JP2008014414A - Thrust roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing for supplying a proper amount of lubricating oil to rolling portions of rollers while restricting the axial movement of a radial roller bearing even without a bearing ring. <P>SOLUTION: The thrust roller bearing 11 comprises: the plurality of rollers 12; and a cage 13 as a disc-like member having a hole 14 in the center and including a roller holding part 16 having a plurality of pockets 17 storing the rollers and extending to the radial direction, and an inner periphery collar part 15 located on the inner periphery of the holding part 16. The inner periphery collar part 15 has: an cylindrical portion 15a facing the hole 14 and linearly extending to the direction of the thickness; first and second bent portions 15b, 15c bent from both axial ends of the cylindrical portion 15a to the radial outside with a predetermined curvature; and wall faces 15d, 15e linearly extending from the first and second bent portions 15b, 15c to the radial outside, respectively. Lengths L2, L3 of linear portions of the wall faces 15d, 15e are each 0.8 mm or greater. <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 a car air conditioner compressor, an automatic transmission, a manual transmission, a hybrid vehicle, and the like.

  In recent years, compressors for car air conditioners, automatic transmissions, manual transmissions, hybrid vehicles, etc., have become more compact and have higher output as well as higher performance and lower fuel consumption considering the environment. The usage environment of thrust roller bearings has become increasingly severe. For example, in thrust roller bearings used in car air conditioner compressors, the lubricating oil has a low viscosity and reduced oil volume, and in thrust roller bearings used in automobile transmissions, super The conditions of use are harsh, such as high-speed rotation.

  In view of this, conventional thrust roller bearings and shaft support structures for supporting shafts of car air conditioner compressors, automatic transmissions, manual transmissions, hybrid vehicles, and the like are disclosed in, for example, Japanese Patent Application Laid-Open No. 2005-220959 (Patent Document 1) and Japanese Patent Application Laid-Open No. Hei. 6-213230 (Patent Document 2).

Referring to FIG. 6, a thrust roller bearing 101 described in Japanese Patent Application Laid-Open No. 2005-220959 (Patent Document 1) includes a plurality of rollers 102 and raceways 103 and 104 that sandwich the rollers 102 in the axial direction. And a cage 105 that holds the rollers 102. The cage 105 includes flange portions 105a and 105b on the inner and outer peripheral portions of a disk-shaped plate material, and a holding portion 105c in which a pocket for accommodating the rollers 102 is formed. The axis of the flange portions 105a and 105b The directional distance l ₁ and the axial distance l _{2 of} the holding portion 105c satisfy the relationship l ₁ <l ₂ .

  In the thrust roller bearing 101 having the above-described configuration, the lubricant can easily enter from between the raceway ring 103 and the flange portions 105a and 105b of the cage 105, thereby improving lubricity, thereby suppressing excessive wear and heat generation. It is described.

  On the other hand, referring to FIG. 7, in the rotating shaft support structure 111 described in Japanese Patent Laid-Open No. 6-213230 (Patent Document 2), the small diameter portion 112a and the large diameter portion 112b are made continuous by the step portion 112c. A shaft 112, an annulus 113 having an inner diameter larger than the outer diameter of the small diameter part 112a, a radial roller bearing 114 disposed between the inner peripheral surface of the annulus 113 and the small diameter part 112a, a step part 112c and an annulus And thrust roller bearings 115 disposed between them.

The thrust roller bearing 115 employed in the rotary shaft support structure 111 includes a roller 115a, a cage 115b that holds the roller 115a, and a raceway ring 115c that is attached to the stepped portion 112c. Then, the radial roller bearing 114 and the thrust roller bearing are provided by bending the inner peripheral portion of the bearing ring 115c at a right angle to the opposite side to the stepped portion 112c and providing the cylindrical portion 115d that restricts the movement of the radial roller bearing 114 in the axial direction. It is described that interference with 115 can be prevented.
JP 2005-220959 A JP-A-6-213230

  In the thrust roller bearing 101 as shown in FIG. 6, when the holding portion 105c of the cage 105 abuts on the raceway ring 103, the gap between the raceway ring 103 and the flange portions 105a and 105b is minimized. The amount of lubricating oil flowing in from there is also reduced. In this case, there is a possibility that a sufficient amount of lubricating oil cannot be supplied when the thrust roller bearing 101 is used in a lean lubrication environment.

