JP5154084B2 - Thrust roller bearing and torque converter - Google Patents

Description

  The present invention relates to a thrust roller bearing, and more particularly to a thrust roller bearing used in an environment involving eccentric rotation such as a torque converter.

  A conventional thrust roller bearing 101 is described in, for example, Japanese Patent Application Laid-Open No. 2003-83339 (Patent Document 1). Referring to FIG. 15, a thrust roller bearing 101 described in the publication includes a plurality of rollers 102, a cage 103 that holds the plurality of rollers 102, and first and first rollers that clamp the rollers 102 from the thickness direction. Two race rings 104 and 105.

  The first race ring 104 has a raceway surface 104a in contact with the roller 102 on the wall surface on one side in the thickness direction of the annular member, a cylindrical flange 104b extending from the outer edge portion of the annular member to the raceway surface 104a side, A plurality of overhanging portions 104c that protrude radially inward from the tip of the flange portion 104b and hold the retainer 103 are provided.

  Similarly, the second race ring 105 includes a raceway surface 105a that contacts the roller 102 on a wall surface on one side in the thickness direction of the annular member, and a cylindrical flange extending from the inner edge of the annular member to the raceway surface 105a side. 105b and a plurality of projecting portions 105c that protrude radially outward from the tip of the flange portion 105b and hold the retainer 103.

  In this thrust roller bearing 101, the inner diameter dimension of the flange portion 104b is set larger than the outer diameter dimension of the cage 103, and a radial bearing internal clearance is provided between the cage 103 and the flange portion 104b. Thus, it is described that even when used in an environment with eccentric rotation such as a torque converter, heat generation and wear due to friction between the cage 103 and the flange 104b can be effectively prevented. .

  Here, the cage 103 and the first race ring 104 may be separated due to the provision of the bearing internal clearance. For example, there is a possibility of separation when the first and second track rings 104a and 105a are transported in a vertical state. Therefore, in the thrust roller bearing 101 described in the publication, the diameter of the circle connecting the tips of the overhang portions 104 c is made smaller than the outer diameter of the cage 103. Thereby, it is described that separation between the cage 103 and the first raceway ring 104 can be prevented. The same applies to the case where the cage 103 is incorporated in the second race ring 105.

Further, thrust roller bearings having the same configuration are disclosed in, for example, Japanese Patent Application Laid-Open No. 9-137824 (Patent Document 2), Japanese Patent Application Laid-Open No. 9-189325 (Patent Document 3), Japanese Patent Application Laid-Open No. 2000-266043 (Patent Document 4). ) And Japanese Patent Application Laid-Open No. 2003-254327 (Patent Document 5).
JP 2003-83339 A JP-A-9-137824 JP-A-9-189325 JP 2000-266043 A JP 2003-254327 A

  However, when the protruding amount of the overhanging portion 104c is increased, the assemblability of the thrust roller bearing 101 is deteriorated. Specifically, the cage 103 and the overhanging portion 104c must be greatly elastically deformed when getting over the overhanging portion 104c. This can also cause deformation of the cage 103 and damage to the overhanging portion 104c.

  As one method for solving this problem, for example, a carburizing treatment or the like is performed on the overhanging portion 104c so that the quenching effect is not exerted, or partial annealing is performed after quenching. However, by performing these processes, it becomes easy to incorporate the cage 103, but at the same time, the strength of the overhanging portion 104c decreases.

  As another method, it is conceivable to heat-treat the entire thrust roller bearing 101 after the roller 102 and the cage 103 are incorporated into the first raceway ring 104. However, the cage 103 and the raceway ring 104 may be deformed, which may cause rotation failure of the thrust roller bearing 101.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is a thrust roller bearing used in an environment involving eccentric rotation such as a torque converter, and the thrust which effectively prevents separation without impairing the assembling property of the cage and the raceway ring. It is to provide a roller bearing.

  Another object of the present invention is to provide a highly reliable torque converter by employing the thrust roller bearing as described above.

