JP2009270692A - Roller with retainer and retainer for roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a roller with a thrust retainer, a retainer for a thrust roller bearing, and a roller bearing incorporated with them capable of suppressing drilling friction between a roller end face and an end face of a retainer pocket. <P>SOLUTION: The roller 1 with the thrust retainer includes a plurality of rollers 2, and the retainer 3 radially provided with a plurality of pockets 4 holding the rollers 2 in plural places in a circumferential direction. One or a plurality of contact positions between the end faces of the rollers 2 and the end faces 4a of the pockets 4 facing the roller end faces are deviated from axes Or of the rollers 2. Preferably, a displacement of the contact position from the axis Or of the roller 2 is within a range of a≤δ≤10a m, wherein (a) is a contact circle radius in contact of the roller end face and the retainer pocket face. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a roller with a cage of a thrust type or a radial type, a cage for a roller bearing, and a roller bearing incorporating these.

  Generally, a thrust roller bearing under operation is subjected to a force radially outward of the cage based on centrifugal force. With this force, the roller slides while being pressed against the end face located radially outward in the pocket of the cage. In this thrust roller bearing, under severe lubrication or high speed operation, severe wear called drilling wear occurs on the sliding portion between the roller end surface and the end surface of the cage pocket facing the roller end surface. Is known to occur. In recent years, such wear is more likely to occur with the increase in the speed of thrust roller bearings.

Therefore, conventionally, the end face of the roller has a convex shape, or a convex portion is provided on the end face of the cage pocket, and the end face of the roller end face and the end face of the cage pocket are brought into point contact with the axis of the roller. Measures have been taken to suppress drilling wear by suppressing (product of contact surface pressure P and sliding speed V) (for example, Patent Documents 1 and 2).
JP 2003-83333 A JP 2006-291979 A

The conventional techniques disclosed in Patent Documents 1 and 2 aim to suppress the PV value and reduce drilling wear by making point contact at the roller axis.
However, if the center of the contact circle coincides with the axis of the roller, there is no pulling action of the lubricant to the contact surface due to sliding between the roller end surface and the end surface of the cage pocket. Due to the rotation of the roller, it is scattered outside the contact circle. For this reason, the contact portion is brought into direct contact between metals due to a reduction in the oil film thickness due to lack of lubricating oil, and the wear rate increases rapidly. Therefore, how to repair the adsorbed molecular film peeled off from the metal surface by friction between the sliding surfaces is important for suppressing surface damage at the sliding portion.

  An object of the present invention is to provide a roller with a cage that can suppress drilling wear between the roller end surface and the end surface of the cage pocket, and a roller bearing, planetary gear mechanism, automobile multi-stage transmission, and hybrid vehicle incorporating these. A power transmission mechanism is provided.

A roller with a cage according to the present invention is a roller with a cage comprising a plurality of rollers and a cage provided with a plurality of pockets for holding each of the rollers. The roller end surface faces the roller end surface. One or a plurality of contact positions between the end faces of the pockets are shifted from the axis of the roller. The roller is, for example, a needle roller.
According to this configuration, the contact position between the end face of the roller and the end face of the cage pocket is shifted from the roller axis, so that the contact position changes as the roller rotates. Thus, in the region where the adsorbed molecular film is once peeled off by the contact between the end surface of the roller and the end surface of the cage pocket, the adsorbed molecular film is repaired until the next contact position. In addition, since the contact position deviates from the roller axis, a lubricating film is more easily formed on the contact portion due to the wedge film action. Due to the effect of improving the lubricity of both, the contact portion can be prevented from reaching a severe environmental lubrication state, and drilling wear can be suppressed.

ρ：ころの密度[kg ／m³]
Ｄ：ころの直径[m]
Ｌr ：ころの長さ[m]
Ｄ_m ：ころピッチ円直径[m]
Ｎ：軌道輪の回転速度[rpm]
Ｒ：ころ／保持器ポケット面接触における等価曲率半径[m]
Ｅ：ころ／保持器ポケット面接触における等価ヤング率[Pa]
である。
試験結果から、耐摩耗性が向上する前記ずれ量の範囲は、ａ≦δ≦１０ａ[m]であることがわかっている。 In this invention, the amount of deviation δ [m] of the contact position from the axis of the roller,
The range is preferably a ≦ δ ≦ 10 a [m].
However,

ρ: Roller density [kg / m ³ ]
D: Roller diameter [m]
Lr: Roller length [m]
D _m : Roller pitch circle diameter [m]
N: Rotational speed of race ring [rpm]
R: Equivalent radius of curvature at roller / cage pocket surface contact [m]
E: Equivalent Young's modulus in roller / cage pocket surface contact [Pa]
It is.
From the test results, it is known that the range of the deviation amount in which the wear resistance is improved is a ≦ δ ≦ 10a [m].

  In this invention, you may shift the said contact position from the axial center of the said roller by inclining a part or whole of the said pocket end surface facing the said roller end surface with respect to the central axis of the said pocket.

In this invention, a part or the whole of the pocket end surface facing the roller end surface is curved, and the center of curvature is shifted from the central axis of the pocket, thereby shifting the contact position from the axis of the roller. Also good. The center of curvature is the most protruding position of the curved pocket end surface.
In this invention, a part or the whole of the roller end surface may be curved, and the contact position may be shifted from the roller axis by shifting the center of curvature from the roller axis.

