JP2000266043A - Roller thrust bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To absorb a large eccentric amount while preventing the cost-up and the increase of the rotational resistance by determining 1/2 of the total clearance obtained by adding an outer diameter side bearing bore clearance and an inner diameter side bearing bore clearance over the diameter direction, larger than the eccentric amount of an outer ring supporting member and an inner ring supporting member. SOLUTION: An outer diameter side bearing bore clearance 18 and an inner diameter side bearing bore clearance 19 respectively have the widths of W18 and W19 in such a state that an outer ring 4, an inner ring 5 and a holding unit 3 are concentraically mounted to one another. 1/2(=W18+W19) of the total clearance (=2W18+2W19) obtained by totally adding the width W18 of the outer diameter side bearing bore clearance 18 and the widths W19 of the inner diameter side bearing bore clearance 19 over the diameter direction is larger than the eccentric amount δ of a casing 13 and a counterpart 24 to be (W18+W19)>δ}. The sum of both width W18, W19 is sufficiently large, so that the eccentric amount δ can be effectively absorbed. As a result, the addition of the forcible force to each part of a roller thrust bearing can be prevented, and the durability of a roller bearing 1c can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION A thrust roller bearing (including a needle bearing) according to the present invention is used to support a thrust load by being mounted on a rotating part of a transmission of an automobile, a compressor for a car cooler, or the like.

[0002]

2. Description of the Related Art For example, a thrust roller bearing 1 as shown in FIG. 12 is mounted on a rotating portion of a transmission or a compressor for a car cooler 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, and a cage 3 which is formed in a ring shape as a whole and holds the plurality of rollers 2 in a freely rolling manner.
And an outer ring 4 and an inner ring 5 sandwiching the plurality of rollers 2 from both sides (right and left are shown in the drawing; they do not represent left and right positions in a used state; the same applies to the entire specification). 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 includes a ring-shaped outer ring race portion 6 and a cylindrical outer flange 7 formed over the entire outer periphery of the outer ring race portion 6. On the other hand, the inner race 5 includes a circular inner race part 8 and an inner flange 9 formed over the entire inner periphery of the inner race part 8.

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 constituting the thrust roller bearing 1 are not separated even before being assembled to the rotating member.

A thrust roller bearing 1 constructed as described above
For example, as shown in FIG. 12, the outer flange 7 formed on the outer peripheral edge of the outer race 4 is attached to the holding portion 14 of the casing 13.
And attached to the rotating part where thrust load is generated. In this state, the outer race portion 6 constituting the outer race 4 comes into contact with the step portion 15 of the holding portion 14, and the inner race portion 8 constituting the inner race 5 comes into contact with the step portion 17 of the shaft 16. As a result, the shaft 16 is rotatably supported by the casing 13, and a thrust load acting between the two members 16, 13 is supported. Note that an outer diameter side bearing inner gap 18 is provided between the outer peripheral surface of the cage 3 and the inner peripheral surface of the outer flange 7, and between the inner peripheral surface of the cage 3 and the outer peripheral surface of the inner flange 9. An inner-diameter-side bearing inner gap 19 is interposed therebetween. Due to the existence of these two bearing inner gaps 18 and 19, the cage 3 can freely displace slightly in the diameter direction with respect to the outer ring 4 and the inner ring 5. Therefore, the shaft 1 is
Even when 6 is eccentric, rotation of these two members 13 and 16 is allowed while absorbing this eccentricity.

In the case of the conventional thrust roller bearing 1 constructed and operating as described above, the shaft 1
6 increases (the eccentricity increases when the eccentricity decreases in the outer-diameter bearing inner clearance 1).
8, larger than the width dimension of the inner diameter side bearing inner gap 19)
This eccentricity cannot be completely absorbed. When the eccentricity cannot be completely absorbed, the outer peripheral surface or the inner peripheral surface of the cage 3
It interferes with the inner peripheral surface of the outer flange 7 or the outer peripheral surface of the inner flange 9, and the interfering peripheral surfaces strongly rub against each other, and further, an excessive radial load is applied to the retainer 3. As a result, the amount of heat generated at the thrust roller bearing portion increases, causing a failure such as seizure or causing damage to the cage 3.