A thrust roller bearing according to the present invention includes a plurality of rollers, a raceway surface on which a cage for holding the plurality of rollers rolls, a cylindrical outer peripheral flange extending in an axial direction from an outer peripheral end of the raceway surface, and an outer peripheral flange An annular first race ring having a first claw portion that protrudes from the tip of the portion to the inner diameter side and restricts axial movement of the cage, a raceway surface on which the roller rolls, and an inner circumference of the raceway surface A second annular ring having a cylindrical inner circumferential flange extending in the axial direction from the end, and a second claw that protrudes from the tip of the inner circumferential collar to the outer diameter side and restricts axial movement of the cage. With a raceway. And the bearing which permits the eccentric rotation of the 1st raceway ring and the 2nd raceway ring between the outer periphery collar part and the outer edge part of a cage, and between an inner circumference collar part and the inner edge part of a cage. An internal gap is provided. Further, at least one of the first and second claw portions is an overhang portion formed by bending .

Further, the edge of the cage facing the overhanging portion is folded back in the radial direction and overlapped in the thickness direction of the cage, and by this folding, the first inclined portion is formed at the corner on the side facing the raceway surface. And a second inclined part having a relatively shorter radial length than the first inclined part are formed at the corner opposite to the thickness direction.

The thrust roller bearing configured as described above generates heat generated by contact between the cage and the raceway due to eccentric rotation by setting the bearing internal clearance between the raceway and the cage to be twice or more the eccentric amount of the support member. And wear can be effectively prevented. In addition, the first and second inclined portions function as guide surfaces when getting over the overhanging portion. Therefore, the radial length of the first inclined portion that functions as a guide surface during assembly of the cage and the bearing ring is increased, and the radial length of the second inclined portion that functions as a guide surface during disassembly is shortened. . Thereby, it is possible to obtain a thrust roller bearing that effectively prevents the separation without impairing the assembling property of the cage and the race.

And the 1st and 2nd inclination part is formed by folding the edge part of a holder | retainer so that it may fold in the radial direction, and overlapping in the thickness direction of a holder | retainer . According to the present invention, a curved surface (R-shaped) inclined portion is formed and the rigidity of the cage is improved. In addition, the inclined portion may be formed by chamfering the edge (including both “C chamfering” and “R chamfering”).

  Preferably, the cage is manufactured by using SPC or SCM as a starting material and performing any of soft nitriding, carburizing, or carbonitriding as the heat treatment. The first and second race rings are preferably manufactured through carburizing or carbonitriding using SPC or SCM as a starting material. As a result, it is possible to obtain the dimensional accuracy and mechanical properties required for the cage and the race.

Preferably, the contact angle θ ₁ between the first inclined portion and the overhang portion when the cage is incorporated in the race ring having the overhang portion satisfies θ ₁ ≧ 45 °.

More preferably, the contact angle θ ₂ between the second inclined portion and the overhang portion when the cage is separated from the bearing ring having the overhang portion satisfies θ ₂ ≦ 45 °.

The larger the contact angle between the cage and the overhang portion, the easier the cage gets over the overhang portion. On the other hand, the smaller the contact angle, the harder the cage gets over the overhang. Therefore, the contact angle theta ₁ between the first inclined portion and the overhang portion and 45 ° or more, by the contact angle theta ₂ between the second inclined portion and the overhang portion and 45 ° or less, embedded easily separated It is possible to obtain a thrust roller bearing that is difficult to perform.

  The torque converter according to the present invention includes an impeller connected to the input shaft, a turbine connected to the output shaft, a stator that directs working fluid from the turbine to the impeller, and between the turbine and the stator, and / or The thrust roller bearing according to any one of the above, which is disposed between an impeller and a stator. A highly reliable torque converter can be obtained by employing the thrust roller bearing having the above configuration as a bearing for supporting a turbine or an impeller with eccentric rotation.

  According to the present invention, the first inclined portion that functions as an insertion guide surface when the cage is incorporated into the raceway is enlarged, so that the assembling property between the cage and the raceway is not impaired and separation is effectively performed. Thus, it is possible to obtain a thrust roller bearing that is prevented. Moreover, a highly reliable torque converter can be obtained by adopting such a thrust roller bearing.

