JP2005337447A - Thrust roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To securely prevent members 3 to 5 from being separated from each other even if the retainer 3 and the inner ring 5 are radially displaced relative to an outer ring 4a when no thrust load is applied thereto. <P>SOLUTION: This thrust roller bearing is formed by disposing outer locking parts 13 and 13 and inner locking parts 14 and 14 at equal intervals in the circumferential direction. The total number of the outer locking parts 13 and 13 is n1 and the heights thereof are h<SB>1</SB>. The total number of the inner locking parts 14 and 14 is n<SB>2</SB>and the heights thereof are h<SB>2</SB>. The width of an outer diameter side clearance 20 is c1 and the width of an inner diameter side clearance 21 is c<SB>2</SB>when outer side flange parts 8, 8a, and 8b and the retainer 3 are disposed concentrically to each other. Then the thrust roller bearing is so formed that the requirements of h<SB>1</SB><c<SB>1</SB>, h<SB>2</SB><c<SB>2</SB>, n<SB>1</SB>>2.1 (h<SB>1</SB>/c<SB>1</SB>)<SP>-0.52</SP>, and n<SB>2</SB>> 2.1 (h<SB>2</SB>/c<SB>2</SB>)<SP>-0.52</SP>are satisfied. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  A thrust roller bearing (including a needle bearing) according to the present invention is mounted on a rotating part of an automobile transmission, a torque converter or the like and used to support a thrust load.

  For example, as described in Patent Document 1 and the like, a thrust roller bearing 1 as shown in FIG. 6 is attached to a rotating portion of a transmission, a torque converter, etc., and a thrust load applied to a rotating shaft or the like is supported. ing. The thrust roller bearing 1 includes a plurality of rollers 2 arranged in a radial direction, a retainer 3 that is formed in an annular shape as a whole and holds the plurality of rollers 2 in a freely rolling manner, and the plurality of rollers 2. Is composed of an outer ring 4 and an inner ring 5 that are clamped from both sides in the axial direction (left-right direction in FIG. 6). Each of the outer ring 4 and the inner ring 5 is formed in an annular shape by a metal plate having sufficient hardness. Outer ring 4 includes an annular outer ring race portion 7 having an outer ring raceway 6 on one side surface (left side surface in FIG. 6), and projects from the outer peripheral edge of the outer ring race portion 7 toward the outer ring raceway 6 in the axial direction. And a cylindrical outer flange 8 formed over the entire circumference. On the other hand, the inner ring 5 protrudes toward the inner ring raceway 9 in the axial direction from an inner ring race portion 10 having an inner ring raceway 9 on one side surface (right side surface in FIG. 6) and an inner peripheral edge of the inner ring race portion 10. And an inner flange 11 formed over the entire circumference.

  The cage 3 is formed by combining in the middle a metal plate that is U-shaped in cross section and formed in a ring shape as a whole, and has the same number of pockets 12 as the rollers 2 arranged in the radial direction. Further, outer locking portions 13 projecting radially inward from the inner peripheral surface of the outer flange portion 8 are provided at a plurality of positions in the circumferential direction of the front end edge of the outer flange portion 8, and the respective portions are radially inward. It is formed by bending in the direction. On the other hand, inner locking portions 14 projecting radially outward from the outer peripheral surface of the inner collar portion 11 are provided at a plurality of locations in the circumferential direction of the tip edge of the inner collar portion 11, respectively. It is formed by bending it. Further, an outer diameter side gap 20 is formed between the outer peripheral surface of the cage 3 and the inner peripheral surface of the outer flange portion 8, and the inner peripheral surface of the retainer 3 and the outer peripheral surface of the inner flange portion 11. An inner diameter side gap 21 is interposed therebetween. Based on the presence of both the gaps 20 and 21, the cage 3, the outer ring 4 and the inner ring 5 can be freely slightly displaced in the radial direction.

