the outer race portion and the shaft and the like that abut and supports the inner race portion. Since it is larger than the eccentricity of the member, the gap absorbs the displacement between the two members due to the eccentricity. Moreover, even if the gap is increased,
Since the locking part prevents the cage from separating from the outer ring or inner ring,
Assembling the thrust roller bearing does not become troublesome.

[0010]

FIG. 1 shows a first embodiment of the present invention.
The thrust roller bearing 1a of the present invention is characterized in that the outer ring 4 and the inner ring 5 and the cage 3 are prevented from being separated from each other before assembly, and both inner and outer circumferential surfaces of the cage 3 and the inner circumference of the outer flange 7 are prevented. The structure is for preventing the surface and the outer peripheral surface of the inner flange 9 from interfering with each other. The structure and function of other parts are
Since it is the same as the conventional thrust roller bearing 1 shown in FIG. 4, the same parts are designated by the same reference numerals to omit or simplify the overlapping description, and the characteristic parts of the present invention will be mainly described below.

Between the inner peripheral surface of the cage 3 and the outer peripheral surface of the inner flange 9, an inner gap 19a having a sufficient width dimension W _19a in the radial direction (vertical direction in FIG. 1) is provided. ing. A locking ring 20 is internally fitted and fixed to the inner flange 9. The locking ring 20 is formed by injection molding a synthetic resin having oil resistance and heat resistance, for example, and is formed into an annular shape as a whole with an L-shaped cross section. The cylindrical portion 21 and one end edge of the cylindrical portion 21. The circular ring portion 22 is continuous from (the right end edge in FIG. 1). The locking ring 20 is fixed to the inner ring 5 by fitting the cylindrical portion 21 into the inner flange 9. In this state, the tip edge (the right end edge in FIG. 1) of the inner flange 9 is abutted against the end portion of the circular ring portion 22 near the outer peripheral surface on one side (the lower end portion of the left side surface in FIG. 1).

With the locking ring 20 fixedly fitted to the inner flange 9 in this manner, the circular ring portion 22 is diametrically outward from the inner peripheral surface of the inner flange 9 by L ₂₂ ( (Upward in FIG. 1). The protrusion amount L ₂₂ of the protrusion, which corresponds to the locking portion described in the claims, is larger than the width W _19a of the inner gap 19a (L ₂₂ > W).
_19a ). In other words, the outer diameter D ₂₂ of the circular ring portion ₂₂ is
Larger than the inner diameter R ₃ of the retainer _{3 (D 22> R 3)} .
Therefore, in the assembled state of the thrust roller bearing 1a, the outer peripheral edge portion of the circular ring portion 22 and the inner peripheral edge portion of the retainer 3 overlap each other in the thrust direction, and the retainer 3 and the inner race 5 are To prevent separation. The separation between the cage 3 and the outer ring 4 is prevented by the engagement of the outer locking portion 11 formed on the outer flange 7 with the outer peripheral edge of the cage 3 as in the conventional structure described above. As a result, the thrust roller bearing 1a
The cage 3 and the outer ring 4 and the inner ring 5 constituting the above are coupled to each other in a non-separable manner.

The outer diameter D ₂₂ of the circular ring portion 22 ensures a sufficient engagement margin between the circular ring portion 22 and the retainer 3, and the outer peripheral edge of the circular ring portion 22 and the outer ring 4 are different from each other. Design is regulated in order to sufficiently secure the dimension L ₂₄ of the gap 24 between the inner peripheral edge. That is, when the shaft 16 swivels with respect to the casing 13, the inner diameter R of the outer ring 4 is set so that the outer peripheral edge of the circular ring portion 22 and the inner peripheral edge of the outer ring 4 do not collide with each other.
The difference between the outer diameter D ₂₂ of ₄ and circular ring portion 22 (R ₄ -D ₂₂₎ is sufficiently secured. The outer peripheral edge of the inner race portion 8 and the outer locking portion 11
The same applies to the gap 26 between the tip end of the. Further, in the case of the illustrated embodiment, a plurality of oil passage holes 23 are formed in a portion of the circular ring portion 22 facing the inner clearance 19a.
Are intermittently formed in the circumferential direction. The plurality of oil passage holes 23 are provided in the portion where the plurality of rollers 2 are provided between the outer race portion 6 and the inner race portion 8 in order to allow a sufficient amount of lubricating oil to flow.

When the thrust roller bearing 1a of the present invention constructed as described above is used, for example, the outer flange 7 formed on the outer peripheral edge of the outer ring 4 is attached to the holding portion 14 of the casing 13.
Installed in the rotating part where the thrust load is generated. In this state, the outer race portion 6 of the outer race 4 contacts the step portion 15 of the holding portion 14, and the inner race portion 8 of the inner ring 5 contacts the step portion 17 of the shaft 16. As a result, the shaft 16 is rotatably supported with respect to the casing 13, and the thrust load acting between the two members 16 and 13 is supported. When the casing 13 and the shaft 16 are eccentric, the shaft 1
With the rotation of 6, the inner ring 5 makes whirling motion with respect to the outer ring 4. The displacement in the diametrical direction of the inner ring 5 with respect to the outer ring 4 due to the whirling motion is absorbed by the inner clearance 19a. Then, the whirling movement prevents an excessive load from being applied to the peripheral surface of the cage 3, thereby preventing the cage 3 from being damaged.