  With reference to FIGS. 1-8, the thrust roller bearing 11 which concerns on one Embodiment of this invention is demonstrated. 1 is an enlarged view of a portion P in FIG. 7, FIG. 2 is a view showing a thrust roller bearing 11, FIGS. 3 and 4 are a sectional view and a plan view of the first race ring 14, and FIGS. A sectional view and a plan view of the second race 15, and FIGS. 7 and 8 are a sectional view and a plan view of the cage 13.

  First, referring to FIG. 2, the thrust roller bearing 11 includes a plurality of rollers 12, a cage 13 that holds the plurality of rollers 12, and first and second race rings 14 and 15 that receive the cage 13. Is a trinary thrust roller bearing.

  Referring to FIGS. 3 and 4, the first track ring 14 is an annular member having a through hole 14 a penetrating in the thickness direction at the center. Further, a raceway surface 14b on which the roller 12 rolls on the wall surface on one side in the thickness direction, a cylindrical outer peripheral flange portion 14c extending toward the raceway surface 14b in the thickness direction on the outer edge portion of the annular member, and an outer peripheral flange portion 14c A plurality of projecting portions 14d as first claw portions projecting radially inward at the tip are included.

  When the thrust roller bearing 11 is assembled, the outer peripheral flange portion 14 c is positioned further outside the outer edge portion of the cage 13. The overhanging portion 14d protrudes radially inward from a plurality of locations on the outer peripheral flange portion 14c. The overhanging portion 14 d engages with the outer edge portion of the cage 13 to prevent the cage 13 from being separated from the first race ring 14. In addition, the overhang | projection part 14d in this embodiment is provided in eight places on the periphery of the outer periphery collar part 14c at equal intervals.

If the circles passing through the tips of the eight protruding portions 14d are O ₁ (indicated by a two-dot chain line in FIG. 4), the diameter of the circle O ₁ is stretched so as to be smaller than the outer diameter of the cage 13. The protruding amount of the protruding portion 14d is adjusted. Therefore, the cage 13 is incorporated into the first track ring 14 in a state where the outer edge portion of the cage 13 and the overhanging portion 14d are elastically deformed.

  Next, referring to FIG. 5 and FIG. 6, the second race ring 15 is an annular member having a through hole 15 a penetrating in the thickness direction at the center. And the raceway surface 15b where the roller 12 rolls on the wall surface on the one side in the thickness direction, the cylindrical inner peripheral flange portion 15c extending toward the raceway surface 15b side in the thickness direction on the inner edge portion of the annular member, and the inner peripheral flange portion A plurality of stakings 15d as second claws projecting radially outward are included at the tip of 15c.

  When the thrust roller bearing 11 is assembled, the inner peripheral flange portion 15 c is positioned further inside the inner edge portion of the cage 13. The staking 15d protrudes radially outward from a plurality of locations on the inner peripheral flange 15c. This staking 15 d is engaged with the inner edge of the cage 13 to prevent the cage 13 from being separated from the second race ring 15. In addition, the staking 15d in this embodiment is provided in four places on the circumference of the inner periphery collar part 15c at equal intervals.

If the circle passing through the tip of the four stakings 15d is O ₂ (indicated by a two-dot chain line in FIG. 6), the staking 15d is such that the diameter of the circle O ₂ is larger than the inner diameter of the cage 13. Adjust the amount of protrusion. Therefore, the cage 13 is incorporated into the second race 15 in a state where the inner edge of the cage 13 and the staking 15d are elastically deformed.

  The 1st and 2nd track rings 14 and 15 of the above-mentioned composition are manufactured by press processing, for example using SPC or SCM as a starting material. Furthermore, in order to obtain a predetermined mechanical property, a carburizing process or a carbonitriding process is performed as a heat treatment.

  The overhanging portion 14 d provided on the first raceway ring 14 and the staking 15 d provided on the second raceway ring 15 function as a claw portion that holds the cage 13. The overhanging portion 14d is formed by bending the distal end of the outer peripheral flange portion 14c radially inward by bending. Moreover, the overhang | projection part 14d has the capability to hold | maintain the holder | retainer 13 compared with staking 15d.

