JP2008180284A - Thrust roller bearing and torque converter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing for effectively preventing the separation of a cage from bearing rings without impairing their assembling efficiency. <P>SOLUTION: The thrust roller bearing 11 comprises a plurality of rollers 12, the cage 13, and the set of bearing rings 14, 15. The cage 13 and the set of bearing rings 14, 15 are connected to each other not to separate each other at less than 30N. Between an outer periphery collar portion 14c and an outer edge portion of the cage 13 and between an inner periphery collar portion 15c and an inner edge portion of the cage 13, bearing internal clearances are provided for allowing eccentric rotation. At least one of first and second pawl portions 14d, 15d is an extending portion formed with bending work. -0.1 mm≤σ≤0.5 mm is satisfied, where σ is a minimum engaging allowance between each of the pawl portions 14d, 15d and the cage 13 with the cage 13 maximally deviating from the bearing rings 14, 15 to one radial side. <P>COPYRIGHT: (C)2008,JPO&INPIT

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. 19, 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 hold the rollers 102 in 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 raceway ring 104 may be separated due to the provision of the bearing internal clearance. For example, there is a possibility of separation when the 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. Thus, it is described that separation between the cage 103 and the raceway ring 104 can be prevented.

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), and 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 assembled in the 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 cage that holds the plurality of rollers, and a set of bearing rings that have raceway surfaces on which the plurality of rollers roll, and the cage and the set of rollers. It is a thrust roller bearing which is connected to the raceway so as not to be separated below 30N. One of the set of race rings includes a cylindrical outer peripheral flange extending in the axial direction from the outer peripheral end of the raceway surface, and a first protrusion that protrudes from the distal end of the outer peripheral flange toward the inner diameter side to limit the axial movement of the cage. It is the 1st track ring which consists of an annular member which has one claw part. The other of the set of race rings includes a cylindrical inner peripheral flange extending in the axial direction from the inner peripheral end of the raceway surface, and an axial movement of the cage protruding from the tip of the inner peripheral flange toward the outer diameter side. It is the 2nd track ring which consists of an annular member which has the 2nd claw part which restricts. 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. Furthermore, the first race ring, the second race ring, and the cage are connected and held by the engagement between the first claw portion and the cage and the engagement between the second claw portion and the cage. If the minimum hooking amount between the claw portion and the cage when the cage is maximally deviated to one side in the radial direction with respect to the raceway is σ, −0.1 mm ≦ σ ≦ 0.5 mm is satisfied.

  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, if the minimum allowance is greater than 0.5 mm, the amount of deformation of the cage increases during assembly, which may cause plastic deformation or breakage. On the other hand, when the minimum allowance is smaller than −0.1 mm, the possibility that the cage and the raceway ring are separated increases. Therefore, by setting the above range, separation can be effectively prevented without impairing assemblability.

  Preferably, the distal end of the overhang portion has a relatively longer radial length than the first inclined portion at the corner portion facing the raceway surface and the first inclined portion at the corner portion on the opposite side in the thickness direction. A second inclined portion. The first and second inclined portions function as guide surfaces when the cage gets over the overhang portion. Therefore, the radial length of the second 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 first inclined portion that functions as a guide surface during disassembly is decreased. . 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.

  More preferably, the edge portion of the cage facing the overhanging portion is more radially than the third inclined portion at the corner portion facing the raceway surface and the third inclined portion at the corner portion on the opposite side in the thickness direction. A fourth inclined portion having a relatively short length. The third and fourth inclined portions function as guide surfaces when getting over the overhanging portion. Therefore, the radial length of the third inclined portion that functions as the guide surface when assembling the cage and the raceway is increased, and the radial length of the fourth inclined portion that functions as the guide surface when disassembled is decreased. . 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.

  As one embodiment, the third and fourth inclined portions are formed by bending an edge portion. By bending the edge part, a curved surface (R-shaped) inclined part 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.

  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 minimum roller allowance σ between the cage and the claw portion is within the above range, so that the thrust roller can be effectively prevented from being separated without impairing the assembly of the cage and the raceway ring. A bearing can be obtained. 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. 3, 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 diameter surface 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.

Further, referring to FIG. 1, at the tip of the overhanging portion 14d, a first inclined portion 14e is formed at the corner facing the raceway surface 14b, and a second inclined portion is formed at the opposite corner in the thickness direction. 14f. Each of the first and second inclined portions 14e and 14f is a curved surface that is curved with a predetermined curvature. The radial length _{A 1} of the first inclined portion 14e is shorter as compared to the radial length _{B 1} of the second inclined portion _{14f (A 1 <B 1)} .