  The thrust roller bearing 1 configured as described above has a thrust load in a state where the outer flange portion 8 formed on the outer peripheral edge of the outer ring 4 is fitted into the holding portion 16 of the casing 15 as shown in FIG. Attach it to the rotating part where this occurs. In this state, the outer race portion 7 constituting the outer ring 4 abuts on the step portion 17 of the holding portion 16, and the inner race portion 10 constituting the inner race 5 abuts on the step portion 19 of the shaft 18. As a result, the shaft 18 is rotatably supported with respect to the casing 15, and a thrust load acting between the members 18 and 15 is supported. The thrust roller bearing 1 is provided with the outer diameter side clearance 20 and the inner diameter side clearance 21 described above, so that even when the shaft 18 is eccentric with respect to the casing 15, the eccentricity is absorbed. The shaft 18 is allowed to rotate with respect to the casing 15.

  Further, when no thrust load is applied, which is realized by switching the clutch or the like, as shown in FIG. 7, there is a force that holds the rollers 2 and 2 between the outer ring raceway 6 and the inner ring raceway 9. Since the rollers 3 are released, the cage 3 that holds the rollers 2 and 2 and the inner ring 5 are displaced downward (in the radial direction) with respect to the outer ring 4 by the action of gravity. In such a case, if the cage 3, the outer ring 4, and the inner ring 5 are separated from each other, when the thrust load is applied again, there is a problem that the constituent members are not combined in a normal state. . On the other hand, in the case of the thrust roller bearing 1 described above, the outer locking portions 13 (see FIG. 6; not shown in FIG. 7) are held at the radially outer end of the cage 3. By engaging the inner locking portions 14 (see FIG. 6, not shown in FIG. 7) with respect to the axial direction at the radially inner end of the vessel 3, the cage 3, the outer ring 4, It is possible to prevent the inner ring 5 from being separated from each other.

By the way, in the case of the conventional structure as described above, as shown in FIG. 6, the height h ₁ of each outer locking portion 13 with respect to the inner peripheral surface of the outer flange 8 is set to the cage. 3 and the outer flange 8 are larger than the width c ₁ of the outer diameter side gap 20 in a state where they are arranged concentrically (h ₁ > c ₁ ). At the same time, the height h ₂ of each of the inner locking portions 14 with respect to the outer peripheral surface of the inner flange portion 11 is set so that the cage 3 and the inner flange portion 11 are arranged concentrically with each other. It is larger than the width c ₂ of the inner diameter side gap 21 (h ₂ > c ₂ ). Therefore, in the case of the conventional structure employing such a dimensional relationship, the outer locking portions 13 and the inner locking portions 14 are arranged at equal intervals (with good balance) in the circumferential direction. In this case, after the cage 3, the outer ring 4 and the inner ring 5 are assembled to each other, the outer and inner locking portions 13 and 14 need to be formed. The reason for this is that if the locking portions 13 and 14 are formed before the members 3 to 5 are assembled together, the locking portions 13 and 14 are in the way, and the members 3 to 5 are This is because they may not be able to be assembled together. Even if each part is assembled while being elastically deformed, the assembling work becomes troublesome.

However, in the case where the locking portions 13 and 14 are formed after the members 3 to 5 are assembled together as described above, the forming operation becomes troublesome as compared to the case where the locking portions 13 and 14 are formed before the assembly. Cost increases. Further, when the outer and inner locking portions 13 and 14 are bent at the distal ends of the outer and inner flange portions 8 and 11, the heights h ₁ and h of the locking portions 13 and 14 are formed. _{As 2} is larger, the shape of the surrounding portions of the locking portions 13 and 14 is more likely to be distorted, and as a result, the roundness of the flanges 8 and 11 is likely to deteriorate.

In contrast, the heights h ₁ and h ₂ of the locking portions 13 and 14 are smaller than the widths c ₁ and c _{2 of the} gaps 20 and 21 (h ₁ <c ₁ , h ₂ <c _2). Then, even when the respective locking portions 13 and 14 are formed before the respective members 3 to 5 are assembled with each other, the respective members 3 to 3 are not obstructed by the respective locking portions 13 and 14. 5 can be assembled together. For this reason, manufacturing cost can be reduced. Further, the roundness of each of the flange portions 8 and 11 can be satisfactorily maintained as much as the heights h ₁ and h ₂ of the respective locking portions 13 and 14 are reduced.