  Next, with reference to FIG. 7 and FIG. 8, the retainer 13 is an annular member having a through hole 13a penetrating in the thickness direction at the center. A plurality of pockets 13b for accommodating the rollers 12 are radially arranged on the wall surface. Further, referring to FIG. 1, the outer edge portion of the cage 13 is folded back inward in the radial direction, and first and second inclined portions 13 c and 13 d are formed at corner portions thereof.

  Each of the first and second inclined portions 13c and 13d is a curved surface that is curved with a predetermined curvature. The radial length A of the first inclined portion 13c is longer than the radial length B of the second inclined portion 13d (A> B). Referring to FIG. 2, when the retainer 13 is incorporated in the first raceway ring 14, the first inclined portion 13c is arranged to face the raceway surface 14b.

  The cage 13 having the above-described configuration is manufactured, for example, by pressing using SPC or SCM as a starting material. Further, in order to obtain a predetermined mechanical property, any of soft nitriding, carburizing or carbonitriding is performed as a heat treatment.

  Next, with reference to FIG. 9 and FIG. 10, a method for incorporating the cage 13 into the first race ring 14 will be described. FIG. 9 is a view showing a state in which the cage 13 is assembled into the first track ring 14, and FIG. 10 is an enlarged view of a portion Q in FIG.

  First, referring to FIG. 9, when the cage 13 is incorporated in the first raceway ring 14, a part of the outer edge of the cage 13 (the right side in FIG. 9) is submerged inside the overhanging portion 14 d, The outer edge portion of the cage 13 is brought into contact with the inner diameter surface of the flange portion 14c. At this time, on the other side (left side in FIG. 9), the outer edge portion of the cage 13 and the overhang portion 14d are caught and cannot be incorporated. Therefore, the cage 13 is incorporated into the first race ring 14 while the cage 13 and the overhanging portion 14d are elastically deformed.

  Referring to FIG. 10, in the Q part of FIG. 9, the first inclined part 13 c of the cage 13 and the corner part of the projecting part 14 d are in contact with each other. Here, the first inclined portion 13 c functions as an insertion guide surface for incorporating the cage 13 into the first race ring 14.

Specifically, the contact portion between the first inclined portion 13c of the projecting portion 14d, embedded load F ₁ in the (downward in FIG. 10) insertion direction of the retainer 13 acts. The built-load F ₁ is the force component F ₁₁ acting in a direction parallel to a tangent l ₁ of the first inclined portion 13c at a position where the corners of the overhang portion 14d comes into contact, perpendicular to the tangent line l ₁ it can be decomposed into a component force F ₁₂ acting in the direction. When the component force F ₁₁ exceeds a predetermined value, the retainer 13 is incorporated in the first bearing ring 14 rides over the projecting portion 14d.

Here, the component force _{F 11} is increased in proportion to make the contact angle theta ₁ between the tangent line _{l 1} and the surface parallel to the straight line _{l 2} of the overhang portion 14d. When θ ₁ ≧ 45 °, F ₁₁ ≧ F ₁₂ is satisfied. Accordingly, embedded load F ₁ when the contact angle theta ₁ is incorporated by adjusting the so as to more than 45 ° radial length A of the first inclined portion 13c, the retainer 13 to the first bearing ring 14 Can be reduced.

  Next, a method for separating the cage 13 from the first track ring 14 will be described with reference to FIGS. 11 and 12. 11 is a view showing a state in which the cage 13 is separated from the first track ring 14, and FIG. 12 is an enlarged view of a portion R in FIG.

  First, referring to FIG. 11, when the cage 13 is separated from the first raceway ring 14, a part of the outer edge of the cage 13 (the right side in FIG. 11) is in contact with the inner diameter surface of the flange portion 14c. In the state, the other side (left side in FIG. 11) is lifted. At this time, the outer edge portion of the cage 13 and the overhanging portion 14d are caught and cannot be separated. Here, when an external force is applied to the thrust roller bearing 11, the cage 13 and the overhanging portion 14d are elastically deformed, and both are separated.