In order to prevent the interference causing the above-described inconvenience, it is conceivable to increase the width of the outer-diameter bearing inner gap 18 and the inner-diameter bearing inner gap 19. However,
When such a method is employed with the structure shown in FIG. 12, it is possible to prevent the cage 3 holding the rollers 2 from being separated from the outer ring 4 and the inner ring 5 before assembling to the rotating member. become unable. As a result, the work of installing the thrust roller bearing 1 between the casing 13 and the shaft 16 becomes troublesome.

As a structure for solving such inconvenience, Japanese Patent Application Laid-Open Nos. 9-137824 and 9-18932 disclose.
No. 5 describes a thrust roller bearing as shown in FIGS. First, as shown in FIG.
Thrust roller bearing 1 described in JP-137824A
a, an outer-diameter-side elastic ring 20 and an inner-diameter-side elastic ring 21 are provided between the inner and outer peripheral surfaces of the cage 3 and the inner peripheral surface of the outer flange 7 and the outer peripheral surface of the inner flange 9, respectively. These two elastic rings 20 and 21 are elastically expandable and contractible in the width dimension in the diameter direction. When whirling motion occurs due to eccentricity between the casing 13 supporting the outer ring 4 and the shaft 16 supporting the inner ring 5, the elastic rings 20 and 21 elastically deform to absorb the displacement.

[0008] Further, as shown in FIG.
In the thrust roller bearing 1b described in Japanese Patent No. 25, an inner diameter side bearing inner gap 19 between the inner peripheral surface of the retainer 3 and the outer peripheral surface of the inner flange 9 is formed by a casing 13 supporting the outer ring 4 and the inner ring 5. It is made large enough to absorb eccentricity with the supported shaft 16. When the whirling motion based on this eccentricity occurs, the retainer 3 and the inner ring 5 are displaced in the radial direction within the range of the inner diameter side bearing inner gap 19. A locking ring 22 is fixed to the inner flange 9, and the annular portion 23 of the locking ring 22 prevents separation of the retainer 3 and the inner ring 5. Also in the case of such a structure, an excessive radial load is prevented from being applied to the retainer 3 irrespective of the eccentricity between the casing 13 supporting the outer ring 4 and the shaft 16 supporting the inner ring 5.

[0009]

In the case of the conventional structure shown in FIG. 13, parts not originally required for forming the thrust roller bearing, such as the outer diameter side elastic ring 20 and the inner diameter side elastic ring 21. , Parts processing, parts management, and assembling work are all complicated and costly. or,
Since the inner and outer peripheral edges of the two elastic rings 20 and 21 and the mating surfaces are in friction with each other, the rotational resistance of the thrust roller bearing is increased, and the transmission efficiency of various mechanical devices incorporating the thrust roller bearing is deteriorated. There are inconveniences. Furthermore, since the two elastic rings 20 and 21 have a function of arranging the constituent members concentrically with each other when no external force acts on the thrust roller bearing, the rollers 2 and 21 are located between the casing 13 and the shaft 16. The function of centering the retainer 3 holding 2 is weak.

In the case of the conventional structure shown in FIG.
Since the eccentricity between the casing 13 and the shaft 16 is absorbed only by the inner-diameter bearing inner gap 19, the width of the inner-diameter bearing inner gap 19 in the diameter direction must be increased. For this reason, in order to prevent the constituent members from being separated from each other, a locking ring 22 which is not necessary for forming a thrust roller bearing is required, which increases the cost. In view of such circumstances, the present invention has been made to realize a thrust roller bearing that can absorb a large amount of eccentricity while preventing an increase in cost and an increase in rotational resistance.

[0011]

In the thrust roller bearing according to the present invention, the thrust roller bearings according to the first and second aspects are all arranged in the radial direction in the same manner as the above-mentioned conventional thrust roller bearing. A plurality of rollers, a retainer that is formed in a ring shape as a whole and holds the plurality of rollers in a freely rolling manner, and a ring-shaped outer ring race portion and an outer peripheral edge of the outer ring race portion over the entire circumference. An outer ring composed of a formed cylindrical outer flange and an inner ring composed of a circular inner race part and an inner flange formed all around the inner periphery of the inner race part. And, the plurality of rollers are sandwiched between the outer race part and the inner race part,
A pair of members that rotate the outer ring and the inner ring relatively to each other,
It is used in a state where the displacement in the radial direction with respect to the member is prevented.