Particularly, in the case of the thrust roller bearing 1a of the present invention, the cage 3 holding the roller 2, the inner ring 4 and the inner ring 5 are provided.
In spite of the fact that they can be handled integrally as a non-separated state, a sufficient width dimension W _19a in the radial direction of the inner clearance 19a is secured, so that the casing 1
The amount of eccentricity between the shaft 3 and the shaft 16 can be increased to sufficiently absorb the displacement.

Next, FIG. 2 shows a second embodiment of the present invention. In the present embodiment, the present invention is applied to a structure in which the thrust roller bearing 1b is guided by the shaft 16. For this reason, this embodiment has a structure in which the inside and outside of the diametrical direction are reversed from those of the first embodiment. That is, in the case of this embodiment, the cage 3
Between the outer surface and the inner peripheral surface of the outer flange 7 of the is provided an outer gap 18a having a sufficient width W _18a over the radial direction (vertical direction in FIG. 2). Then, the cylindrical portion 21a of the locking ring 20a is externally fitted and fixed to the outer flange 7, and the inner peripheral edge portion of the circular ring portion 22a of the locking ring 20a and the outer peripheral edge portion of the retainer 3 are engaged with each other. The cage 3 and the outer ring 4 are prevented from separating. Other configurations and operations are the same as those of the above-described first embodiment except that the inside and outside of the diametrical direction are reversed.

Next, FIG. 3 shows a third embodiment of the present invention. In both the first embodiment and the second embodiment described above, the circular ring portions 22 and 22a of the locking rings 20 and 20a fitted and fixed to the outer flange 7 or the inner flange 9 are replaced with the outer ring 4 or the inner ring 5, respectively. In the thrust roller bearing 1c according to the present embodiment, the protrusion 25 is provided on the tip edge of the inner flange 9, while the locking portion is used to prevent separation from the cage 3.
Is formed toward the outer side in the diametrical direction (the upper side in FIG. 3).
A plurality of the protruding pieces 25 are provided intermittently in the circumferential direction. By engaging the leading edge of each of the projecting pieces 25 and the inner peripheral edge of the cage 3, separation of the inner ring 5 and the cage 3 is prevented. The member for preventing the retainer 3 and the inner ring 5 from separating is the circular ring portion 2 of the locking ring 20.
The configuration and operation are the same as those of the first embodiment described above except that the number of the protruding pieces 25 is changed from two.

[0018]

Since the thrust roller bearing of the present invention is constructed and operates as described above, it is possible to secure the durability of the thrust roller bearing which receives the thrust load between the members which relatively rotate in the eccentric state. Further, even if the dimensional accuracy and the assembly accuracy of the respective constituent parts are not particularly high, it is possible to prevent the outer ring and the inner ring from interfering with the cage and prevent damage to the cage. Also, the assembly work is not troublesome. Therefore, the rotary support having high reliability and durability can be obtained at low cost.

[Brief description of the drawings]

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

FIG. 2 is a partial sectional view showing the second embodiment.

FIG. 3 is a partial sectional view showing the third embodiment.

FIG. 4 is a partial sectional view showing an example of a conventional thrust roller bearing.

[Explanation of symbols]

 1, 1a, 1b, 1c Thrust roller bearing 2 Roller 3 Cage 4 Outer ring 5 Inner ring 6 Outer ring race part 7 Outer flange 8 Inner ring race part 9 Inner flange 10 Pocket 11 Outer locking part 12 Inner locking part 13 Casing 14 Holding part 15 step part 16 shaft 17 step part 18, 18a outer side clearance 19, 19a inner side clearance 20, 20a locking ring 21, 21a cylindrical part 22, 22a ring part 23 oil passage hole 24 gap 25 projecting piece 26 gap

Claims (1)

[Claims] 1. A plurality of rollers arranged in a radial direction, a cage made entirely in a circular ring shape to hold the plurality of rollers rotatably, an outer ring race section having a circular ring shape, and an outer ring race section. An outer ring composed of a cylindrical outer flange formed around the entire outer peripheral edge of the inner ring, an inner ring race portion having a circular ring shape, and an inner flange formed around the entire inner peripheral edge of the inner ring race portion. A thrust roller bearing comprising an inner ring composed of and a plurality of rollers sandwiched between the outer ring race portion and the inner ring race portion, and an outer circumference surface of the cage and an inner circumference of the outer flange. A member for supporting the outer ring and a member for supporting the inner ring, wherein at least one of the outer gap between the inner ring and the inner gap between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange, Eccentricity of the outer flan A locking portion is provided on at least one of the flange and the inner flange over a gap larger than the eccentric amount, and the flange is formed based on the engagement between the locking portion and the peripheral portion of the cage. A thrust roller bearing, characterized in that the outer ring or inner ring is prevented from separating from the cage.