としたことを特徴とする。
一般的に保持器ポケットの形状は、ころの寸法に比べて大きな寸法に設定されているので、軸受の運転中に、その隙間の範囲内でころがポケットに対して相対的に動き得る。そこで、上記条件を満たすように軸方向距離δ₁または周方向距離δ₂を設定すれば、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、耐摩耗性の向上が可能となる。 The roller with a thrust cage of the first configuration according to the present invention is disposed between a pair of bearing rings facing each other in the axial direction, and is provided with a plurality of pockets that radially hold the rollers at a plurality of locations in the circumferential direction. A rolling element guide type, on the end face of the pocket facing the end face of the roller, a convex part or a plurality of convex parts having a curved surface in part or in its entirety are provided, the end face of the roller, The contact position with the end face of the pocket facing the roller end face is shifted from the axial center of the roller,
The axial clearance between the pocket and the roller is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the axial distance from the central axis of the pocket at the apex position of the convex portion is When δ ₁ m and the circumferential distance from the central axis of the pocket at the apex position of the convex portion are δ ₂ m,

It is characterized by that.
In general, the cage pocket is set to have a size larger than that of the roller, so that the roller can move relative to the pocket within the clearance during the operation of the bearing. Therefore, if the axial distance δ ₁ or the circumferential distance δ ₂ is set so as to satisfy the above conditions, the contact between the roller end face and the cage pocket end face can be achieved even if the position of the roller changes within the pocket clearance. In other words, the distance from the shaft center is within the range of a ≦ δ ≦ 10 a [m], and the wear resistance can be improved.

としたことを特徴とする。
この構成の場合も、上記条件を満たすように軸方向距離δ₁または周方向距離δ₂を設定すれば、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、耐摩耗性の向上が可能となる。 A roller with a thrust retainer according to another configuration of the present invention is disposed between a pair of bearing rings facing each other in the axial direction, and is provided with a plurality of pockets that radially hold the rollers at a plurality of locations in the circumferential direction. A bearing ring guide type, wherein one or a plurality of convex portions are provided on an end surface of the pocket facing the end surface of the roller, an end surface of the roller, and an end surface of the pocket facing the roller end surface; Shift the contact position of the roller from the axis of the roller,
The axial clearance between the cage and the race is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the axial distance from the central axis of the pocket at the apex position of the convex portion is δ _1. m, when the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m,

It is characterized by that.
Even in this configuration, if the axial distance δ ₁ or the circumferential distance δ ₂ is set so as to satisfy the above conditions, even if the roller position changes within the pocket clearance, the roller end face / retainer pocket The distance between the contact portion between the end faces and the axis is within the range of a ≦ δ ≦ 10 a [m], and the wear resistance can be improved.

としたことを特徴とする。
この構成の場合も、上記条件を満たすように径方向距離δ₁または周方向距離δ₂を設定すれば、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、耐摩耗性の向上が可能となる。 The roller with a radial cage according to the first configuration of the present invention is disposed between inner and outer races disposed concentrically with respect to the shaft center, and the rollers are parallel to the shaft center at a plurality of circumferential positions. A rolling element guide type provided with a plurality of pockets to be held in the pocket, wherein one or a plurality of convex portions are provided on an end face of the pocket facing the end face of the roller; The position of contact with the end face of the pocket facing the end face is shifted from the axial center of the roller,
The radial clearance between the pocket and the roller is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the radial distance from the central axis of the pocket at the apex position of the convex portion is When δ ₁ m and the circumferential distance from the central axis of the pocket at the apex position of the convex portion are δ ₂ m,

It is characterized by that.
Even in this configuration, if the radial distance δ ₁ or the circumferential distance δ ₂ is set so as to satisfy the above conditions, even if the roller position changes within the pocket clearance, the roller end face / retainer pocket The distance between the contact portion between the end faces and the axis is within the range of a ≦ δ ≦ 10 a [m], and the wear resistance can be improved.

としたことを特徴とする。
この構成の場合も、上記条件を満たすように径方向距離δ1 または周方向距離δ2 を設定すれば、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、耐摩耗性の向上が可能となる。 A roller with a radial cage according to another configuration of the present invention is disposed between inner and outer races arranged concentrically with respect to the shaft center, and the rollers are parallel to the shaft center at a plurality of circumferential positions. A bearing ring guide type provided with a plurality of pockets to be held, wherein one or a plurality of convex portions are provided on an end face of the pocket facing the end face of the roller, and an end face of the roller and the end face of the roller The position of contact with the end face of the pocket opposite to the center is shifted from the axial center of the roller,
The radial clearance between the cage and the race is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the radial distance from the central axis of the pocket at the apex position of the convex portion is When δ ₁ m and the circumferential distance from the central axis of the pocket at the apex position of the convex portion are δ ₂ m,

It is characterized by that.
Even in this configuration, if the radial distance δ1 or the circumferential distance δ2 is set so as to satisfy the above conditions, even if the roller position changes within the pocket clearance, the distance between the roller end face and the cage pocket end face The distance between the contact portion and the shaft center is within the range of a ≦ δ ≦ 10 a [m], and the wear resistance can be improved.

A roller bearing according to the present invention is characterized by incorporating a roller with a cage having any one of the above-described configurations according to the present invention. By applying this roller with cage as a roller bearing used in a mechanism having a high rotational speed, the effect of suppressing drilling wear at the end surface contact portion can be improved.
The planetary gear mechanism according to the present invention is characterized by incorporating the roller with cage having any one of the above-described configurations according to the present invention. Thereby, the effect of suppressing drilling wear at the end surface contact portion in the roller with cage incorporated therein can be increased, and a planetary gear mechanism having excellent durability can be obtained.
A multi-stage transmission for an automobile according to the present invention is characterized by incorporating a roller with a cage having any one of the above-described configurations according to the present invention. Thereby, the drilling wear suppression effect in the end surface contact part in the roller with a built-in roller can be improved, and the multistage transmission for an automobile having excellent durability can be obtained.
A power transmission mechanism for a hybrid vehicle according to the present invention is characterized by incorporating a roller with a retainer having any one of the configurations according to the present invention. As a result, the effect of suppressing drilling wear at the end face contact portion of the roller with cage incorporated therein can be improved, and a power transmission mechanism for a hybrid vehicle having excellent durability can be obtained.