In particular, in the thrust roller bearing according to the first aspect, the outer peripheral surface of the retainer and the inner peripheral surface of the outer flange are arranged in a state where the outer ring, the inner ring and the retainer are concentrically arranged. Between the outer diameter side bearing inner gap, the inner diameter side bearing inner gap having substantially the same width as the outer diameter side bearing inner gap between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange, A member that supports the outer ring and a member that supports the inner ring each provide 1/2 of a total gap obtained by adding the outer-diameter-side bearing inner gap and the inner-diameter-side bearing inner gap in the diametric direction. Greater than the amount of eccentricity.

[0013] In the thrust roller bearing according to the second aspect, the flange formed on the peripheral edge of at least one of the outer ring and the inner ring is looser with respect to the member to which the bearing ring is to be assembled. In a state where the member, the outer ring, the inner ring, and the retainer are concentrically arranged with each other, the outer diameter side bearing is disposed between the outer peripheral surface of the retainer and the inner peripheral surface of the outer flange. The gap, between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange, an inner-diameter-side bearing inner gap having substantially the same width as the outer-diameter-side bearing inner gap, at the peripheral edge of the at least one raceway ring. An assembling gap is provided between the formed flange and a part of a peripheral surface of a member to which the bearing ring is to be assembled. Added 1/2 of total clearance, is made larger than the eccentricity of the member supporting member and the inner ring supporting the outer ring.

The thrust roller bearings according to claims 3 and 4 each include a plurality of rollers arranged in a radial direction.
A retainer that is made entirely in a ring shape and holds the plurality of rollers so that it can roll freely, and a bearing ring having a ring-shaped race portion,
A cylindrical flange formed on the periphery of the bearing ring. The plurality of rollers are held between a thrust raceway surface provided on the other member that rotates relative to the other member that supports and fixes the raceway ring while preventing displacement in the radial direction and the race portion. Used in the state.

In particular, in the thrust roller bearing according to the third aspect, in a state where the bearing ring and the retainer are arranged concentrically with each other, a space between the peripheral surface of the retainer and the peripheral surface of the flange is provided. And a half of the total clearance obtained by adding all the clearances in the bearing in the diametric direction to
The amount of eccentricity between the one member and the other member is set larger.

In the thrust roller bearing according to a fourth aspect of the present invention, the bearing ring, the retainer, and one of the members are concentrically arranged with respect to the inner and outer circumferential surfaces of the retainer. A clearance in the bearing is provided between one peripheral surface and one peripheral surface of the flange, and an assembling clearance is provided between the flange and a partial peripheral surface of the one member, respectively. A half of the total gap obtained by adding all the inner gaps in the diameter direction is set to be larger than the eccentricity of the one member and the other member.

Further, the thrust roller bearing according to claim 5 comprises a plurality of rollers arranged in a radial direction and a retainer which is formed in a ring shape as a whole and holds the plurality of rollers in a freely rolling manner. Prepare. The plurality of rollers are sandwiched between thrust raceway surfaces provided on a pair of relatively rotating members, and one of the inner and outer circumferential surfaces of the cage is connected to the pair of members. It is used in a state where it faces the cylindrical surface formed on one of the members.

[0018] In particular, in the thrust roller bearing according to the fifth aspect, in a state where the cage and the one member are concentrically arranged, one of the inner and outer peripheral surfaces of the cage is provided. An assembling gap is provided between the surface and the cylindrical surface, and a half of a total gap obtained by adding all the assembling gaps in the diametric direction is set to be larger than the eccentricity of the pair of members. .

[0019]

The operation of the thrust roller bearing of the present invention constructed as described above is the same as that of a conventional thrust roller bearing. In particular, in the case of each thrust roller bearing of the present invention, since appropriate gaps are arranged in each part, a pair of members can be connected to each other while preventing separation of constituent members without using extra parts. The eccentricity existing between them can be absorbed.

[0020]

FIG. 1 shows a first embodiment of the present invention corresponding to claim 1. The feature of the thrust roller bearing 1c of the present invention is that the outer ring 4
To prevent the inner ring 5 and the retainer 3 from being separated from each other and to prevent the inner and outer peripheral surfaces of the retainer 3 from interfering with the inner peripheral surface of the outer flange 7 and the outer peripheral surface of the inner flange 9. In the structure. The structure and operation of the other parts are as described in FIG.
Is the same as the conventional thrust roller bearing 1 shown in FIG.
The same parts are denoted by the same reference numerals, and duplicate description will be omitted or simplified. Hereinafter, the description will focus on the characteristic parts of the present invention.