However, when the dimensional relationship as described above (h ₁ <c ₁ , h ₂ <c ₂ ) is adopted, these locking portions 13, 14 are not considered without considering the total number of the locking portions 13, 14. If the heights h ₁ and h ₂ are simply reduced, in some cases, the outer and inner locking portions 13 and 14 are disposed at both radial ends of the retainer 3 in the state shown in FIG. May not be able to engage with each other in the axial direction.

  That is, as schematically shown in FIG. 8A, the total number n of the locking portions (in the illustrated example, the outer locking portions 13, 13) is large, and the two locking portions 13 adjacent in the circumferential direction are large. , 13 is narrow, the radial ends of the cage 3 (in the illustrated example, the radial outer ends) even if the heights of the locking portions 13 and 13 are reduced to some extent. The engaging portions 13 and 13 can be engaged with each other in the axial direction. On the other hand, as schematically shown in FIG. 8B, the total number n of the locking portions (in the illustrated example, the outer locking portions 13 and 13) is small, and two locking portions adjacent in the circumferential direction are provided. When the interval between the portions 13 and 13 is wide, even if the height of each of the locking portions 13 and 13 is the same as that in the case (A), the radial end of the retainer 3 (not shown) In the example, the locking portions 13 and 13 may not be engaged with each other in the axial direction with respect to the radially outer end portion. And when it becomes impossible to engage in this way, it is possible to separate the cage 3, the outer ring 4 and the inner ring 5 in a state where the thrust load is lost after assembling to the rotation support part. It cannot be prevented. Therefore, it is desired to realize a means that can prevent the occurrence of such inconvenience.

JP 2000-266043 A

  In view of the circumstances as described above, the thrust roller bearing of the present invention has a structure in which the heights of the outer and inner locking portions are made smaller than the widths of the outer diameter side and inner diameter side gaps, and the thrust load is not applied. At times, the invention has been invented to realize a structure that can reliably prevent the cage, inner ring and outer ring from separating.

The thrust roller bearing of the present invention includes an outer ring, an inner ring, a plurality of rollers, and a cage.
Of these, the outer ring is a cylindrical outer ring race part having an outer ring raceway on one side, and a cylindrical shape formed over the entire circumference in a state of projecting from the outer peripheral edge of the outer ring race part toward the outer ring raceway side in the axial direction. And the outer buttock.
The inner ring includes an annular inner ring race portion having an inner ring raceway on one side surface, and an inner ring formed over the entire circumference so as to protrude from the inner peripheral edge of the inner ring race portion toward the inner ring raceway side in the axial direction. It consists of parts.
The plurality of rollers are arranged in a radial direction between the outer ring raceway and the inner ring raceway.
Further, the cage is entirely formed in an annular shape, and holds the rollers in a rollable manner. Furthermore, outer locking portions that protrude radially inward from the inner peripheral surface of the outer collar at a plurality of locations in the circumferential direction of the distal edge of the outer collar are provided at the circumference of the tip edge of the inner collar. Inner locking portions that protrude radially outward from the outer peripheral surface of the inner flange portion are formed at a plurality of locations in the direction (for example, by bending the portion in the diametrical direction).

In particular, in the thrust roller bearing of the present invention, the outer locking portions and the inner locking portions are arranged at equal intervals in the circumferential direction. At the same time, the total number of the outer locking portions is n ₁ , the height of the outer locking portions is h ₁ , and the outer flange and the cage are arranged concentrically with each other. The width in the radial direction of the outer diameter side clearance existing between the inner peripheral surface of the outer flange and the outer peripheral surface of the cage is c _1, and the total number of the inner locking portions is n _2. The inner diameter that exists between the outer peripheral surface of these inner flanges and the inner peripheral surface of the cage in a state where the height of the stopper is h ₂ and the inner flange and the cage are arranged concentrically with each other When the width in the radial direction of the side gap is c ₂ and the two dimensionless heights H ₁ and H ₂ are set as H ₁ = h ₁ / c ₁ and H ₂ = h ₂ / c ₂ , respectively. , H ₁ <c ₁ (H ₁ <1), h ₂ <c ₂ (H ₂ <1), n ₁ > 2.1H ₁ ^-0.52 and n ₂ > 2.1H ₂ ^-0.52 Meet.

