JPH09137824A - Thrust roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a retainer from being applied with an excessive radial load regardless of the eccentricity between a casing supporting an outer ring and a shaft supporting an inner ring. SOLUTION: An outside elastic ring 20 and an inside elastic ring 21 are installed between both inner/outer peripheral surfaces of a retainer 3 and the inner peripheral surface of an outside flange 7 and the outer peripheral surface of an inside flange 9. In both the elastic rings 20, 21, the width spread in the diameter direction is expanded/shrunk freely and elastically. When whirling is generated owing to an eccentricity, the displacement is absorbed by the elastic deformation of both the elastic rings 20, 21.

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 A thrust roller bearing as shown in FIG. 5, for example, is mounted on a rotating portion of a transmission, a car cooler compressor or the like 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. It does not represent the left and right position in use. The same applies throughout this specification.)
It is composed of an outer ring 4 and an inner ring 5 that 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. Outer ring 4 of these is
The outer ring race portion 6 has a circular ring shape, and a cylindrical outer flange 7 formed on the outer peripheral edge of the outer ring race portion 6 over the entire circumference. 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. The tip end edge of the outer flange 7 is formed by bending the entire circumference or a plurality of locations in the circumferential direction partially inward in the diametrical direction to form the outer locking portion 13.
The engagement between the outer locking portion 13 and the outer peripheral edge of the cage 3 prevents the cage 3 and the outer ring 4 from being separated. On the other hand, the front edge of the inner flange 9 is formed with the inner locking portion 14 by bending the entire circumference or a plurality of locations in the circumferential direction partially outward in the diametrical direction.
The engagement between the inner locking portion 14 and the inner peripheral edge of the cage 3 prevents the cage 3 and the inner ring 5 from being separated. 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. 5, the outer flange 7 formed on the outer peripheral edge of the outer ring 4 is fitted in the holding portion 12 of the casing 11 and mounted on the rotating portion where the thrust load is generated. In this state, the outer ring race portion 6 forming the outer ring 4 contacts the step portion 15 of the holding portion 12, and the inner ring race portion 8 forming the inner ring 5 contacts the step portion 17 of the shaft 16.
As a result, the shaft 16 is rotatably supported by the casing 11, and the thrust load acting between the two members 16 and 11 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 11, the eccentricity is absorbed and the rotation of the two members 11, 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 11 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, the center of the outer ring 4 and the center of the inner ring 5 are likely to be greatly deviated when the thrust roller bearing 1 is assembled. And if the deviation between these two centers becomes excessive,
When the thrust roller bearing 1 rotates, that is, when the outer ring 4 and the inner ring 5 rotate relative to each other, the amount of slippage generated at the contact portion between the rolling surface of each roller 2 and the outer ring race portion 6 and the inner ring race portion 8 is Will increase. An increase in the amount of slippage causes an increase in the amount of heat generated in the thrust roller bearing portion and an increase in rolling resistance. Therefore, there is a limit to increase the width of the outer gap 18 and the inner gap 19. Further, even if the widths of the outer gap 18 and the inner gap 19 are increased, the gaps move as the cage 3 rotates, so the eccentricity of the shaft 16 causes the inner surface of the inner flange 9 and the cage 3 to be eccentric. Interference with the peripheral surface occurs. Therefore, simply increasing the gap is
It is not a sufficient solution to prevent interference.

Therefore, conventionally, the eccentric amount of the shaft 16 with respect to the casing 11 is suppressed to a small value to prevent the above-described inconvenience from occurring. Therefore, it is necessary to increase the processing accuracy of the casings 11 and 16 and the assembling accuracy of the radial bearing portions of the both members 11 and 16, resulting in high processing cost and assembly cost. 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 suppressing an increase in heat generation amount and rolling resistance.

[0008]

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 width dimension in the diametrical direction provided between the outer peripheral surface of the cage and the inner peripheral surface of the outer flange can be elastically expanded and contracted. An outer elastic ring, and an inner elastic ring provided between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange and elastically expandable / contractible in the width dimension in the diametrical direction.

[0010]

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. In particular, in the case of the thrust roller bearing of the present invention, even if the member such as the casing that abuts and supports the outer race portion and the shaft and the like that abuts and supports the inner race portion are eccentric, the outer elastic ring The elastic deformation of the inner elastic ring and the inner elastic ring absorbs the displacement between the two members due to the eccentricity. Moreover, due to the presence of both elastic rings, the center of the outer ring and the center of the inner ring do not deviate significantly when the thrust roller bearing is assembled, and the rolling surface of each roller and the outer ring race part The amount of slippage generated at the contact portion with the inner ring race portion can be suppressed to be small.