The outer diameter of each of the inner and outer peripheral surfaces of the cage 3 and the outer peripheral surface of the inner flange 9 and the inner peripheral surface of the outer flange 7 extends in the radial direction (vertical direction in FIG. 1). A side bearing inner gap 18 and an inner diameter side bearing inner gap 19 are provided. The outer-diameter-side bearing inner gap 18 and the inner-diameter-side bearing inner gap 19 have widths of W ₁₈ and W ₁₉ , respectively, in a state where the outer ring 4 and the inner ring 5 and the retainer 3 are concentrically arranged. The widths W ₁₈ and W ₁₉ are substantially equal to each other (W ₁₈ ≒ W _{19. The} difference is within a manufacturing error, for example, 20% or less).

In the above-described thrust roller bearing 1c, for example, the outer ring 4 is fitted inside the support recess 25 provided in the casing 13 without play, and the inner ring 5 is brought into contact with the end face of the mating member 24. Assembling allows both members 13 and 24 to rotate relative to each other while supporting a thrust load applied between casing 13 and mating member 24. Particularly, in the case of a thrust roller bearing 1c of this embodiment, the sum of all over a width W ₁₉ of width W ₁₈ and the inner diameter side bearing in the gap 19 of the outer diameter side bearing the gap 18 in the radial direction 1/2 of the total clearance (= 2W ₁₈ + 2W ₁₉ ) (= W ₁₈ + W)
₁₉ ) is larger than the eccentricity δ between the casing 13 and the counterpart member 24 (the distance between the rotation center of the casing 13 and the rotation center of the counterpart member 24) and {(W ₁₈ + W ₁₉ )> δ}.

Thrust roller bearing 1c of the present invention as described above
In the case of, the outer diameter side bearing inner gap 18 having substantially the same width dimension W ₁₈ , W ₁₉ on the outer diameter side and the inner diameter side of the cage 3.
And the inner-diameter-side bearing inner gap 19 are arranged, so that the cage 3 can be prevented from being separated from the outer ring 4 and the inner ring 5 without using extra parts such as an elastic ring and a locking ring. The eccentricity existing between the casing 13 and the counterpart member 24 can be absorbed. That is, even without particularly increasing the respective width dimension W ₁₉ of width W ₁₈ and the inner diameter side bearing in the gap 19 of the outer diameter side bearing the gap 18, the both width W _18, W ₁₉
Can be made sufficiently large to effectively absorb the eccentricity δ. As a result, an excessive force is prevented from being applied to each part of the thrust roller bearing, and the durability of the thrust roller bearing 1c can be improved.

FIG. 2 shows the results of an experiment conducted to confirm that the structure of the present invention is effective in improving durability. In FIG. 2, the vertical axis indicates the life ratio, and the horizontal axis indicates the amount of eccentricity between the member that supports and fixes the outer ring and the member that supports and fixes the inner ring. Further, the solid line in FIG. 2 shows the life of the structure of the present invention shown in FIG. 1, and the broken line shows the life of the conventional structure shown in FIG. The life ratio was set to 1 when the eccentricity was 0.3 mm in the conventional structure, and was shown in a proportional relationship therewith. The experimental conditions were as follows.
Using automatic fluid (ATF) at 10 ° C,
Thrust load is 0.2-0.4C and rotation speed is 350
0 to 5000 rpm. As is clear from FIG. 2 showing the results of such an experiment, the thrust roller bearing 1c of the present invention
According to this, especially when the amount of eccentricity is large, a long life extension effect can be obtained as compared with the conventional structure.

On the other hand, individual values of the width W ₁₉ of width W ₁₈ and the inner diameter side bearing in the gap 19 of the outer diameter side bearing the gap 18 is not so large. Accordingly, the outer engaging portion 11 formed on the inner peripheral edge of the inner ring 5 is provided with the outer engaging portion 11 which is bent inward in the diameter direction at the distal end edge of the outer flange 7 formed on the outer peripheral edge of the outer ring 4. By forming the inner locking portions 12 bent outward in the direction, the separation between the retainer 3 and the outer ring 4 and the inner ring 5 can be prevented.

Next, FIG. 3 shows a second example of the embodiment of the present invention, which also corresponds to claim 1. In the case of this example, the inner ring 5 constituting the thrust roller bearing 1c is fitted to the shaft 16 without looseness, and the outer ring 4 is abutted against the mating member 24. The structure and operation of the thrust roller bearing 1c are the same as those of the first example except that the structure of the mounting portion of the thrust roller bearing 1c is different.
A duplicate description will be omitted.