  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.

  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 portion of FIG. 9, the corner portion of the retainer 13 is in contact with the second inclined portion 14 f of the overhang portion 14 d. Here, the second inclined portion 14f functions as an insertion guide surface for incorporating the retainer 13 into the first race ring 14, and facilitates the incorporation.

Specifically, the outer and the contact portion between the second inclined portion 14f of the retainer 13, the 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 between the second inclined portion 14f at the position where the corners of the cage 13 are in contact, the direction perpendicular to the tangent line l ₁ It can be decomposed into a component force F ₁₂ acting on the. 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 when incorporated by adjusting the radial length A ₁ of the second inclined portion 14f so that the contact angle theta ₁ is 45 ° or more, the retainer 13 to the first bearing ring 14 ₁ 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 corner portion of the retainer 13 and the first inclined portion 14e of the overhang portion 14d are in contact with each other. The outer edge of the retainer 13 and the contact portion between the first inclined portion 14e, 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 first inclined portion 14e at the position where the corners of the cage 13 comes into contact, in a direction perpendicular to the tangent line l ₃ it can be decomposed into a component force F ₂₂ acting. 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 ₁ of the first inclined portion 14e such that the contact angle theta ₂ is at 45 ° or less, the separation load when separating the retainer 13 from the first bearing ring 14 two F 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 portion of the cage 13 and the flange portion 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 first and second inclined portions 14e and 14f having the curved surface shape (R shape) are shown. However, the present invention is not limited to this, and other shapes may be adopted. it can. For example, with reference to FIG. 14, another embodiment of the first and second inclined portions formed in the overhang portion will be described. Since other configurations are the same as those of the first race ring 14 described above, the description thereof is omitted.

Referring to FIG. 14, the tip of the overhang 16d is inclined so as to reduce the protruding amount of the overhang 16d from the corner on the side facing the raceway surface 16b toward the corner on the opposite side in the thickness direction. A portion 16e is provided. In comparison with FIG. 1, the first inclined portion 14e does not exist (A ₂ = 0), and the inclined portion 16e corresponds to the second inclined portion 14f. These inclined portions 14e, 14f, and 16e can be formed, for example, by chamfering corner portions (including both “C chamfering” and “R chamfering”).

  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.

  In the above embodiment, an example of the thrust roller bearing 11 including the first race ring 14 having the overhanging portion 14d and the second race ring 15 having the staking 15d is shown. Any configuration can be adopted without limitation. 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. Furthermore, you may form an overhang | projection part in both the 1st and 2nd track ring. Each overhang has first and second inclined portions.

  In the above embodiment, the first and second inclined portions 14e and 14f are provided on the overhanging portion 14d. However, the present invention is not limited to this, and the first and second inclined portions 14e and 14f may be provided on the edge of the cage. . A thrust roller bearing 31 according to another embodiment of the present invention will be described with reference to FIGS. 15 is a diagram corresponding to FIG. 1, FIG. 16 is a diagram corresponding to FIG. 10, and FIG. 17 is a diagram corresponding to FIG. Further, the basic configuration of the thrust roller bearing 31 is the same as that of the thrust roller bearing 11, and therefore, description of common points will be omitted, and description will be made focusing on differences.

First, referring to FIG. 15, the outer edge portion of the cage 33 is folded back inward in the radial direction, and third and fourth inclined portions 33 c and 33 d are formed at corner portions thereof. The third and fourth inclined portions 33c and 33d are curved surfaces that are curved with a predetermined curvature, respectively. The radial length _{A 3} of the third inclined portion 33c, as compared to radial length _{B 3} of a fourth inclined portion 33d is longer _{(A 3> B} 3). Further, when the cage 33 is incorporated in the raceway ring 34, the third inclined portion 33c is disposed so as to face the raceway surface.

  Referring to FIG. 16, when the cage 33 is incorporated in the raceway ring 34, the third inclined portion 33 c and the overhang portion 34 d of the cage 33 are located at the position corresponding to the Q portion of the thrust roller bearing 31 in FIG. 9. Is in contact with the corner. Here, the third inclined portion 33 c functions as an insertion guide surface for incorporating the retainer 33 into the third race ring 34.