  The roller with a thrust cage of the present invention is a roller with a thrust cage comprising a plurality of rollers and a cage in which a plurality of pockets for holding the rollers are radially provided at a plurality of locations in the circumferential direction. Since one or a plurality of contact positions between the roller end surface and the end surface of the pocket facing the roller end surface are shifted from the roller axis, drilling wear between the roller end surface and the end surface of the cage pocket Can be suppressed.

としたため、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、その接触部でのドリリング摩耗を抑制できる。 A roller with a thrust retainer according to a first configuration of the present invention is of a rolling element guide type, and is provided with one or a plurality of convex portions on an end surface of the pocket facing the end surface of the roller, The position of contact between the end surface and the end surface of the pocket facing the roller end surface is shifted from the axial center of the roller, the axial clearance between the pocket and the roller is δ _pa m, and the pocket and the roller Δ _pc m, the axial distance of the apex position of the convex part from the central axis of the pocket δ ₁ m, and the peripheral distance of the apex position of the convex part from the central axis of the pocket δ _{When 2} m

Therefore, even if the position of the roller changes within the pocket clearance, the distance between the roller end face and the cage pocket end face and the shaft center is within the range of a ≦ δ ≦ 10 a [m]. The drilling wear at the contact portion can be suppressed.

としたため、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、その接触部でのドリリング摩耗を抑制できる。 A roller with a thrust retainer according to another configuration of the present invention is of a bearing ring guide type, and is provided with one or a plurality of convex portions on an end surface facing the end surface of the roller in the pocket, and the end surface of the roller And the position of contact with the end surface of the pocket facing the roller end surface is shifted from the axial center of the roller, the axial clearance between the cage and the raceway is δ _pa m, and the pocket and the roller The circumferential clearance is δ _pc m, the axial distance from the central axis of the pocket at the apex position of the convex portion is δ ₁ m, and the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m

Therefore, even if the position of the roller changes within the pocket clearance, the distance between the roller end face and the cage pocket end face and the shaft center is within the range of a ≦ δ ≦ 10 a [m]. The drilling wear at the contact portion can be suppressed.

としたため、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、その接触部でのドリリング摩耗を抑制できる。 A roller with a radial cage according to a first configuration of the present invention is of a rolling element guide type, and is provided with one or a plurality of convex portions on an end surface facing an end surface of a pocket roller, The position of contact between the end surface and the end surface of the pocket facing the roller end surface is shifted from the axial center of the roller, the radial clearance between the pocket and the roller is δ _pa m, and the pocket and the roller Δ _pc m, the radial distance from the central axis of the pocket at the apex position of the convex portion to δ ₁ m, and the circumferential distance from the central axis of the pocket at the apex position of the convex portion to δ _{When 2} m

Therefore, even if the position of the roller changes within the pocket clearance, the distance between the roller end face and the cage pocket end face and the shaft center is within the range of a ≦ δ ≦ 10 a [m]. The drilling wear at the contact portion can be suppressed.

としたため、ポケットの隙間の範囲内でころの位置が変化しても、ころ端面・保持器ポケット端面間の接触部ところ軸心との距離がａ≦δ≦１０ａ[m]の範囲内に収まり、その接触部でのドリリング摩耗を抑制できる。 A radial roller bearing retainer according to another configuration of the present invention is a bearing ring guide type retainer, and is provided with one or a plurality of convex portions on an end surface of the pocket facing the end surface of the roller. The position of contact between the end face of the roller and the end face of the pocket facing the roller end face is shifted from the axial center of the roller, the radial clearance between the cage and the raceway is δ _pa m, The circumferential clearance between them is δ _pc m, the radial distance from the central axis of the pocket at the apex position of the convex portion is δ ₁ m, and the circumferential distance from the central axis of the pocket at the apex position of the convex portion is When δ ₂ m,

Therefore, even if the position of the roller changes within the pocket clearance, the distance between the roller end face and the cage pocket end face and the shaft center is within the range of a ≦ δ ≦ 10 a [m]. The drilling wear at the contact portion can be suppressed.

  A roller bearing according to the present invention incorporates a roller with a cage having any one of the above-described configurations of the present invention or a roller bearing cage having any one of the above-described configurations according to the present invention. By applying this roller bearing as the bearing, the effect of suppressing drilling wear at the end surface contact portion can be increased.

  A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a sectional view of a roller with a thrust cage according to this embodiment, and FIG. 2 is a partially enlarged plan view thereof. This roller 1 with a thrust cage is composed of a plurality of needle rollers 2 and an annular cage 3 in which a plurality of pockets 4 for holding the rollers 2 are provided at a plurality of locations in the circumferential direction. The As shown in FIG. 3A, the end surface of the roller 2 has a convex curved surface whose apex is shifted from the roller axis Or by a predetermined amount δ. Hereinafter, the deviation of the apex of the end face is referred to as eccentricity. For comparison, FIG. 3B shows an example of a general needle roller 2A having an end surface that is curved with the center of curvature coinciding with the roller axis Or. In this case, the end face vertex of the roller 2A coincides with the roller axis Or.

According to this embodiment, since the contact position between the end surface of the roller 2 and the end surface 4a of the cage pocket 4 is shifted from the roller axis Or, the contact circle of the roller 2 rotates as shown in FIG. The position changes. In the figure, a circle 21A indicated by a broken line indicates a contact circle at the previous time, and a circle 21B indicated by a solid line indicates a contact circle at the next time.
Thereby, in the region where the adsorbed molecular film is once peeled off due to the contact between the end face of the roller 2 and the end face 4a of the cage pocket 4, the adsorbed molecular film is repaired before entering the inside of the contact circle. Is done. Further, since the contact circles 21A and 21B are disengaged from the roller axis Or, a lubricating film is more easily formed on the contact portion due to the wedge film action. Due to the effect of improving the lubricity of both, the contact portion can be prevented from reaching a severe environmental lubrication state, and drilling wear can be suppressed.