  Also, in car air conditioner compressors, automatic transmissions, manual transmissions, and hybrid cars, it is common to use cage and roller type thrust roller bearings consisting of rollers and cages to reduce the axial width. It is. Therefore, when the thrust roller bearing 115 in which the bearing ring 115c is an essential component for preventing the interference with the radial roller bearing 114 is used, it also hinders reduction in axial dimension.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a thrust roller having a structure capable of supplying an appropriate amount of lubricating oil to the rolling part of the roller and capable of restricting axial movement of the radial roller bearing even if the bearing ring is omitted. It is to provide a bearing.

  A thrust roller bearing according to the present invention includes a plurality of rollers and a disk-shaped member in which a hole is formed in the center, a roller holding portion that has a plurality of pockets for accommodating the rollers and extends in the radial direction, And a cage including an inner circumferential flange located on the inner circumference of the roller holding portion. The inner peripheral flange portion has a cylindrical portion that faces the hole and extends linearly in the thickness direction, and first and second bent portions that are bent radially outward with a predetermined curvature from both axial end portions of the cylindrical portion. And a wall surface linearly extending radially outward from each of the first and second bent portions, and the length of the linear portion of the wall surface is 0.8 mm or more.

  As in the above configuration, the length of the linear portion of the wall surface extending radially outward from each of the first and second bent portions is set to 0.8 mm or more, thereby restricting the axial movement of the radial roller bearing by the wall surface. can do. Further, by providing the wall surfaces on both sides in the thickness direction, the thrust roller bearing can be assembled without being conscious of the front and back sides, so that there is an advantage that the assembling becomes easy.

  Preferably, the retainer further includes a plurality of pockets that penetrate the wall surface extending radially outward from the first bent portion in the thickness direction and accommodates the rollers, and the protrusion amount of the roller pockets is 0.1 mm or more. is there.

  As one embodiment, the wall surface facing the rolling surface of the roller in the pocket has a first retaining portion for preventing the roller from coming off to one side in the axial direction on the one side in the thickness direction of the cage, and the thickness direction of the cage. A second retaining portion for preventing the roller from coming off to the other side in the axial direction is provided on the other side.

  With this configuration, the cage serves as a roller guide when the bearing rotates, and a predetermined amount of protrusion from the roller pocket is always ensured. As a result, a gap through which the lubricating oil can flow is ensured between the cage and the peripheral member, so that a thrust roller bearing with excellent lubricity can be obtained.

  According to the present invention, there is provided a thrust roller bearing having a structure capable of supplying an appropriate amount of lubricating oil to the rolling portion of the roller and capable of restricting axial movement of the radial roller bearing even if the bearing ring is omitted. Obtainable.

  With reference to FIGS. 1-5, the thrust roller bearing 11 which concerns on one Embodiment of this invention is demonstrated. 1 is a plan view of the thrust roller bearing 11, FIG. 2 is a sectional view taken along line II-II in FIG. 1, FIG. 3 is a diagram showing dimensions of the thrust roller bearing 11, and FIGS. It is the elements on larger scale of the state which incorporated in shafts 21 and 31.

  First, referring to FIG. 1 and FIG. 2, the thrust roller bearing 11 includes a plurality of rollers 12 and a cage 13 that holds a distance between adjacent rollers 12. The roller 12 is a cylindrical roller and has chamfered portions at both ends in the longitudinal direction.

  The cage 13 is a disk-shaped member having a hole 14 formed in the center, and is formed by bending a metal flat plate by pressing or the like. A plurality of pockets 17 for accommodating the rollers 12 are formed to extend in the radial direction, and a roller holding portion 16 that is formed in the inner periphery of the roller holding portion 16 along the outer periphery of the hole 14. And have.

  The inner peripheral flange 15 faces the hole 14 and extends linearly in the thickness direction of the retainer 13, and first and second bent portions that are bent radially outward at both axial ends of the cylindrical portion 15 a. The first and second bent portions 15b and 15c include wall surfaces 15d and 15e extending radially outward, respectively.