Specifically, the contact portion between the third inclined portion 33c of the projecting portion 34d, a built load F ₃ acts on the insertion direction of the retainer 33 (downward direction in FIG. 16). The built-load F ₃ is a component force F ₃₁ acting in a direction parallel to the tangent l ₅ between the third inclined portion 33c at a position where the corners of the overhang portion 34d comes into contact, perpendicular to the tangent line l ₅ It can be decomposed into a component force F ₃₂ acting in the direction. When the component force F ₃₁ exceeds a certain value, the retainer 33 gets over the overhanging portion 34 d and is incorporated into the third race ring 34.

Here, the component force _{F 31} is increased in proportion to the tangent line _{l 3} and makes contact angle theta ₃ between the line _{l 6} surface and parallel of the overhang portion 34d. When θ ₃ ≧ 45 °, F ₃₁ ≧ F ₃₂ . Accordingly, embedded load F when incorporated by adjusting the radial length A ₃ of the third inclined portion 33c so that the contact angle theta ₃ is 45 ° or more, the retainer 33 in the third track ring 34 ₃ can be reduced.

Referring to FIG. 17, when separating retainer 33 from raceway ring 34, fourth inclined portion 33 d and overhanging portion of retainer 33 are located at a position corresponding to R portion in FIG. 11 of thrust roller bearing 31. The corner of 34d is in contact. The contact portion between the fourth inclined portion 33d of the protruding portion 34d, the separation direction of the retainer 33 is separated load F ₄ (the upward direction in FIG. 17) acts. The separation force F ₄ includes a component force F ₄₁ acting in a direction parallel to a tangent l ₇ of the fourth inclined portion 33d at the position where the corners of the overhang portion 34d comes into contact, the direction perpendicular to the tangent line l ₇ It can be decomposed into a component force F ₄₂ acting on the. When the component force F ₄₁ exceeds a certain value, the retainer 33 gets over the overhanging portion 34 d and separates from the third race ring 34.

Here, the component force F ₄₁ increases in proportion to the contact angle θ ₄ formed between the tangent line ₁₇ and the straight line ₁₈ parallel to the surface of the overhanging portion 34d. When θ ₄ ≦ 45 °, F ₄₁ ≦ F ₄₂ is satisfied. Therefore, by adjusting the radial length B ₃ of a fourth inclined portion 33d so that the contact angle theta ₄ is 45 ° or less, the separation load when separating the retainer 33 from the third bearing ring 34 two F ₄ can be increased.

  Further, when the bearing ring 14 having the first and second inclined portions 14e and 14f and the cage 33 having the third and fourth inclined portions 33c and 33d are combined, the built-in load is further reduced and the separation is performed. The load increases.

  Furthermore, 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, the test performed in order to confirm the effect of this invention using the thrust roller bearing 11 is demonstrated. The effect confirming test, the radial dimension A ₁ of the first inclined portion _14e, the radial dimension B _1, and the minimum take allowance three thrust values were as shown in Table 1 of the σ of the second inclined portion 14f The built-in load and the separation load were measured for each of the roller bearings (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 14e and the second inclined portion 14f have the same radial dimension (A ₁ ≈B ₁ ), the built-in load and the separation load are the same. Met. On the other hand, in the test bearing 2 in which A ₁ > B ₁ , the built-in load exceeded the separation load. Furthermore, in the test bearing 3 in which A ₁ <B ₁ , the separation load exceeded the built-in load.

Thus, as the radial dimension B ₁ of the second inclined portion 14f is large, incorporation into the bearing ring 14 of the cage 13 will become readily confirmed. Similarly, it was confirmed that the smaller the radial dimension A1 of the _first inclined portion 14e, the more difficult it is to separate the cage 13 from the raceway ring 14. Then, if A 1 _{<B 1,} easy to incorporate the cage 13 in the bearing ring 14, and both are confirmed that are difficult to thrust roller bearings 11 separated is obtained.

Next, with reference to Table 2, a test performed to confirm the effect of the present invention using the thrust roller bearing 31 will be described. The effect confirming test, the radial dimension A ₃ of the third inclined portion _33c, a fourth three kinds radial dimension B ₃ of the inclined portion _33d, and the value of the minimum take allowance σ was as shown in Table 2 in the thrust The built-in load and the separation load were measured for each of the roller bearings (test bearings 4 to 6). Incorporation was performed using the method shown in FIGS. 9 and 16, and separation was performed using the method shown in FIGS.