FIG. 4 is an explanatory view of a test for confirming the drilling wear suppression effect in the roller with a thrust cage 1 of this embodiment. In this test, the roller axis Or is perpendicular to the flat plate 20 imitating the end surface 4a (FIG. 3) facing the end surface of the roller 2 of the cage pocket 4, and FIG. 3) and the general roller 2A shown in FIG. 3B were rotated by pressing their end faces against the flat plate 20, and the flat end 20 was slid. Table 1 shows the test conditions in this case, and Table 2 shows the specifications of the rollers used in the test. The roller pitch circle diameter was D _m = 48.2 mm, and a load equivalent to D _{m n} 1.8 million was applied. Here, the D _m n, roller pitch diameter Dm [mm] and represents the product of the axial rotation speed n [rpm], commonly used when comparing at different axial受径the severity of the rotational speed of the bearing Index.

  FIG. 5 is a graph showing the results of the drilling wear test. The plot in the figure shows the wear volume of the flat plate 20 at each eccentric amount, and the solid line connects the maximum wear volume at each eccentric amount.

ただし、
ρ：ころの密度[kg ／m3]
Ｄ：ころの直径[m]
Ｌｒ：ころの長さ[m]
Ｄ_m ：ころピッチ円直径[m]
Ｎ：軌道輪の回転速度[rpm]
この時、接触面における接触円半径は以下のようになる。

ただし，ａ：接触円半径[m]
Ｆ：干渉力[N]
Ｒ：ころ／保持器ポケット面接触における等価曲率半径[m]
Ｅ：ころ／保持器ポケット面接触における等価ヤング率[Pa]
したがって、偏芯量δを接触円半径ａに対して、
１≦（δ／ａ）≦１０
とすることで．偏芯が無い場合に比べて耐摩耗性が向上する。なお、接触円はからなずしも真円である必要はなく、楕円であってもよい。楕円の場合は、長軸方向の半径を採用することで、安全側の設計をすることが可能である。
なお、式（１）および式（２）を変形すると，

となり、Ｄ_mｎ１８０万の運転条件下では、接触円の半径は、

となる。ころ直径，ころ長さ，ピッチ円直径などの軸受仕様が異なっても、式（３）に基づいて計算された接触円半径ａに基づいてａ≦δ≦１０ａ[m]とすれば、Ｄ_mｎ１８０万相当までの条件において、摩耗低減効果が望める。 From the test results of FIG. 5, it can be seen that the amount of drilling wear tends to decrease by decentering the end face vertex of the roller 2 from the roller axis Or as in the embodiment. However, even if the amount of eccentricity is too large, the wear volume increases. From this test result, it can be seen that the range of the eccentricity with which the wear resistance is improved is 0.05 to 0.5 mm as compared with the case where there is no eccentricity.
Considering the effect of improving the lubricity due to the movement of the contact circle described above, it is ideal that the contact circles do not overlap with each other (eccentricity ≧ contact circle radius). Here, when the eccentricity range in which the wear resistance is improved is divided by the theoretical contact circle radius and arranged by a parameter of eccentricity (eccentration amount / contact circle radius), the result is as shown in FIG. . According to FIG. 6, it was found that the wear resistance was improved when the eccentricity ratio was in the range of 1 to 10, and the above-mentioned lubricity improvement mechanism (eccentricity ≧ contact circle radius) was proved.
In the thrust roller bearing, the interference force between the roller end surface and the cage pocket surface is equivalent to the centrifugal force acting on the roller by the revolution of the roller.
Theoretically, the roller revolves at half the rotational speed of the race, so the centrifugal force F [N] acting on the roller is as follows. In addition, since the curvature of a roller end surface and the mass of a chamfer part are usually small with respect to roller mass, this is disregarded.

However,
ρ: Roller density [kg / m3]
D: Roller diameter [m]
Lr: Roller length [m]
D _m : Roller pitch circle diameter [m]
N: Rotational speed of race ring [rpm]
At this time, the contact circle radius on the contact surface is as follows.

Where a: contact circle radius [m]
F: Interference force [N]
R: Equivalent radius of curvature at roller / cage pocket surface contact [m]
E: Equivalent Young's modulus in roller / cage pocket surface contact [Pa]
Accordingly, the eccentricity δ is set to the contact circle radius a.
1 ≦ (δ / a) ≦ 10
By doing so. Abrasion resistance is improved compared to the case where there is no eccentricity. Note that the contact circle need not be a perfect circle but may be an ellipse. In the case of an ellipse, it is possible to design on the safe side by adopting the radius in the major axis direction.
In addition, when formula (1) and formula (2) are transformed,

Under the operating conditions of D _{m n} 1.8 million, the radius of the contact circle is

It becomes. Even if the bearing specifications such as the roller diameter, the roller length, and the pitch circle diameter are different, if a ≦ δ ≦ 10a [m] based on the contact circle radius a calculated based on the formula (3), D _m Under conditions up to n1.8 million, wear reduction effect can be expected.

  FIG. 8 shows another embodiment of the present invention. This roller 1 with a thrust cage has an inclined end surface 4a facing the roller end surface of the cage pocket 4, instead of making the end surface of the roller 2 eccentric in the embodiment shown in FIGS. It is. Specifically, the end surface 4a facing the roller end surface of the cage pocket 4 is inclined with respect to the central axis Op of the cage pocket 4, that is, with respect to the roller axis Or in a plan view. The inclination of the end face 4a may be the whole or a part. Other configurations are the same as those in the embodiment of FIGS.