FIG. 4 shows a third embodiment of the present invention corresponding to claim 2. In the case of this example, the outer ring 4 is loosely fitted in the support recess 25 formed in the casing 13. The casing 13 and the outer ring 4
And the inner ring 5 and the retainer 3 are arranged concentrically with each other,
In addition to providing the outer-diameter-side bearing inner gap 18 and the inner-diameter-side bearing inner gap 19 inside the thrust roller bearing 1c constituted by the outer ring 4, the inner ring 5, and the retainer 3 as in the first and second examples described above, Outer flange 7 formed on the outer peripheral edge of outer ring 4
Of between the outer surface and the inner peripheral surface of the support recess 25, provided with a gap 26 assembled with a width dimension consisting W _26.

In the case of the present embodiment, the width W ₁₈ of the outer diameter side bearing inner gap ₁₈ and the inner diameter side bearing inner gap 19
The total width (= 2W _{18) obtained by} adding the width W ₁₉ of the above and the width W ₂₆ of the assembling clearance 26 in the diameter direction.
1/2 of + 2W ₁₉ + 2W ₂₆ ) (= W ₁₈ + W ₁₉ + W ₂₆ )
Is larger than the eccentricity δ between the casing 13 and the mating member 24 and {(W ₁₈ + W ₁₉ + W ₂₆ )> δ}. Also in the case of this example, the eccentricity existing between the casing 13 and the mating member 24 is prevented while preventing the cage 3 from being separated from the outer ring 4 and the inner ring 5 without using extra parts. Can be absorbed. Particularly, in the case of this example, the width dimensions W ₁₈ , W _{18 of} the outer diameter side bearing inner gap 18 and the inner diameter side bearing inner gap 19 are described.
₁₉ is made smaller than that of the first and second examples described above, so that the cage 3 can be reliably prevented from being separated from the outer ring 4 and the inner ring 5, and a larger eccentricity δ can be absorbed. Other configurations and operations are the same as those of the above-described first and second examples. Therefore, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

Next, FIG. 5 shows a fourth embodiment of the present invention, also corresponding to claim 2. In the case of this example, the inner ring 5 constituting the thrust roller bearing 1c is loosely fitted to the shaft 16 and the outer ring 4 is abutted against the mating member 24. That is, in the case of this example, the assembling gap 26 having a width dimension of W ₂₆ is provided between the inner peripheral surface of the inner flange 9 and the outer peripheral surface of the shaft 16. Thrust roller bearing 1
The structure and operation other than the point that the structure of the mounting part of c is different are:
Since this is the same as in the case of the above-described third example, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

Next, FIG. 6 shows a fifth embodiment of the present invention corresponding to claim 3. The thrust roller bearing 1d used in this example includes a plurality of rollers 2 arranged in a radial direction, a retainer 3 made of a whole ring shape and holding the plurality of rollers 2 so as to roll freely, and a ring shape. And an outer race 4 having a cylindrical outer flange 7 on the outer peripheral edge. The inner ring 5 (see FIG. 1,
3, 4, 5) are not provided. Accordingly, the rollers 2 abut the outer race 6 and directly abut the end surfaces of the mating members (not shown).

In the case of this example, such a thrust roller bearing 1
d, the outer race 4 is connected to the support recess 25 of the casing 13.
It fits inside without rattling. Then, in a state where the outer ring 4 and the cage 3 are arranged concentrically with each other, between the outer peripheral surface of the cage 3 and the inner peripheral surface of the outer flange 7,
An outer-diameter-side bearing inner gap 18 having a width dimension of W ₁₈ is provided. Then, 1/2 of the total gap (= 2W ₁₈ ) obtained by adding all the gaps 18 in the outer diameter side bearing in the diameter direction.
(= W ₁₈ ) is larger than the eccentricity δ between the casing 13 and the mating member (W ₁₈ > δ). Also in the case of this example, the eccentricity existing between the casing 13 and the mating member can be absorbed while preventing separation of the retainer 3 and the outer ring 4 without using extra parts.