As described above, in the case of the thrust roller bearing of the present invention, the height h ₁ of the outer locking portion is set to the width c of the outer diameter side clearance in a state where the outer flange portion and the cage are arranged concentrically with each other. _It is smaller than ₁ (h ₁ <c ₁ ). At the same time, the height h ₂ of the inner locking portion is made smaller than the width c ₂ of the inner diameter side clearance in the state where the inner flange portion and the cage are arranged concentrically (h ₂ <c ₂ ). . For this reason, even when the outer and inner locking portions are formed before the cage, outer ring and inner ring are assembled together, the outer and inner locking portions are not obstructed by the outer and inner locking portions. And the inner ring can be assembled together. Therefore, the manufacturing cost can be reduced. Further, the distortion generated in the peripheral portion of each of the engaging portions is suppressed by bending each of the engaging portions as much as the heights h ₁ and h ₂ of the outer and inner engaging portions are reduced. I can do things. For this reason, the roundness of each said inner side and outer side collar part can be hold | maintained favorably.

As described above, the thrust roller bearing of the present invention satisfies the conditions of n ₁ > 2.1H ₁ ^-0.52 and n ₂ > 2.1H ₂ ^-0.52 . For this reason, when no thrust load is applied, the cage and the inner ring are completely displaced in the radial direction with respect to the outer ring, and at least one outer locking portion with respect to the radially outer end of the cage. Similarly, at least one inner locking portion can be reliably engaged with the radially inner end portion in the axial direction. Hereinafter, this reason will be described with reference to FIGS.

FIG. 1 shows an inner member {retainer 3 (or inner flange 11) having a cylindrical outer peripheral surface inside an outer member {outer flange 8 (or retainer 3)} having a cylindrical inner peripheral surface. } Is a schematic diagram showing a state in which it is completely displaced in the radial direction (downward in FIG. 4). In FIG. 1, point O is the central axis of the inner member 3 (11), and point P is the outer peripheral surface of the inner member 3 (11) and the inner peripheral surface of the outer member 8 (3). Each of the contact points is represented. In the state shown in FIG. 1, a gap existing between the inner peripheral surface of the outer member 8 (3) and the outer peripheral surface of the inner member 3 (11) {the outer diameter side clearance 20 (or the inner diameter side clearance 21). )} In the radial direction with respect to the central axis O is not the same in the circumferential direction. The width δ can be expressed by the following equation (1) as a function of the angle θ with respect to the line segment OP.
δ = c {1 + cos (π−θ)} −−−−−− (1)
In the right side of the equation (1), c represents the radial direction of the gap 20 (21) in a state where the outer member 8 (3) and the inner member 3 (11) are arranged concentrically with each other. It represents the width c ₁ (c ₂ ).

On the other hand, in the case of the present invention, a plurality of outer locking portions 13 and 13 (only a part thereof is shown in FIG. 1) provided on the outer flange 8 and a plurality of provided on the inner flange 11. The inner locking portions (not shown) are arranged at equal intervals in the circumferential direction. The positions of these locking portions (outer locking portions 13 and 13 or inner locking portions) in the circumferential direction are variously changed by the rotation of the outer flange portion 8 or the inner flange portion 11. However, in the case of the present invention, the following can be said regardless of the total number n (n ₁ or n ₂ ) of the respective locking portions (the outer locking portions 13, 13 or the inner locking portions). That is, as shown in FIG. 1, when two circumferentially adjacent locking portions (outer locking portions 13, 13 or inner locking portions) are positioned symmetrically on both sides of the point P, The possibility that the two locking portions (the outer locking portions 13 and 13 or the inner locking portion) and the radial end portion of the cage 3 are not engaged is greatest. In this case, the circumferential position of the two locking portions (the outer locking portions 13, 13 or the inner locking portion) {the point O and the two locking portions (the outer locking portions 13, 13, or The angle formed between each line segment (in FIG. 1, only the left line segment is shown) and the line segment OP, which are connected to the inner locking portion, can be expressed by the following equation (2).
α = π / n ------ (2)