In the embodiment of FIGS. 1 to 3, as the situation where the contact position between the end surface of the roller 2 and the end surface 4 a of the cage pocket 4 changes as the roller rotates, the contact position on the roller 2 side is unchanged, and the cage pocket 4 is assumed in which the contact position on the end face 4a side (the flat plate 20 side in the test of FIG. 4) changes. However, from the viewpoint that the contact position changes, even if the contact position on the end surface 4a side (flat plate 20 side) of the cage pocket 4 is unchanged and the contact position on the roller 2 side changes, Should be equivalent.
In order to confirm this, with respect to the flat plate 20 imitated on the end face 4a of the cage pocket 4, a general roller 2 having no eccentricity is set so that its axial center Or has a vertical posture as shown in FIG. A drilling wear test similar to that in the case of FIG. 4 was performed in the case of sliding in this state and in the case of sliding in an inclined state as shown in FIG. When the roller axis Or is inclined, the contact position on the end face of the roller 2 is a position deviated from the roller axis Or, but moves in the circumferential direction as the roller 2 rotates. The test conditions are the same as in Table 1. In this test, the distance from the center of the contact circle and the apex position of the end face is called an eccentricity equivalent amount. Table 3 shows the amount of eccentricity in this test.

FIG. 10 is a graph showing the results of the drilling wear test. Test items (a) and (b) in the figure correspond to (A) and (B) in FIG. 9, respectively.
As is apparent from the test results of FIG. 10, even if the contact position on the flat plate 20 side imitating the end surface 4a of the cage pocket 4 is unchanged, the amount of wear may be reduced by changing the contact position on the roller 2 side. Recognize. That is, if the contact position relatively changes between the roller 2 and the end face 4a (the flat plate 20 in FIG. 9) of the cage pocket 4, it can be said that drilling wear can be suppressed.

  The embodiment of FIG. 8 embodies this test result and corresponds to the test example of FIG. 9B in which the roller axis Or is inclined with respect to the flat plate 20.

  In the test of FIG. 9, the contact position at the end face of the roller 2 was removed from the roller axis Or by tilting the flat plate 20 imitating the end face 4 a of the cage pocket 4 with respect to the roller 2. For example, the configuration of FIG. 11 may be used. That is, even when the roller 2 is brought into contact with the flat plate 20 in a vertical posture, the convex portion 10 is provided on the flat plate 20 side, that is, the end surface 4a side of the cage pocket 4, and the convex portion 10 at the end surface of the roller 2 is provided. An equivalent effect can be obtained by shifting the contact position from the roller axis Or. In particular, when the end surface of the roller 2 is a flat surface, if the roller 2 and the end surface 4a of the cage pocket 4 are brought into contact with each other at an inclination, the edge contact is caused and the amount of wear increases rapidly. It is preferable to provide the convex portion 10 on the 4a side, or to make the end surface 4a of the cage pocket 4 convex so as to shift the contact position from the roller axis Or.

  12 and 13 show still another embodiment of the present invention. FIG. 12 shows a cross-sectional view of a thrust roller bearing 30 incorporating the roller 1 with a thrust cage of this embodiment. The roller 1 with a thrust cage is disposed between a pair of race rings 31 and 32 that face each other in the axial direction. FIG. 13 shows an enlarged longitudinal sectional view of a part thereof. The roller with thrust retainer 1 of this embodiment has an end surface 4a facing the roller end surface of the cage pocket 4 in place of the configuration in which the end surface of the roller 2 is an eccentric curved surface in the embodiment of FIGS. In a side view, the cage pocket 4 is inclined with respect to the central axis Op, that is, with respect to the roller axis Or. The inclination of the end face 4a may be the whole or a part. Other configurations are the same as those in the embodiment of FIGS.

  Also in this embodiment, as in the case of the embodiment of FIG. 8, the contact position of the end surface 4a of the roller 2 with the end surface 4a of the retainer pocket 4 deviates from the roller axis Or, and the contact position is the roller. Since it changes with the rotation of 2, drilling wear can be suppressed.

  FIG. 14 shows still another embodiment of the present invention. In the embodiment shown in FIG. 8, the roller 1 with a thrust cage has a concave curved surface in plan view, instead of an end surface 4 a facing the roller end surface of the cage pocket 4, and the curvature of the concave curved surface. The center is shifted from the central axis Op of the cage pocket 4. The concave surface of the end surface 4a may be the whole or a part of the end surface 4a. Other configurations are the same as those in the embodiment of FIGS.

  In the case of this embodiment, the two positions deviated from the roller axis Or become the contact position at the end face of the roller 2, and the contact position changes due to the rotation of the roller 2. Therefore, as in the embodiment of FIG. Drilling wear can be suppressed.

  FIG. 15 shows still another embodiment of the present invention. In the embodiment shown in FIG. 13, the roller with a thrust cage 1 has a concave curved surface as viewed from the side, instead of a sloped end surface 4a facing the roller end surface of the cage pocket 4, and the center of curvature of the concave curved surface. Is offset from the central axis Op of the cage pocket 4. The concave surface of the end surface 4a may be the whole or a part of the end surface 4a. Other configurations are the same as those in the embodiment of FIGS.

  Also in this embodiment, the two positions deviated from the roller axis Or are the contact positions at the end face of the roller 2, and the contact positions change due to the rotation of the rollers 2, so that the same as in the embodiment of FIG. Drilling wear can be suppressed.

  16 to 21 show still another embodiment of the present invention. This embodiment is a cage 3 incorporated in a thrust roller bearing 30 as shown in FIG. 12, and is an end surface 4a (here, a diameter) facing the end surface of the needle roller 2 held in each pocket 4 thereof. The convex part 10 demonstrated in FIG. 11 is provided in the direction outer side end surface. One or a plurality of the convex portions 10 may be provided. Further, the convex portion 10 may be formed integrally with the cage 3 or may be formed separately from the end surface 4a.