Next, FIG. 7 shows a sixth embodiment of the present invention, which also corresponds to claim 3. In the case of this example, the thrust roller bearing 1e is
It comprises a retainer 3 which holds the plurality of rollers 2 so as to roll freely, and an inner ring 5 having a circular inner race part 8 and a cylindrical inner flange 9 at the inner peripheral edge. Outer ring 4
(FIGS. 1, 3, 4, 5, and 6) are not provided. Therefore, the roller 2 abuts on the inner race 8 and directly abuts the end surface of the mating member (not shown).

In the case of this example, such a thrust roller bearing 1
The inner ring 5 constituting e is fitted onto the shaft 16 without play. Then, in a state where the inner ring 5 and the retainer 3 are arranged concentrically with each other, an inner diameter side having a width dimension of W ₁₉ is provided between an inner peripheral surface of the retainer 3 and an outer peripheral surface of the inner flange 9. A bearing internal gap 19 is provided. A half (= W ₁₉ ) of the total gap (= 2W ₁₉ ) obtained by adding all the gaps 19 in the inner diameter side bearing in the diametric direction is set to be smaller than the eccentricity δ between the shaft 16 and the mating member. It is large (W ₁₉ > δ). In the case of this embodiment as well, the eccentricity existing between the shaft 16 and the mating member can be absorbed while preventing separation of the retainer 3 and the inner ring 5 without using extra parts.

Next, FIG. 8 shows a seventh embodiment of the present invention corresponding to claim 4. In the case of this example, the outer ring 4 constituting the thrust roller bearing 1d is
3 is loosely fitted in the support recess 25 formed therein. Then, in a state where the casing 13, the outer ring 4, and the retainer 3 are arranged concentrically with each other, an outer ring similar to the sixth example described above is provided inside the thrust roller bearing 1d formed by the outer ring 4 and the retainer 3. In addition to providing the radial bearing inner gap 18, an assembling gap 26 having a width dimension of W ₂₆ is provided between the outer peripheral surface of the outer flange 7 formed on the outer peripheral edge of the outer ring 4 and the inner peripheral surface of the support recess 25. Provide.

[0035] Then, in the case of this example, the outer width dimension W ₁₈ in diameter bearing the gap 18, the assembled all plus combined total gap over a width W ₂₆ of the gap 26 in the diameter direction ( = 2W ₁₈ + 2W ₂₆ ) (= W ₁₈ + W ₂₆ ) is larger than the eccentricity δ between the casing 13 and the counterpart member 24, and {(W ₁₈ + W ₂₆ )> δ}. Also in the case of this example, the eccentricity existing between the casing 13 and the mating member can be absorbed while preventing separation of the retainer 3 and the outer ring 4 without using extra parts. In particular, in the case of this example, the width dimension W ₁₈ of the outer diameter side bearing inner gap 18 is
It is possible to absorb a larger amount of eccentricity δ while making sure that the retainer 3 and the outer ring 4 are prevented from being separated from each other by making it smaller than the case of the fifth example described above. Other configurations and operations are the same as those of the above-described fifth example. Therefore, the same parts are denoted by the same reference numerals, and overlapping description will be omitted.

Next, FIG. 9 shows an eighth embodiment of the present invention, which also corresponds to claim 4. In the case of this example, the inner ring 5 constituting the thrust roller bearing 1e is loosely fitted to the shaft 16 and is fitted to the inner circumferential surface of the inner flange 9 formed on the inner circumferential edge of the inner ring 5 and the outer circumferential surface of the shaft 16. between the outer peripheral surface of the formed convex portion 27 is provided with a gap 26 assembled with a width W _26. And the clearance 1 in the inner diameter side bearing
The width W ₁₉ of 9, the width W ₂₆ of the assembly gaps 26
And the total clearance (= 2W)
₁₉ + 2W ₂₆ ) (= W ₁₉ + W ₂₆ )
Greater than the amount of eccentricity δ between the member and the mating member ｛(W ₁₉ + W ₂₆ )
> Δ｝. Other structures and operations are the same as those of the above-described seventh example. Therefore, the same reference numerals are given to the same parts, and the overlapping description will be omitted.