Referring to Table 2, in the test bearing 4 in which the third inclined portion 33c and the fourth inclined portion 33d have the same radial dimension (A ₃ ≈B ₃ ), the built-in load and the separation load are the same. Met. On the other hand, in the test bearing 5 in which A ₃ <B ₃ , the built-in load exceeded the separation load. Furthermore, in the test bearing 6 in which A ₃ > B ₃ , the separation load exceeded the built-in load.

From the above, it was confirmed that the larger the radial dimension A3 of the _third inclined portion 33c, the easier the cage 33 can be incorporated into the race ring 34. Similarly, as the radial dimension B ₃ of the fourth inclined portion 33d is small, separated from the bearing ring 34 of the retainer 33 may be difficult was confirmed. And it was confirmed that if A ₃ > B ₃ , it is possible to obtain the thrust roller bearing 31 in which the retainer 33 is easily incorporated into the race ring 34 and the two are difficult to separate.

  Next, a torque converter 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 raceway 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. The same effect can be obtained when the thrust roller bearing 31 is employed instead of the thrust roller bearing 11.

  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. 18 is shown. However, the present invention is not limited to this, and other applications, particularly eccentric rotation, are 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 which shows other embodiment of the overhang | projection part provided in a bearing ring. It is a figure corresponding to FIG. 1 of the thrust roller bearing which concerns on other embodiment of this invention. It is a figure corresponding to FIG. 10 of the thrust roller bearing which concerns on other embodiment of this invention. It is a figure corresponding to FIG. 12 of the thrust roller bearing which concerns on other embodiment of this invention. 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, 31, 101 Thrust roller bearing, 12, 32, 102 Roller, 13, 33, 103 Cage, 14, 15, 16, 34, 104, 105 Race ring, 13a, 14a, 15a Through hole, 13b Pocket, 14b , 15b, 104a, 105a Track surface, 14c, 15c, 16c, 34c, 104b, 105b Saddle, 14d, 16d, 34d, 104c, 105c Overhang, 15d Staking, 14e, 14f, 16e, 33c, 33d, 33e inclined part, 20 torque converter, 21 impeller, 21a impeller blade, 22 stator, 23 turbine, 23a turbine blade.

Claims (7)

A plurality of rollers, a cage for holding the plurality of rollers, and a set of bearing rings having a raceway surface on which the plurality of rollers roll, and the holder and the set of bearing rings are 30 N A thrust roller bearing connected so as not to be separated below,
One of the set of race rings includes 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 protruding from the tip of the outer peripheral flange toward the inner diameter side. A first race ring made of an annular member having a first claw portion for limiting
The other of the set of race rings includes a cylindrical inner circumferential flange extending in an axial direction from an inner circumferential end of the raceway surface, and an outer diameter projecting from the tip of the inner circumferential collar to the retainer. A second race ring made of an annular member having a second claw portion for restricting the axial movement of
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 first race ring, the second race ring, and the cage are connected by the engagement between the first claw portion and the cage and the engagement between the second claw portion and the cage. And
Assuming that σ is a minimum allowance between the claw portion and the cage when the cage is maximally biased to one radial side with respect to the raceway, −0.1 mm ≦ σ ≦ 0.5 mm is satisfied. , Thrust roller bearings.   The distal end of the overhang portion has a relatively longer radial length than the first inclined portion at the corner on the side facing the raceway surface and the first inclined portion at the opposite corner in the thickness direction. The thrust roller bearing according to claim 1, further comprising a second inclined portion.   An edge portion of the cage facing the overhanging portion has a third inclined portion at a corner portion facing the raceway surface and a radial direction from the third inclined portion at a corner portion on the opposite side in the thickness direction. The thrust roller bearing according to claim 1, further comprising a fourth inclined portion having a relatively short length.   The thrust roller bearing according to claim 3, wherein the third and fourth inclined portions are formed by bending the edge portion.   The thrust roller bearing according to any one of claims 1 to 4, wherein the cage is manufactured by using SPC or SCM as a starting material and undergoing any of soft nitriding, carburizing, or carbonitriding as heat treatment. .   The thrust roller bearing according to any one of claims 1 to 5, wherein the first and second race rings are manufactured through carburizing or carbonitriding using SPC or SCM as a starting material. 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 1-6 arrange | positioned between the said turbine and the said stator and / or between the said impeller and the said stator.

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