Referring to FIG. 12, in the R portion of FIG. 11, the second inclined portion 13d of the retainer 13 and the corner portion of the overhang portion 14d are in contact with each other. The contact portion between the second inclined portion 13d of the protruding portion 14d, the separation direction of the cage 13 is separate load F ₂ (the upward direction in FIG. 12) acts. This separation load F ₂ is the force component F ₂₁ acting in a direction parallel to the tangent l ₃ of the second inclined portion 13d at the position where the corners of the overhang portion 14d comes into contact, the direction perpendicular to the tangent line l ₃ It can be decomposed into a component force F ₂₂ acting on the. When the component force F ₂₁ exceeds a certain value, the cage 13 gets over the overhanging portion 14 d and is separated from the first race ring 14.

Here, the component force _{F 21} is increased in proportion to make the contact angle theta ₂ between the tangent line _{l 3} and the surface parallel to the straight line _{l 4} of the overhang portion 14d. When θ ₂ ≦ 45 °, F ₂₁ ≦ F ₂₂ is satisfied. Therefore, by adjusting the radial length B of the second inclined portion 13d so that the contact angle theta ₂ is at 45 ° or less, the separation load F when separating retainer 13 from the first bearing ring 14 two ₂ can be increased.

  Next, the dimensional relationship between the cage 13 and the first track ring 14 will be described with reference to FIG. FIG. 13 is a view showing a state in which the cage 13 is maximally biased to one side in the radial direction with respect to the first track ring 14. Note that the following description is similarly established between the cage 13 and the second race 15.

First, the minimum engagement margin σ between the outer edge portion of the cage 13 and the overhanging portion 14d is set to −0.1 mm ≦ σ ≦ 0.5 mm. The minimum allowance σ is σ = D ₁ − (D ₂ − where D ₁ is the outer diameter of the cage 13, D _{2 is} the inner diameter of the flange 14c, and t is the protruding amount of the overhang 14d. It is a value calculated in t).

  When the minimum allowance σ is larger than 0.5 mm, the amount of deformation of the cage 13 and the overhanging portion 14d becomes large at the time of assembly, which may cause deformation or breakage. On the other hand, if the minimum engagement allowance σ is smaller than −0.1 mm, the possibility that the cage 13 and the first race ring 14 are separated increases. Therefore, by setting the above range, separation can be effectively prevented without impairing assemblability.

The case where the minimum engagement allowance σ is −0.1 mm is a state in which the overhanging portion 14 d cannot lock the outer edge portion of the cage 13. However, as in the embodiment shown in FIG. 4, when a plurality of overhanging portions 14d are provided on the circumference of the outer peripheral flange portion 14c, the cage 13 is locked by the overhanging portions 14d on both sides thereof. Is done. With the above configuration, the retainer 13 and the separation force F ₂ between the first bearing ring 14 is greater than or equal to 30 N. As a result, it is possible to effectively prevent the two from separating when transported, particularly when transported with the track surface 14b vertical.

  Next, the radial bearing internal clearance δ formed between the outer edge of the cage 13 and the outer peripheral flange 14c is adjusted by the amount of eccentricity of the support member. Specifically, it is set to be twice or more the eccentric amount of the support member. Thereby, the heat_generation | fever and abrasion which arise when a cage | basket and a bearing ring contact by eccentric rotation can be prevented effectively.

  In the above embodiment, the outer edge portion of the cage 13 is folded to form the first and second inclined portions 13c and 13d having curved surfaces (R shape). However, the present invention is not limited to this. The first and second inclined portions 13c and 13d can be formed by any method. For example, chamfering may be performed on the corners of the outer edge. Further, the first and second inclined portions 13c and 13d are not limited to the curved surface shape (R shape), but may be a linear shape (tapered shape).

  In the first track ring 14 in the above embodiment, the position and number of the overhang portions 14d can be arbitrarily determined. However, if the number of the overhanging portions 14d is small, the retainer 13 may not be appropriately retained. On the other hand, if the number of the overhang portions 14d is too large, it is difficult to incorporate the cage 13. Further, from the viewpoint of appropriately holding the cage 13, it is desirable to arrange the overhang portions 14 d at equal intervals. This also applies to the staking 15d formed on the second race 15.