Next, FIG. 10 shows a ninth embodiment of the present invention corresponding to claim 5. In the case of this example, the thrust roller bearing 1f is composed of a plurality of rollers 2 arranged in a radial direction and a retainer 3 which is formed in a ring shape as a whole and holds the plurality of rollers 2 in a freely rolling manner. Make up.
The outer ring 4 and the inner ring 5 as in the respective examples described above are omitted. Then, the retainer 3 is connected to the casing 1 which is one of the members.
3 is loosely fitted in the support recess 25 provided therein. The rolling surfaces of the plurality of rollers 2 abut on the inner surface of the support recess 25 and the end surface of the mating member 24. In the case of this example, with the retainer 3 and the casing 13 arranged concentrically with each other, the outer peripheral surface of the retainer 3 and the inner peripheral surface of the support recess 25 which is a cylindrical surface are provided. , Width dimension is W ₂₆
Is provided. Then, 1/2 (= W ₂₆ ) of the total gap (= 2W ₂₆ ) obtained by adding all the width dimensions W ₂₆ of the assembling gap 26 in the diameter direction.
Is larger than the eccentricity δ between the casing 13 and the counterpart member 24 (W ₂₆ > δ). In this case as well, the eccentricity existing between the casing 13 and the mating member 24 can be absorbed while preventing separation of the retainer 3 and the outer ring 4 without using extra parts.

Next, FIG. 11 shows a tenth embodiment of the present invention, also corresponding to claim 5. In the case of this example, the cage 3 forming the thrust roller bearing 1f
The externally fitted loosely to the shaft 16, between the inner peripheral surface of the retainer 3 and the outer peripheral surface of the convex portion 27 formed on the outer peripheral surface of the shaft 16, provided with a gap 26 assembled with a width W ₂₆ I have. Then, 1/2 (=) of the total gap (= 2W ₂₆ ) obtained by adding the width dimension W ₂₆ of the assembling gap 26 in the diametric direction.
W ₂₆ ) is larger than the eccentricity δ between the shaft 16 and the counterpart member 24 (W ₂₆ > δ). Other structures and operations are the same as those in the ninth example described above, and therefore, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

[0039]

Since the thrust roller bearing of the present invention is constructed and operates as described above, it is possible to ensure the durability of the thrust roller bearing which receives a thrust load between members which rotate relatively in an eccentric state. Furthermore, without increasing the dimensional accuracy and assembling accuracy of the components in particular, the interference between the outer ring and the inner ring, or the casing or shaft and the retainer is prevented,
The cage can be prevented from being damaged. Further, the manufacturing operation and the assembling operation are not troublesome. Therefore, a highly reliable and durable rotating support can be obtained at low cost.

[Brief description of the drawings]

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

FIG. 2 is a diagram showing the results of an experiment performed to confirm the effects of the present invention.

FIG. 3 is a partial sectional view showing a second example of the embodiment of the present invention.

FIG. 4 is a partial cross-sectional view showing the third example.

FIG. 5 is a partial sectional view showing the fourth example.

FIG. 6 is a partial sectional view showing the fifth example.

FIG. 7 is a partial sectional view showing the sixth example.

FIG. 8 is a partial sectional view showing the seventh example.

FIG. 9 is a partial sectional view showing the eighth example.

FIG. 10 is a partial sectional view showing the ninth example.

FIG. 11 is a partial sectional view showing the tenth example.

FIG. 12 is a partial sectional view showing a first example of a conventional thrust roller bearing.

FIG. 13 is a partial sectional view showing the second example.

FIG. 14 is a partial cross-sectional view showing the third example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a-1f 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 engaging part 12 Inner engaging part 13 Casing 14 Holding part 15 steps Part 16 Shaft 17 Stepped part 18 Outer diameter side bearing inner gap 19 Inner diameter side bearing inner gap 20 Outer diameter side elastic ring 21 Inner diameter side elastic ring 22 Locking ring 23 Ring part 24 Mating member 25 Support recess 26 Assembly gap 27 Projection

Claims (5)