[0011]

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 are prevented from being largely decentered during assembly, and both the inner and outer peripheral surfaces of the cage 3 and the inner and outer flanges of the outer flange 7 are prevented. It has a structure for preventing interference with the outer peripheral surface of 9. Since the structure and operation of the other parts are the same as those of the conventional thrust roller bearing 1 shown in FIG. 5, the same parts are designated by the same reference numerals to omit or simplify duplicate description, and the present invention will be described below. The description will focus on the characteristic part of.

An outer elastic ring 20 is provided between the outer peripheral surface of the retainer 3 and the inner peripheral surface of the outer flange 7, and an inner side is provided between the inner peripheral surface of the retainer 3 and the outer peripheral surface of the inner flange 9. Elastic rings 21 are provided respectively. Both the outer and inner elastic rings ₂₀ and ₂₁ have a structure capable of elastically expanding and contracting the width dimensions W ₂₀ and W ₂₁ in the diametrical direction.
Therefore, the cage 3 is elastically supported between the inner peripheral surface of the outer flange 7 and the outer peripheral surface of the inner flange 9 so as to be displaceable in the diametrical direction.

In the case of this embodiment, the outer elastic ring 20 is used.
Is composed of a short-cylindrical holding ring 22 and an annular elastic material 23 which is joined and supported on the outer peripheral surface of the holding ring 22 by adhesion, baking, or the like. In the illustrated embodiment, the outer peripheral surface of the elastic member 23 is joined and supported by the inner peripheral surface of the outer flange 7 by adhesion, baking, or the like. The width of the elastic member 23 in the diametrical direction in the free state is uniform over the entire circumference. Therefore, the retaining ring 22 is retained diametrically inside the outer flange 7 and concentric with the outer flange 7 unless an external force acts.

The inner elastic ring 21 is composed of a short cylindrical holding ring 24 and an annular elastic member 25 which is joined and supported on the inner peripheral surface of the holding ring 24 by adhesion, baking or the like. In the case of the illustrated embodiment, the inner peripheral surface of the elastic member 25 is joined and supported by the outer peripheral surface of the inner flange 9 by adhesion, baking or the like. In addition, the width dimension of the elastic member 25 in the diametrical direction in the free state is uniform over the entire circumference. Therefore, the retaining ring 24 is retained diametrically inside the inner flange 9 and concentric with the inner flange 9 unless an external force acts.

The holding rings 22 and 24 constituting the outer elastic ring 20 and the inner elastic ring 21 are formed of a metal plate such as stainless steel or a synthetic resin such as polyamide, polytetrafluoroethylene, polyacetal or the like. In any case, it is preferable to use a material that can reduce the sliding resistance between the peripheral surfaces of the retaining rings 22 and 24 and the peripheral surface of the retainer 3 and is less likely to be worn. Therefore, when the holding rings 22 and 24 are made of metal, the peripheral surfaces of the holding rings 22 and 24 are slidably in contact with the peripheral surface of the cage 3.
It is conceivable to coat the slippery material such as the above synthetic resin, or to make the cage 3 with these synthetic resins, or to coat the peripheral surface of the cage 3 with the slippery material. Further, the elastic members 23 and 25 constituting the outer elastic ring 20 and the inner elastic ring 21 are made of oil resistant rubber, elastomer, etc.
It is made of an oil resistant material that is not affected by the lubricating oil flowing through the thrust roller bearing 1a.

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 12 of the casing 11.
Installed in the rotating part where the thrust load is generated. In this state, the outer ring race portion 6 forming the outer ring 4 contacts the step portion 15 of the holding portion 12, and the inner ring race portion 8 forming the inner ring 5 contacts the step portion 17 of the shaft 16. As a result, the shaft 16 is rotatably supported by the casing 11, and the thrust load acting between the two members 16 and 11 is supported. When the casing 11 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 diametrical displacement of the inner ring 5 with respect to the outer ring 4 based on this whirling motion causes the outer elastic ring 20 and the inner elastic ring 21 to elastically deform in a direction in which the width dimension in each diametrical direction is expanded or contracted. Absorb by things. And, by the whirling motion,
An excessive load is prevented from being applied to the peripheral surface of the cage 3 to prevent the cage 3 from being damaged.