  Moreover, in said embodiment, the 1st track ring 14 which has the overhang | projection part 14d, the 2nd track ring 15 which has staking 15d, and 1st and 2nd inclination part 13c, 13d in an outer edge part. Although the example of the thrust roller bearing 11 provided with the holder | retainer which has this was shown, it is not restricted to this, Arbitrary structures are employable. For example, the staking may be formed on the outer peripheral flange portion of the first track ring, and the overhang portion may be formed on the inner peripheral flange portion of the second track ring. In that case, the first and second inclined portions are provided at the inner edge of the cage. Furthermore, you may form an overhang | projection part in both the 1st and 2nd track ring. In this case, the first and second inclined portions are provided on both the outer edge portion and the inner edge portion of the cage.

  Further, the present invention can be applied to all types of thrust roller bearings having needle rollers, rod rollers, or cylindrical rollers as rollers. However, a thrust needle roller bearing is desirable from the viewpoint of reducing the thickness dimension.

  Next, with reference to Table 1, a test performed to confirm the effect of the present invention will be described. This effect confirmation test was performed using three types of thrust roller bearings in which the radial dimension A of the first inclined part 13c, the radial dimension B of the second inclined part 13d, and the minimum engagement allowance σ are as shown in Table 1. The built-in load and the separation load were measured for each of (Test bearings 1 to 3). Incorporation was performed using the method shown in FIGS. 9 and 10, and separation was performed using the method shown in FIGS.

  Referring to Table 1, in the test bearing 1 in which the first inclined portion 13c and the second inclined portion 13d have the same radial dimension (A≈B), the built-in load and the separation load are the same. It was. On the other hand, in the test bearing 2 in which A <B, the built-in load exceeded the separation load. Furthermore, in the test bearing 3 in which A> B, the separation load exceeded the built-in load.

  From the above, it was confirmed that as the radial dimension A of the first inclined portion 13c is larger, the cage 13 can be easily incorporated into the first race ring 14. Similarly, it was confirmed that the smaller the radial dimension B of the second inclined portion 13d is, the more difficult it is to separate the cage 13 from the first race ring 14. Then, if A> B, it was confirmed that the thrust roller bearing 11 can be obtained in which the cage 13 can be easily incorporated into the first race ring 14 and the two are difficult to separate.

  Next, a torque converter 20 according to an embodiment of the present invention will be described with reference to FIG. The torque converter 20 mainly includes an impeller 21, a stator 22, and a turbine 23. Specifically, an impeller 21 connected to an output shaft of an engine (not shown) (an “input shaft” when the torque converter 20 is centered) and an input shaft (not shown) of an automatic transmission (not shown) are centered. In this case, the turbines 23 connected to the “output shaft”) are arranged so as to face each other. The stator 22 is attached to a stator shaft fixed to the casing via a one-way clutch 24.

  The stator 22 directs the fluid recirculated between the impeller blades 21a and the turbine blades 23a each formed in a bowl shape from the turbine 23 side to the impeller 21 side on the inner diameter side thereof. Thereby, the flow direction of the fluid is changed and a forward rotational force is applied to the impeller 21 to amplify the transmission torque.

  The torque converter 20 generates a thrust load due to the rotation of either the input shaft or the output shaft. Further, the impeller 21 and the turbine 23 rotate eccentrically. Therefore, the thrust roller bearing 11 according to one embodiment of the present invention as shown in FIG. 2 is arranged between the impeller 21 and the stator 22 and between the stator 22 and the turbine 23.

  The thrust roller bearing 11 sets the internal gap δ between the cage 13 and the first race ring 14 to be twice or more the eccentric amount of the impeller 21 and the turbine 23. Thereby, it becomes a bearing suitable for supporting the rotating member which rotates eccentrically, such as the impeller 21 and the turbine 23. As a result, a highly reliable torque converter 20 can be obtained.