[Claims] 1. A plurality of rollers arranged in a radial direction, a retainer made of a whole ring shape and holding the plurality of rollers in a freely rolling manner, a ring-shaped outer ring race portion, and an outer ring race portion , An outer ring comprising a cylindrical outer flange formed all around the outer peripheral edge of the outer ring, an annular inner race part, and an inner flange formed all around the inner peripheral edge of the inner race part. And an inner ring consisting of: the outer race part and the inner race part sandwiching the plurality of rollers,
A pair of members that rotate the outer ring and the inner ring relatively to each other,
In a thrust roller bearing used in a state in which displacement in the radial direction with respect to the member is prevented, the outer ring, the inner ring, and the cage are arranged concentrically with each other, and the outer peripheral surface of the cage is The outer-diameter bearing inner gap between the inner flange of the outer flange and the outer-diameter bearing inner gap between the inner peripheral surface of the cage and the outer peripheral surface of the inner flange have substantially the same width. An inner-diameter-side bearing inner gap is provided, and the outer-diameter-side bearing inner gap and the inner-diameter-side bearing inner gap are all added up in the diametric direction.
2. A thrust roller bearing, wherein 2 is larger than the eccentricity of a member supporting the outer ring and a member supporting the inner ring. 2. A plurality of rollers arranged in a radial direction, a retainer made entirely in a ring shape and holding the plurality of rollers so as to roll freely, a ring-shaped outer ring race portion, and the outer ring race portion , An outer ring comprising a cylindrical outer flange formed all around the outer peripheral edge of the outer ring, an annular inner race part, and an inner flange formed all around the inner peripheral edge of the inner race part. And an inner ring consisting of: the outer race part and the inner race part sandwiching the plurality of rollers,
In a thrust roller bearing used in a state where the outer ring and the inner ring are assembled to a pair of members that rotate relative to each other,
A flange formed on a peripheral edge of at least one of the outer ring and the inner ring is loosely fitted to a member to which the bearing ring is to be assembled, and this member, the outer ring, the inner ring, and the retainer are In a state of being arranged concentrically with each other, an outer diameter side bearing inner gap between the outer peripheral surface of the retainer and the inner peripheral surface of the outer flange is formed between the inner peripheral surface of the retainer and the outer peripheral surface of the inner flange. In the meantime, an inner-diameter-side bearing gap having substantially the same width as the outer-diameter-side bearing inner gap is formed between the flange formed on the peripheral edge of the at least one race and the partial peripheral surface of a member to which the race is to be assembled. And a member for supporting the outer ring, and a half of a total clearance obtained by adding the outer diameter side bearing inner clearance, the inner diameter side bearing inner clearance, and the assembling clearance in the diametrical direction. Support the inner ring Thrust roller bearing, characterized in that is larger than the eccentricity of the wood. 3. A plurality of rollers arranged in a radial direction, a retainer made in a ring shape as a whole and holding the plurality of rollers in a freely rolling manner, and a track ring having a ring-shaped race portion; A cylindrical flange formed on the peripheral edge of the race, and a thrust race provided on the other member which rotates relative to the one member which is supported and fixed in a state where displacement of the race in the radial direction is prevented. In a thrust roller bearing used in a state in which the plurality of rollers are sandwiched between a surface and the race portion, in a state where the race and the cage are arranged concentrically with each other, the circumferential surface of the cage is A gap in the bearing is provided between the bearing and the peripheral surface of the flange, and の of a total gap obtained by adding all the gaps in the bearing in the diametric direction is:
A thrust roller bearing wherein the amount of eccentricity between the one member and the other member is made larger. 4. A plurality of rollers arranged in a radial direction, a retainer made into a whole ring shape and holding the plurality of rollers so as to roll freely, and a track ring having a ring-shaped race portion; A cylindrical flange formed on a peripheral portion of the race, and a plurality of races formed between a thrust race surface provided on the other member that rotates relative to one member supporting the race and the race portion; In a thrust roller bearing used in a state in which the rollers are sandwiched, in a state in which the bearing ring, the retainer and one member are concentrically arranged, one of the inner and outer peripheral surfaces of the retainer is provided. A bearing internal clearance is provided between the peripheral surface and one of the peripheral surfaces of the flange, and an assembling clearance is provided between the flange and a partial peripheral surface of the one member, respectively. And added all over the diameter direction A thrust roller bearing, wherein a half of a total clearance is larger than an eccentric amount of the one member and the other member. 5. A plurality of rollers arranged in a radial direction, and a retainer which is formed in a ring shape as a whole and holds the plurality of rollers in a freely rotatable manner. A cylindrical surface which holds the plurality of rollers between the provided thrust raceway surfaces and forms one of the inner and outer peripheral surfaces of the cage on one of the pair of members. In a thrust roller bearing used in a state of being opposed to the above, in a state where the retainer and one member are concentrically arranged, one of the inner and outer peripheral surfaces of the retainer is While providing an assembling gap between the cylindrical surface and
A thrust roller bearing wherein a half of a total gap obtained by adding all of the assembling gaps in the diameter direction is larger than an eccentric amount of the pair of members.