  As shown in FIG. 16, when the end surface of the roller 2 is a flat surface, the end surface 4a of the cage pocket 4 is inclined as in the embodiment of FIGS. 8 and 13 from the viewpoint of avoiding the edge contact described above. Not desirable. Therefore, in this embodiment, the convex portion 10 is provided on the end surface 4 a of the cage pocket 4. In this case, the convex portion 10 is provided at a position where the apex position deviates from the roller axis Or. Thereby, the contact position with the said convex part 10 in the end surface of the roller 2 turns into the position remove | deviated from the roller axial center Or, and the contact position changes with rotation of the roller 2. As shown in FIG. As a result, drilling wear can be suppressed as in other embodiments. Here, the end surface of the roller 2 is a flat surface, but the convex portion 10 can also be provided when the end surface of the roller 2 is a curved surface.

  By the way, the shape of the cage pocket 4 is generally set to a size larger than the size of the roller 2. Therefore, the roller 2 can move relative to the pocket 4 within the gap during the operation of the bearing. If it is intended to improve the lubricity of the contact portion by the relative change in the contact position between the end surface of the roller 2 and the end surface 4a of the cage pocket 4 as described above, the roller 2 within the gap of the pocket 4 is used. Even if the position changes, the distance between the roller end surface and the cage pocket end surface and the axial center Or is preferably in the range of a ≦ δ ≦ 10a [m] described above.

In the thrust roller bearing 30 as shown in FIG. 12, the distance that the roller 2 and the cage pocket 4 can move relative to each other in the circumferential direction (revolution direction of the roller 2) coincides with the circumferential clearance δ _pc (FIG. 16). On the other hand, the distance that the roller 2 and the cage pocket 4 can move relative to each other in the axial direction of the cage 3 varies depending on the guide type of the cage 3. In general, the cage 3 has two types of guide forms, a rolling element guide form schematically shown in FIG. 17 and a raceway guide form schematically shown in FIG. 17 shows a cross-sectional view taken along the line AA in FIG. A rolling element guide type retainer 3 shown in FIG. 17 is, for example, a box-shaped structure composed of a pair of retainer constituting plates 3A and 3B overlapping in the axial direction, and each retainer constituting plate 3A is opposed in the axial direction. , 3B, pockets 4 are constituted by pocket holes 4A, 4B, and rollers 4A, 4B have claws (not shown) for preventing the rollers from dropping off at the end surfaces on the circumferential side.

In the rolling element guide type cage 3 shown in FIG. 17, the axial movement of the cage 3 is limited by the rollers 2 that are rolling elements. On the other hand, in the raceway guide type cage 3 shown in FIG. 18, the axial movement of the cage 3 is limited by the raceways 31 and 32. Therefore, the distance δ _pa in which the roller 2 and the cage 3 can move relative to each other in the axial direction becomes a clearance (FIG. 17) between the roller 2 and the cage 3 in the rolling element guide type, and between the cage 3 and the bearing ring guide type. It becomes a clearance (FIG. 18) between the race rings 31 and 32.

ただし、δ₁ ，δ₂ ，δ_pa，δ_pcはｍ単位の値である。 Now, with the roller 2 placed at the center position of the cage pocket 4 as shown in FIG. 19, the vertex position of the convex portion 10 provided on the end face 4a of the pocket 4 in FIG. 16 is held from the pocket center axis Op. The axial distance of the device 3 is δ ₁ as shown in FIG. 20, and the circumferential distance is δ ₂ as shown in FIG. At this time, if the apex position of the convex portion 10 is set in the range shown below, the above-described drilling wear reduction effect can be obtained.

However, δ ₁ , δ ₂ , δ _pa , δ _pc are values in m units.

  In the embodiment shown in FIGS. 16 to 21, the contact portion between the end surface of the roller 2 and the end surface 4 a of the cage pocket 4 in the thrust roller bearing 30 has been described, but from the viewpoint of improving the lubricity of the contact portion. The configurations of the embodiments of FIGS. 16 to 21 can also be applied to the cage 13 incorporated in the radial roller bearing 40 shown in FIG. In the radial roller bearing 40 of FIG. 22, the cage 13 is disposed between the inner and outer race rings 41 and 42 that are concentrically arranged with respect to the axis O, and the rollers 2 are arranged at a plurality of locations in the circumferential direction. A plurality of pockets 14 that are held in parallel with the center O are provided.

In this case, the axial gap δ _pa and the axial distance δ _{1 in} the thrust roller bearing retainer 3 of the embodiment shown in FIGS. This corresponds to the radial gap δ _pa and the radial distance δ ₁ . The circumferential clearance δ _pc and the circumferential distance δ ₂ in the thrust roller bearing retainer 3 are the same in the radial roller bearing retainer 13. By such replacement, the formulas (4) and (5) in the thrust roller bearing retainer 3 can be directly applied to the radial roller bearing retainer 13 to obtain the above-described drilling wear reduction effect.

  When the cage 13 is a rolling element guide type, not only as a radial roller bearing 40 having raceways 41 and 42 as shown in FIG. 22, but also as a radial cage comprising rollers 2 and cage 13 as shown in FIG. The same configuration as that of the embodiment shown in FIGS.

  In recent years, transmissions for automobiles, particularly automatic transmissions (AT), which are mainstream, have been increasingly multistaged from the viewpoint of improving fuel efficiency, and the rotational speeds of the gears and bearings of the planetary gear mechanism used have been increased. . Similarly, in a hybrid vehicle, the required rotational speed of the bearing tends to increase due to the high speed rotation of the motor and the generator. In roller bearings used in these mechanisms, particularly thrust roller bearings, as a result of an increase in rotational speed, a large load (centrifugal force) is applied to the end surface contact portion. Therefore, wear countermeasures at the end surface contact portion are essential. . As the thrust roller bearing used in such a planetary gear mechanism, a multi-speed transmission for automobiles, a transmission mechanism for hybrid automobiles, etc., the effect of suppressing drilling wear at the end surface contact portion is improved by applying the above-described embodiments. be able to. Specific examples thereof will be described with reference to FIGS.