Then, the height h (h ₁ or h ₂₎ of the engaging portion (the outer locking portion 13, 13 or the inner locking portion), the two locking portions (the outer locking portion 13, 13 or If the width 20 of the gap 20 (21) is smaller (h <δ) at the position (θ = α) where the inner locking portion is present (h <δ), the two locking portions (outer locking portions) 13, 13 or the inner locking portion) and the radial end portion of the cage 3 cannot be engaged in the axial direction. Accordingly, each of these engagements required for engaging the two engagement portions (outer engagement portions 13, 13 or the inner engagement portion) and the radial end portion of the retainer 3 in the axial direction. The minimum value (critical value) of the height h (h ₁ or h ₂ ) of the stop portion (outer engagement portion 13, 13 or inner engagement portion) can be expressed by the following equation (3).
h = c {1 + cos (π−α)} −−−−−− (3)
Here, the dimensionless height H (H ₁ or H ₂ ) is defined as in the following equation (4).
H = h / c ------ (4)
As a result, the following expression (5) is obtained from the above expressions (3) and (4).
H = 1 + cos (π-α) ------ (5)
Here, in order to simply describe the relationship of the above equation (5), the relationship is approximated by the following equation (6) in which n (n ₁ or n ₂ ) is represented by a function of H.
n = 2.1H ^-0.52 ------ (6)
A curve C in FIG. 2 represents a curve that can be expressed by the equation (6) (approximate equation).

The above equation (6) (curve C in FIG. 2) indicates that the two locking portions (the outer locking portions 13, 13 or the inner locking portion) and the radial end of the cage 3 are in the axial direction. The critical value of the total number n (n ₁ or n ₂ ) of the respective locking portions (outer locking portions 13, 13 or inner locking portions) for enabling engagement is shown. Accordingly, if the total number n (n ₁ or n ₂ ) is greater than or equal to the value expressed by the above formula (6), that is, the following formula (7) is satisfied, the two locking portions ( The outer locking portions 13 and 13 or the inner locking portion) and the radial end of the cage 3 can be engaged with each other in the axial direction.
n> 2.1H ^-0.52 ------ (7)
In the graph of FIG. 2, the region above the curve C including the curve C is a region satisfying the relationship (7).
Further, as long as the relationship of the expression (7) is satisfied as described above, at least one locking portion (the outer locking portion 13) regardless of the circumferential phase of the outer flange portion 8 or the inner flange portion 11. Or the inner locking portion) can be engaged with the radial end of the cage 3 in the axial direction.

In the case of the present invention, as described above, the relationship (n ₁ > 2.1H ₁ ^-0.52 and n ₂ > 2.1H ₂ ^-0.52 ). Therefore, as described above, when no thrust load is applied, at least one of the cage and the inner ring is radially displaced with respect to the outer ring with respect to the radially outer end of the cage. Similarly, at least one inner locking portion can be reliably engaged with the radially inner end portion in the axial direction. Therefore, it is possible to reliably prevent the cage, the outer ring, and the inner ring from separating when the thrust load is not applied.

  FIG. 3 shows a first embodiment of the present invention. The feature of this embodiment is that the outer locking portions 13 and 13 are formed at the tip of the outer flange 8a constituting the outer ring 4a, and the inner engagement formed at the tip of the inner flange 11a constituting the inner ring 5a. It exists in the point which regulates the arrangement | positioning method, the total number, and height regarding the circumferential direction with the stop parts 14 and 14. FIG. Since the structure and operation of other parts are the same as those of the conventional structure shown in FIGS. 6 to 7 described above, overlapping illustrations and explanations are omitted or simplified, and hereinafter, the characteristic parts of this embodiment will be mainly described. explain.