  The wall surface 15d extending from the first bent portion 15b has a straight portion having a predetermined length, and its tip extends radially outward while being bent in the thickness direction of the cage 13, and further includes the roller holding portion 16 and the outside thereof. An outer peripheral flange 18 is formed along the outer periphery of the cage 13.

  The wall surface 15e extending from the second bent portion 15c extends linearly outward in the radial direction to the front of the pocket 17, and the tip is bent in the thickness direction of the retainer 13, that is, in the direction of the wall surface 15d. And the cross-sectional shape of the inner periphery collar part 15 becomes a substantially square shape with four corners each having a predetermined curvature.

  The roller holding portion 16 is positioned on the extension of the wall surface 15d extending radially outward from the first bent portion 15b, and a plurality of pockets 17 penetrating in the thickness direction are directed in the radial direction with respect to the bearing rotation axis. They are arranged radially.

  The pocket 17 has a rectangular shape along the outer diameter of the roller 12, and the wall surface facing the rolling surface of the roller 12 in the pocket 17 is the axis of the roller 12 at the radial center of one side in the thickness direction of the cage 13. A first retaining portion 17a that prevents the roller 12 from coming off to one side in the direction, and a second retaining portion 17b that prevents the roller 12 from coming off to the other side in the axial direction at both radial ends on the other side in the thickness direction of the cage 13. And an inclined portion 17c that connects the first and second retaining portions 17a, 17b.

  The outer peripheral flange portion 18 is formed by bending the outer peripheral portion of the wall surface 15d extending from the first bent portion 15b to one side in the axial direction and further folding the tip end thereof 180 ° to the other side in the axial direction. In this embodiment, the axial widths of the inner peripheral flange 15 and the outer peripheral flange 18 are the same. In addition, although the outer periphery collar part 18 is not an essential component of this invention, the rigidity of the holder | retainer 13 whole improves by providing the outer periphery collar part 18. FIG.

Further, with reference to FIG. 3, assuming that the thickness of the cage 13 is t, the radius of curvature of the first bent portion 15 b is R ₁ , and the radius of curvature of the second bent portion 15 c is R ₂ , t <R ₁ , t <A range that satisfies R ₂ is set. Further, when the length of the cylindrical portion 15a and _{L 1,} is set to satisfy _{L 1} ≧ 0.4 mm. Further, the protrusion amount δ ₁ from the opening on one side of the pocket 17 of the roller 12 and the protrusion amount δ ₂ from the opening on the other side of the pocket 17 are each set to 0.1 mm or more. Further, the lengths L ₂ and L ₃ of the straight portions of the wall surfaces 15d and 15e extending from the first and second bent portions 15b and 15c are set to 0.8 mm or more.

Next, referring to FIG. 4, the thrust roller bearing 11 is disposed at a stepped portion of the shaft 21 of a car air conditioner compressor, an automatic transmission, a manual transmission, a hybrid vehicle, or the like. The cylindrical portion 15 a functions as a guide portion when the hole 14 is fitted to the shaft 21. Thereby, the behavior of the cage 13 can be stabilized when the bearing rotates. The length L ₁ of the cylindrical portion 15a can be set to L ₁ ≧ 0.4 mm, so that wear of the inner peripheral flange portion 15 and the shaft 21 can be suppressed.

  Further, the shaft 21 has a corner R portion 21a at the step portion from the viewpoint of strength and processing cost, and the thrust roller bearing 11 is disposed so that the second bent portion 15c faces the corner R portion 21a. Thereby, it can prevent that the axial direction edge part of the cylindrical part 15a interferes with the corner R part 21a of the axis | shaft 21. FIG. As a result, it becomes possible to prevent the behavior of the cage from becoming unstable and the cage 13 from being worn away.

Note that the radii of curvature R ₁ and R ₂ of the first and second bent portions 15b and 15c are t <R ₁ and t <R ₂ in relation to the plate thickness t of the cage 13, and are for car air conditioners. In the thrust roller bearing 11 that supports the shaft 21 of a compressor, automatic transmission, manual transmission, hybrid vehicle or the like, the plate thickness of the cage 13 is generally set to about 0.4 mm to 1.0 mm. Further, the radii of curvature R ₁ and R ₂ of the first and second bent portions 15b and 15c may be the same value (R ₁ = R ₂ ) or different values as long as they are within the above range. (R ₁ ≠ R ₂ ) may be used.