FIG. 24 shows an example of a planetary gear mechanism to which this roller with cage is applied. The planetary gear mechanism 50 includes a plurality of planetary gears 53 meshing with the sun gear 51 and the internal gear 52, and a carrier 54 that is rotatable about the coaxial axis with the sun gear 51 and the internal gear 52. It is provided so as to be freely rotatable. The internal gears 52 are fixed to each other via a support frame 57 on the central shaft 56.
Each planetary gear 53 is rotatably supported on the outer periphery of the support shaft 55 via two rollers 11A with radial cages arranged in the axial direction. Further, the roller 1 with a thrust retainer is interposed between the carrier 54 and the sun gear 51 and between the carrier 54 and the support frame 57, and on the surface of the support frame 57 opposite to the carrier 54. A roller 1A with a thrust retainer interposed between other members (not shown) is provided.
For example, when the planetary gear mechanism is rotated with the sun gear 51 as an input unit and the internal gear 52 is in a non-rotatable state, a rotational output decelerated from the carrier 54 is obtained.

  In the planetary gear mechanism 50 having the above-described configuration, the roller with thrust retainer 1A and the roller with radial retainer 11A are replaced with the roller with thrust retainer 1 according to any one of the embodiments described above with reference to FIGS. A roller 11 with a cage is used.

  According to the planetary gear mechanism of this configuration, the roller with thrust retainer 1 and the roller with radial retainer 11 according to any one of the above embodiments are used as the roller with thrust retainer 1A and the roller with radial retainer 11A used in each part. Therefore, the roller 1A with the thrust cage and the roller 11A with the radial cage can obtain the effect of suppressing the drilling wear at the end surface contact portion, and the planetary gear mechanism is excellent in durability.

FIG. 25 shows an example of an automobile multi-stage transmission to which the roller with cage is applied. In the multi-stage transmission 60 for an automobile, the rotation of the input shaft 61 is decelerated by the first-stage transmission 64 and transmitted to the intermediate shaft 62, and the rotation of the intermediate shaft 62 is further decelerated by the second-stage transmission 65. Is transmitted to the output shaft 63.
A planetary gear mechanism similar to the planetary gear mechanism 50 shown in FIG. 24 is used for the first-stage transmission 64. Similarly to the example of FIG. 24, the roller 1 with the thrust cage in any of the above embodiments. And the roller 11 with a radial cage is used.
The second-stage transmission 65 includes a front sun gear 51A, a rear sun gear 51B, an internal gear 52, a plurality of planetary gears 53, and a carrier (not shown) that supports the planetary gears 53. Also in the second-stage transmission, the roller 11 with the radial cage according to any one of the above embodiments is used at a location where the planetary gear 53 is supported with respect to the carrier via a support shaft (not shown). And the roller 1 with a thrust holder which concerns on one of the said embodiments is used before and behind a carrier.

  Also in the multistage transmission for an automobile having this configuration, since the roller with thrust retainer 1 and the roller with radial retainer 11 according to any one of the above-described embodiments are used, the effect of suppressing drilling wear at the end surface contact portion can be improved. And a planetary gear mechanism with excellent durability.

  FIG. 26 shows an example of a power transmission mechanism for a hybrid vehicle to which this roller with cage is applied. In this hybrid vehicle power transmission mechanism 70, rotation from an engine (not shown) that is an internal combustion engine is input from an input shaft 71, and a charger (generator) 73, a power split mechanism 74, a motor 75, and 2. It is transmitted to the output shaft 72 via the stepped reduction mechanism 76 and transmitted to the propeller shaft (not shown). A planetary gear mechanism is used for the power split mechanism 74 and the speed reduction mechanism 76. Between the planet gear 53 and the support shafts provided on the carriers 54B and 54C, the roller 11 with a radial cage according to any one of the above embodiments. Is used. Further, the roller with thrust retainer 1 according to any one of the above embodiments is used for thrust support of the carriers 54B and 54C.

  Also in the power transmission mechanism for a hybrid vehicle having this configuration, since the roller with thrust retainer 1 and the roller with radial retainer 11 according to any one of the above-described embodiments are used, the effect of suppressing drilling wear at the end surface contact portion is increased. And a power transmission mechanism for a hybrid vehicle with excellent durability.