  In the above embodiment, the example in which the thrust roller bearing 11 shown in FIG. 2 is incorporated in the torque converter 20 shown in FIG. 14 is shown. However, the present invention is not limited to this, and other applications, in particular, eccentric rotation is performed. Can be used in an accompanying environment.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The present invention is advantageously used for a thrust roller bearing used in an environment in which eccentric rotation occurs.

It is an enlarged view of the P section of FIG. It is a figure which shows the thrust roller bearing which concerns on one Embodiment of this invention. It is sectional drawing of a 1st track ring. It is a front view of the 1st track ring. It is sectional drawing of a 2nd track ring. It is a front view of the 2nd track ring. It is sectional drawing of a holder | retainer. It is a front view of a holder | retainer. It is a figure which shows the state which incorporates a holder | retainer in a track ring. FIG. 10 is an enlarged view of a Q portion in FIG. 9. It is a figure which shows the state which isolate | separates a holder | retainer from a track ring. It is an enlarged view of the R part of FIG. It is a figure which shows the state which the cage | bias biased to the radial direction to the maximum in a track ring. It is a figure showing a torque converter concerning one embodiment of this invention. It is a figure which shows the conventional thrust roller bearing.

Explanation of symbols

  11, 101 Thrust roller bearing, 12, 102 Roller, 13, 103 Cage, 14, 15, 104, 105 Race ring, 13a, 14a, 15a Through hole, 13b Pocket, 13c, 13d Inclined portion, 14b, 15b, 104a , 105a raceway surface, 14c, 15c, 104b, 105b flange, 14d, 104c, 105c overhang, 15d staking, 20 torque converter, 21 impeller, 21a impeller blade, 22 stator, 23 turbine, 23a turbine blade.

Claims (6)

With multiple times,
A cage for holding the plurality of rollers;
A raceway surface on which the roller rolls, a cylindrical outer peripheral flange extending in the axial direction from an outer peripheral end of the raceway surface, and an axial movement of the cage are restricted by protruding from the tip of the outer peripheral flange to the inner diameter side. An annular first race ring having a first claw portion to
A raceway surface on which the rollers roll, a cylindrical inner circumferential flange extending in an axial direction from an inner circumferential end of the raceway surface, and a shaft of the retainer protruding from the tip of the inner circumferential flange to the outer diameter side An annular second race ring having a second claw portion for restricting directional movement;
Eccentric rotation of the first raceway and the second raceway between the outer peripheral flange and the outer edge of the cage, and between the inner peripheral flange and the inner edge of the cage. A bearing internal clearance that allows
At least one of the first and second claw portions is an overhang portion formed by bending,
The edge portion of the cage facing the overhanging portion is bent so as to be folded back in the radial direction and overlapped in the thickness direction of the cage, and the bending causes the first corner portion to face the raceway surface. an inclined portion, and the radial length than the first inclined portion at a corner portion in the thickness direction opposite relatively short second inclined portion Ru is formed, the thrust roller bearing. 2. The thrust roller bearing according to claim 1 , wherein the cage is manufactured by using SPC or SCM as a starting material, and undergoes soft nitriding, carburizing, or carbonitriding as a heat treatment. The thrust roller bearing according to claim 1 or 2 , wherein the first and second race rings are manufactured through carburizing or carbonitriding using SPC or SCM as a starting material. The contact angle theta ₁ between said protruding portion and the first inclined portion when incorporating the retainer bearing ring having a projecting portion satisfies theta ₁ ≧ 45 °, any of claims 1 to 3 The thrust roller bearing described in the above. The contact angle theta ₂ between the said protruding portion and the second inclined portion in separating the retainer from the bearing ring with the protruding portion satisfies theta ₂ ≦ 45 °, of claims 1 to 4 A thrust roller bearing according to any one of the above. An impeller connected to the input shaft;
A turbine connected to the output shaft;
A stator for directing working fluid from the turbine to the impeller;
A torque converter provided with the thrust roller bearing in any one of Claims 1-5 arrange | positioned between the said turbine and the said stator and / or between the said impeller and the said stator.

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