In the case of the present embodiment, the total number n ₁ of the outer locking portions 13 and 13 is 6 (n ₁ = 6), and the total number n ₂ of the inner locking portions 14 and 14 is 5 (n ₂ = 5). At the same time, the outer locking portions 13 and 13 and the inner locking portions 14 and 14 are arranged at equal intervals in the circumferential direction. Further, the height h ₁ of each of the outer locking portions 13 and 13 is determined from the width c _{1 in} the radial direction of the outer diameter side gap 20 in a state where the outer flange portion 8a and the cage 3 are arranged concentrically with each other. Is also small (h ₁ <c ₁ ). Specifically, the dimensionless height H ₁ (= h ₁ / c ₁ ) is set to 0.2. Further, the height h ₂ of the inner locking portions 14, 14 is determined from the width c _{2 in} the radial direction of the inner diameter side gap 21 in a state where the inner flange portion 11 a and the cage 3 are arranged concentrically with each other. Is also small (h ₂ <c ₂ ). Specifically, the dimensionless height H ₂ (= h ₂ / c ₂ ) is set to 0.25. In FIG. 1, O ₁ indicates the central axis of the cage 3 and O ₂ indicates the central axis of the inner flange portion 11a.

Then, by performing the dimensional restrictions as described above, the condition of n ₁ > 2.1 (h ₁ / c ₁ ) ^−0.52 is satisfied, and n ₂ > 2.1 (h ₂ / c ₂ ) ^−0.52 The condition is satisfied. That is, in the case of the present embodiment as described above, n ₁ = 6 and 2.1 (h ₁ / c ₁ ) ^−0.52 is calculated to be 4.85, so that n ₁ > 2 .1 (h ₁ / c ₁ ) ^-0.52 is satisfied. Since n ₂ = 5 and 2.1 (h ₂ / c ₂ ) ^−0.52 is calculated to be 4.31, n ₂ > 2.1 (h ₂ / c ₂ ) ^−0.52 is ^satisfied . Meet the conditions.

In the case of the thrust roller bearing of the present embodiment configured as described above, the heights h ₁ and h ₂ of the outer and inner locking portions 13 and 14 are set to the outer diameter and inner diameter gaps 20 and 21, respectively. The widths c ₁ and c ₂ are smaller (h ₁ <c ₁ , h ₂ <c ₂ ). For this reason, even when the outer and inner locking portions 13 and 14 are formed before the cage 3, outer ring 4a and inner ring 5a are assembled together, the outer and inner locking portions 13 and 14 are obstructed. The cage 3, the outer ring 4a, and the inner ring 5a can be assembled to each other without any problems. Therefore, the manufacturing cost can be reduced. Further, the respective locking portions 13, 14 are formed by bending the locking portions 13, 14 as much as the heights h ₁ , h ₂ of the outer and inner locking portions 13, 14 are reduced. It is possible to suppress distortion generated in the peripheral portion of 14. For this reason, the roundness of the inner and outer flanges 8a and 11a can be favorably maintained.

Furthermore, in this embodiment, the conditions of n ₁ > 2.1H ₁ ^-0.52 and n ₂ > 2.1H ₂ ^-0.52 are satisfied. Therefore, as shown in the figure, when the thrust load is not applied, the radially outer end of the retainer 3 is in a state where the retainer 3 and the inner ring 5a are completely displaced in the radial direction with respect to the outer ring 4a. It is possible to reliably engage at least one outer locking portion 13 with respect to the portion and at least one inner locking portion 14 with respect to the radially inner end portion with respect to the axial direction. Therefore, it is possible to reliably prevent the cage 3, the outer ring 4a, and the inner ring 5a from separating when the thrust load is not applied.

4 to 5 show a second embodiment of the present invention. In the case of the first embodiment described above, the total number n ₁ of the outer locking portions 13 and 13 is six (n ₁ = 6), whereas in the case of the present embodiment, the outer locking portions 13 and 13 are set. The total number n ₁ is 9 (n ₁ = 9). Other specifications including the value of the dimensionless height H ₁ are the same as those in the first embodiment. In FIG. 5, the values of the total number n regarding the outer flanges 13 and 13 for both Example 1 and Example 2 are indicated by “Δ” marks, respectively.