Moreover, in the case of the thrust roller bearing 1a of the present invention, due to the existence of both elastic rings 20 and 21,
When the thrust roller bearing 1a is assembled, the center of the outer ring 4 and the center of the inner ring 5 do not deviate significantly. Therefore,
Even when the width dimensions W ₂₀ and W ₂₁ of both elastic rings ₂₀ and ₂₁ are sufficiently large in order to increase the displacement absorbing capability, the assembly work is not particularly troublesome and the thrust roller bearing 1a is rotated. It is possible to reduce the amount of slippage that occurs at the contact portion between the rolling surface of each roller 2 and the outer race portion 6 and the inner race portion 8.

Next, FIGS. 2 to 4 show a second embodiment of the present invention. In the case of this embodiment, the outer elastic ring 20 a mounted between the outer peripheral surface of the cage 3 and the inner peripheral surface of the outer flange 7, and the inner peripheral surface of the cage 3 and the inner flange 9 are mounted.
As shown in FIGS. 3 to 4, a corrugated spring-shaped inner member is used as the inner elastic ring 21a to be mounted between the outer peripheral surface and the outer peripheral surface. Of course, the width dimensions W _20a and W _21a of the outer and inner elastic rings 20 a and 21 a in the diametrical direction are elastically expandable and contractible.
Therefore, the cage 3 is elastically supported between the inner peripheral surface of the outer flange 7 and the outer peripheral surface of the inner flange 9 in a diametrically displaceable manner, as in the case of the first embodiment. ing. Both the outer and inner elastic rings 20a, 2
1a is made of a material that has oil resistance, has a low surface friction coefficient, and is hard to wear. For example, it is conceivable that the surface of a metal spring material is covered with a synthetic resin having oil resistance, or that the whole is made of a synthetic resin having oil resistance and elasticity. In the case of the illustrated embodiment, the outer locking portion 13 formed at the tip edge of the outer flange 7 prevents the outer elastic ring 20a from slipping out from the inner peripheral side of the outer flange 7. Further, the inner locking portion 14 formed on the tip edge of the inner flange 9 prevents the inner elastic ring 21a from coming off from the outer peripheral side of the inner flange 9.

Also in the case of the present embodiment configured as described above,
The displacement of the inner ring 5 with respect to the outer ring 4 in the diametrical direction based on the whirling motion due to the eccentricity of the casing 11 and the shaft 16 causes the outer elastic ring 20a and the inner elastic ring 21 to move.
a absorbs by elastically deforming in a direction in which the width dimension across each diametrical direction is expanded and contracted. 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.
Further, even if the width dimensions W _20a and W _21a of the elastic rings 20a and _21a are made sufficiently large in order to increase the displacement absorbing capability, the thrust roller bearing 1b can be easily assembled without troublesome assembling work. It is possible to suppress the amount of slippage that occurs at the contact portion between the rolling surface of each roller 2 and the outer race portion 6 and the inner race portion 8 during rotation.

[0020]

Since the thrust roller bearing of the present invention is constructed and operates as described above, interference between the outer ring and the inner ring and the cage can be prevented without particularly increasing the dimensional accuracy and assembly accuracy of each component. Therefore, the cage can be prevented from being damaged. 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 schematic view of an outer elastic ring incorporated in the second embodiment as seen from the side of FIG.

FIG. 4 is a schematic view of the inner elastic ring as viewed from the side of FIG.

FIG. 5 is a partial sectional view showing an example of a conventionally known thrust roller bearing.

[Explanation of symbols]

 1, 1a, 1b 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 Casing 12 Holding part 13 Outer locking part 14 Inner locking part 15 steps Part 16 Shaft 17 Stepped part 18 Outer gap 19 Inner gap 20, 20a Outer elastic ring 21, 21a Inner elastic ring 22 Retaining ring 23 Elastic material 24 Retaining ring 25 Elastic material

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 on the outer peripheral edge of the entire circumference, an inner ring race portion having a circular ring shape, and an inner flange formed on the inner peripheral edge of the inner ring race portion over the entire circumference. A thrust roller bearing having an inner ring composed of and a plurality of rollers sandwiched between the outer race portion and the inner race portion, and an outer peripheral surface of the cage and an inner periphery of the outer flange. An outer elastic ring that is elastically expandable and contractible in the width dimension across the diametrical direction, and a diameter that is provided between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange. The inner elastic ring that elastically expands and contracts the width across the direction Thrust roller bearing characterized by having.