  Here, the radius of curvature of only one of the first and second bent portions 15b and 15c may be larger than the plate thickness t of the cage 13, but the first radius having a radius of curvature larger than the plate thickness t. Further, by providing the second bent portions 15b and 15c at both axial ends of the cylindrical portion 15a, the thrust roller bearing 11 can be incorporated into the shaft 21 without being aware of the front and back. That is, regardless of which of the first and second bent portions 15b and 15c is disposed so as to face the corner R portion 21a, interference between the cage 13 and the corner R portion 21a can be prevented.

  In addition, by providing the first and second retaining portions 17a and 17b in the pocket 17, the cage 13 serves as a roller guide when the bearing rotates. Thereby, since the movement of the cage 13 in the axial direction is restricted, it is possible to ensure a predetermined protrusion amount from the opening of the pocket 17 of the roller 12 even when the cage 13 is biased in the axial direction as much as possible. It becomes. As a result, the wall surface in the thickness direction of the cage 13 and the shaft 21 are not in contact with each other, torque loss during rotation of the bearing can be suppressed, and between the wall surface in the thickness direction of the cage 13 and the shaft 21. Oil permeability is improved.

  Next, a shaft support structure for supporting the shaft 31 with the radial roller bearing 33 and the thrust roller bearing 11 according to one embodiment of the present invention will be described with reference to FIG.

  The rotating shaft support structure includes a shaft 31 having a small-diameter portion 31a and a large-diameter portion 31b, an outer member 32 disposed on the radially outer side of the small-diameter portion 31a, an outer-diameter surface of the small-diameter portion 31a, and an outer member 32. A radial roller bearing 33 disposed between the inner diameter surfaces and a thrust roller bearing 11 according to one embodiment of the present invention disposed between the large diameter portion 31b and the end surface of the outer member 32 are provided.

  The radial roller bearing 33 includes a plurality of rollers 33a and a retainer 33b that holds an interval between adjacent rollers 33a, and a cage having an outer diameter surface of the small diameter portion 31a and an inner diameter surface of the outer member 32 as a raceway surface. This is a & roller type needle roller bearing that supports a radial load applied to the shaft 31.

  On the other hand, in the thrust roller bearing 11 according to an embodiment of the present invention, the end surface of the large diameter portion 31b and the wall surface 15e extending in the outer diameter direction from the second bent portion 15c face each other, and the retainer 33b of the radial roller bearing 33 It arrange | positions so that the axial direction end surface and the linear part of the wall surface 15d extended in an outer diameter direction from the 1st bending part 15b may face.

  By disposing the radial roller bearing 33 and the thrust roller bearing 11 as shown in FIG. 5, even if the bearing ring is omitted, the movement of the radial roller bearing 33 in the axial direction can be restricted by the straight portion of the wall surface 15d. It becomes possible. At this time, since the cross-sectional shape of the inner peripheral flange portion 15 is made substantially rectangular and the rigidity is improved, the inner peripheral flange portion 15 can be prevented from being deformed by contact with the radial roller bearing 33.

In the thrust roller bearing 11 used for a compressor for an car air conditioner, an automatic transmission, a manual transmission, a hybrid vehicle, and the like, the length L ₂ of the linear portion of the wall surfaces 15d and 15e that restricts the radial roller bearing 33 from moving in the axial direction. , L ₃ is desirably 0.8 mm or more. In order to restrict the movement of the radial roller bearing 33 in the axial direction, a linear portion having a predetermined length may be provided only on the wall surface 15d facing the radial roller bearing 33, but both wall surfaces 15d and 15e have a predetermined length. Providing this straight portion is advantageous in that it can be incorporated without being conscious of the front and back of the thrust roller bearing 11.

Further, in this embodiment, the length _{L 2} of the linear portion of the wall 15d extending from the first bent portion 15b is made longer than the length _{L 3} of the linear portion of the wall surface 15e extending from the second bend 15c _(L 2> Although an example of L ₃ ) has been shown, the length is not limited thereto, and can be set to any length within the above range. For example, the straight portion of the wall surface 15e may be longer than the straight portion of the wall surface 15d (L ₂ <L ₃ ), or both may have the same length (L ₂ = L ₃ ).