In the case of the thrust roller bearing of the present embodiment as described above, the total number n ₁ of the outer locking portions 13 and 13 is larger than that in the case of the first embodiment. In the state in which the cage 3 is completely displaced in the radial direction with respect to the outer flange portion 8b constituting the diameter, the number of the outer locking portions 13 and 13 that engage with the radially outer end portion of the cage 3 is set to the embodiment. The number can be larger than the case of 1 (up to 2 in the case of the above-described first embodiment, but up to 4 in the case of the present embodiment). Therefore, the effect of preventing the cage 3 and the outer ring 4b from being separated can be made larger than in the case of the first embodiment. The configuration and operation of the other parts are the same as in the case of the first embodiment.

  In carrying out the present invention, as described above, if the dimensionless height H of the locking portion is constant, the number n of the locking portions is increased to increase the cage, outer ring, and outer ring. The effect of preventing separation from the inner ring can be further increased.

BRIEF DESCRIPTION OF THE DRAWINGS Schematic which shows the state which the outer member and the inner member used for demonstrating the conditions which this invention should satisfy | fill with relative displacement to radial direction. The graph showing the relationship between the dimensionless height H and the total number n of a latching part which this invention should satisfy | fill. Sectional drawing which shows Example 1 of this invention. Sectional drawing which similarly shows Example 2. FIG. The figure which plotted the value regarding the outer side latching | locking part of Example 1 and Example 2 on the graph showing the relationship between the dimensionless height H and the number n of a latching | locking part. The fragmentary sectional view shown in the state which assembled | attached the conventional thrust roller bearing to the rotation part. Similarly, (A) is sectional drawing regarding the virtual plane orthogonal to an axial direction, and (B) is sectional drawing regarding the virtual plane containing a central axis shown in the state at the time of no load of a thrust load. The schematic diagram which shows the state (A) in which a holder | retainer and a latching | locking part engage, and the state (B) which does not engage.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Thrust roller bearing 2 Roller 3 Cage 4, 4a, 4b Outer ring 5, 5a, 5b Inner ring 6 Outer ring raceway 7 Outer ring race part 8, 8a, 8b Outer flange part 9 Inner ring raceway 10 Inner ring race part 11, 11a, 11b Inner collar Part 12 Pocket 13 Outer engaging part 14 Inner engaging part 15 Casing 16 Holding part 17 Step part 18 Shaft 19 Step part 20 Outer diameter side clearance 21 Inner diameter side clearance

Claims (1)

A ring-shaped outer ring race portion having an outer ring raceway on one side surface and a cylindrical outer collar portion formed over the entire circumference in a state protruding from the outer peripheral edge of the outer ring race portion toward the outer ring raceway in the axial direction. The outer ring comprises an annular inner ring race portion having an inner ring raceway on one side surface and an inner collar portion formed over the entire circumference in a state protruding from the inner peripheral edge of the inner ring race portion toward the inner ring raceway side in the axial direction. An inner ring, a plurality of rollers arranged in a radial direction between the outer ring raceway and the inner ring raceway, and a cage that is formed in a ring shape and holds these rollers in a freely rolling manner. The outer hooks projecting radially inward from the inner circumferential surface of the outer collar at a plurality of locations in the circumferential direction of the distal edge of the outer collar, Radially outward from the outer peripheral surface of this inner collar at the location In the thrust roller bearing in which the protruding inner locking portions are respectively formed, the outer locking portions and the inner locking portions are arranged at equal intervals in the circumferential direction. The total number of stop portions is n ₁ , the height of each outer locking portion is h _1, and the inner peripheral surfaces of these outer flange portions in a state where the outer flange portion and the cage are arranged concentrically with each other the width in the radial direction of the outer diameter side gap existing between the outer peripheral surface of the cage and c ₁ and the total number of the respective inner engagement portion and n _2, the height of each inner locking portion h ₂ , the width in the radial direction of the inner diameter side gap existing between the outer peripheral surface of the inner flange and the inner peripheral surface of the cage in a state where the inner flange and the cage are arranged concentrically with each other Is c ₂ , h ₁ <c ₁ , h ₂ <c ₂ , and n ₁ > 2.1 (h ₁ / c ₁ ) ⁻ A thrust roller bearing characterized in that ^0.52 and n ₂ > 2.1 (h ₂ / c ₂ ) ^−0.52 are satisfied.

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