  Next, a method for manufacturing the cage 13 having the above configuration will be described. The cage 13 is manufactured by pressing using a steel plate such as carbon steel as a starting material. First, a steel plate is punched into a disc shape and a hole 14 is formed in the center. Next, the inner peripheral flange portion 15, the outer peripheral flange portion 18, and portions that become the retaining portions 17a and 17b when forming the pocket are formed by bending. Finally, a pocket 17 penetrating in the thickness direction of the cage 13 is formed by punching. At this time, the pockets 17 may be processed one by one, but by processing all the pockets 17 at the same time, the processing time can be shortened and the processing accuracy can be improved.

  In order to obtain predetermined mechanical properties such as hardness, the cage 13 manufactured by the above method is subjected to heat treatment such as soft nitriding treatment, carburizing quenching, and tempering. In addition, since the processing of the cage 13 described above is performed while supplying lubricating oil to the processed portion, it is desirable to wash and dry the lubricating oil adhering to the surface of the cage 13 before the heat treatment.

  In addition, although the example which employ | adopted the cylindrical roller as a rolling element showed the thrust roller bearing 11 in said embodiment, this invention is applicable not only to this but a thrust needle roller bearing. Since the thrust needle roller bearing has a small thickness direction dimension, it is effective in reducing the axial dimension of the support portion.

  Further, the thrust roller bearing 11 in the above embodiment is an example of a cage and roller type bearing composed of the roller 12 and the cage 13, but is not limited thereto, and the track covers one or both of the axial directions. A ring may be further provided.

  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 in thrust roller bearings that support shafts of compressors for car air conditioners, automatic transmissions, manual transmissions, and hybrid vehicles.

It is a top view of the thrust roller bearing which concerns on one Embodiment of this invention. It is sectional drawing in II-II of FIG. It is a figure which shows the dimensional relationship of the thrust roller bearing of FIG. It is the elements on larger scale in the state where the thrust roller bearing of Drawing 1 was built in the axis. It is the elements on larger scale in the state where the thrust roller bearing of Drawing 1 was built in the axis. It is a figure which shows an example of the conventional thrust roller bearing. It is a figure which shows the conventional rotating shaft support structure.

Explanation of symbols

  11, 101 Thrust roller bearing, 111 Rotating shaft support structure, 12, 32a, 102, 115a Roller, 13, 33b, 105, 115b Cage, 105a, 105b Flange, 105c Holding, 103, 104, 115c Raceway, 115d cylindrical portion, 14 holes, 15 inner peripheral flange portion, 15a cylindrical portion, 15b, 15c bent portion, 15d, 15e wall surface, 16 roller holding portion, 17 pocket, 17a, 17b retaining portion, 17c inclined portion, 18 outer peripheral flange Part, 21, 31, 112 shaft, 31a, 112a small diameter part, 31b, 112b large diameter part, 21a, 112c stepped part, 21b corner R part, 32 outer member, 113 ring body, 33, 114 radial roller bearing.

Claims (3)

With multiple times,
A disk-shaped member having a hole formed in the center, having a plurality of pockets for accommodating the rollers and extending in the radial direction, and an inner circumference located on the inner circumference of the roller holding part A cage including a buttock,
The inner circumferential collar is
A cylindrical portion facing the hole and extending linearly in the thickness direction;
First and second bent portions having a predetermined curvature and bent radially outward from both axial end portions of the cylindrical portion;
A wall surface linearly extending radially outward from each of the first and second bent portions,
A thrust roller bearing, wherein a length of the straight portion of the wall surface is 0.8 mm or more.   The thrust roller bearing according to claim 1, wherein an amount of protrusion of the roller from the pocket is 0.1 mm or more. The wall surface of the pocket facing the rolling surface of the roller is
A first retaining portion for preventing the roller from coming off to one side in the axial direction on one side in the thickness direction of the cage;
The thrust roller bearing according to claim 2, further comprising a second retaining portion that prevents the roller from slipping out to the other side in the axial direction on the other side in the thickness direction of the cage.

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