It is sectional drawing of the roller with a thrust holder which concerns on one Embodiment of this invention. It is a partial enlarged plan view of the roller with the same thrust cage. (A) is a partial expanded horizontal sectional view of the roller with the same thrust cage, and (B) is a partially enlarged plan view of a comparative example. It is explanatory drawing of the test of the abrasion suppression effect of the roller with the same thrust holder. It is a graph of the test result. It is a graph which shows the relationship between the eccentricity and the wear volume in the roller with the same thrust cage. It is explanatory drawing of the contact circle movement in the roller with the same thrust retainer. It is a partial enlarged plan view of a roller with a thrust cage according to another embodiment of the present invention. It is explanatory drawing of the test of the abrasion suppression effect of the roller with the same thrust holder. It is a graph of the test result. It is explanatory drawing of the test of the abrasion suppression effect by a convex part. It is sectional drawing of the thrust roller bearing which concerns on other embodiment of this invention. It is a partial expanded sectional view of the thrust roller bearing. It is a partial expanded horizontal sectional view of the roller with a thrust retainer which concerns on other embodiment of this invention. It is a partial expanded sectional view of the thrust roller bearing which concerns on other embodiment of this invention. It is a partial expanded horizontal sectional view of the thrust roller bearing which concerns on other embodiment of this invention. It is explanatory drawing of the axial direction clearance gap between holder | retainer pocket places when the holder | retainer of the same thrust roller bearing is a rolling element guide type. It is explanatory drawing of the axial direction clearance gap between holder | retainer pocket places when the holder | retainer of the same thrust roller bearing is a bearing ring guide type. It is explanatory drawing of the convex part position in the holder | retainer pocket in the thrust roller bearing. It is explanatory drawing of the axial direction distance of the convex part vertex in the holder | retainer pocket in the same thrust bearing. It is explanatory drawing of the circumferential direction distance of the convex part vertex in the holder | retainer pocket in the same thrust bearing. It is a top view of the radial roller bearing which concerns on other embodiment of this invention. It is a top view of the roller with a radial cage concerning other embodiments of this invention. It is a fragmentary sectional view of the planetary gear mechanism concerning one embodiment of this invention. It is explanatory drawing of the conceptual structure of the multistage transmission for motor vehicles based on one Embodiment of this invention. It is explanatory drawing of the conceptual structure of the power transmission mechanism for hybrid vehicles which concerns on one Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Roller with a thrust retainer 2 ... Roller 3, 13 ... Retainer 4, 14 ... Pocket 4a ... Pocket end surface 10 ... Convex part 11 ... Roller with radial retainer 30 ... Thrust roller bearing 31, 32 ... Race ring 40 ... Radial Roller bearings 41, 42 ... raceway ring 50 ... planetary gear mechanism 60 ... automotive multi-stage transmission 70 ... hybrid vehicle power transmission mechanism Or ... roller shaft center delta ... eccentricity Op ... pocket central axis delta _pc ... circumferential clearance δ _pa … Axial clearance (radial clearance)
δ ₁ Axial distance (radial distance)
δ ₂ ... Circumferential distance

Claims (15)

In a roller with a cage comprising a plurality of rollers and a cage provided with a plurality of pockets for holding each of these rollers,
A roller with a cage, wherein one or a plurality of contact positions between an end face of the roller and an end face of the pocket facing the end face of the roller are shifted from an axial center of the roller.   The retainer according to claim 1, wherein a part or the whole of the pocket end surface facing the roller end surface is inclined with respect to a central axis of the pocket, whereby the contact position is shifted from the axis of the roller. Time.   2. The contact position is shifted from the axial center of the roller according to claim 1, wherein a part or the whole of the pocket end surface facing the roller end surface is curved, and the center of curvature is shifted from the central axis of the pocket. Roller with cage.   The roller with a retainer according to claim 1, wherein a part or the whole of the roller end surface is curved, and the center of curvature is shifted from the roller axis to shift the contact position from the axis of the roller. In a roller with rolling element guide type thrust retainer provided between a pair of raceways facing each other in the axial direction and provided with a plurality of pockets for holding the rollers at a plurality of locations in the circumferential direction,
Provided on the end face of the pocket facing the end face of the roller is a convex part or a plurality of convex parts, part or all of which is curved, an end face of the roller, and an end face of the pocket facing the roller end face Shift the contact position of the roller from the axis of the roller,
The clearance in the bearing axial direction between the pocket and the roller is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the axial direction from the central axis of the pocket at the apex position of the convex portion When the distance is δ ₁ m and the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m,

A roller with a thrust cage, characterized by
However,

δ _pa : Axial clearance between roller and cage pocket (for rolling element guide type cage) [m]
δ _pc : circumferential clearance between roller and cage pocket [m]
ρ: Roller density [kg / m ³ ]
D: Roller diameter [m]
Lr: Roller length [m]
D _m : Roller pitch circle diameter [m]
N: Rotational speed of race ring [rpm]
R: Equivalent radius of curvature at roller / cage pocket surface contact [m]
E: Equivalent Young's modulus in roller / cage pocket surface contact [Pa]
It is. A roller with guide ring type thrust retainer which is disposed between a pair of bearing rings facing each other in the axial direction and has a plurality of pockets for holding the rollers at a plurality of locations in the circumferential direction. On the end face facing the end face of the roller, a convex part or a plurality of convex parts having a curved surface or a part thereof are provided, and contact between the end face of the roller and the end face of the pocket facing the end face of the roller Shift the position from the axis of the roller,
The clearance in the bearing axial direction between the cage and the bearing ring is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the axial distance from the central axis of the pocket at the apex position of the convex portion Δ ₁ m, the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m, and the contact circle radius at the contact between the roller end surface and the cage pocket surface is am.

A roller with a thrust cage, characterized by Rolling element guide type radial holding that is arranged between inner and outer races that are concentrically arranged with respect to the shaft center and that is provided with a plurality of pockets that hold the rollers in parallel with the shaft center at a plurality of locations in the circumferential direction. A roller with a container, on the end face of the pocket facing the end face of the roller, provided with a convex part or a plurality of convex parts partly or entirely of a curved surface, the end face of the roller, and this roller end face The position of contact with the end face of the pocket opposite to the center is shifted from the axial center of the roller,
The radial clearance between the pocket and the roller is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the radial distance from the central axis of the pocket at the apex position of the convex portion is When δ ₁ m, the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m, and the contact circle radius at the contact between the roller end surface and the cage pocket surface is am,

A roller with a radial cage, characterized by Radial holding of the bearing ring guide type that is arranged between inner and outer races that are concentrically arranged with respect to the shaft center and that is provided with a plurality of pockets that hold the rollers parallel to the shaft center at a plurality of locations in the circumferential direction. A roller with a container, on the end face of the pocket facing the end face of the roller, provided with a convex part or a plurality of convex parts partly or entirely of a curved surface, the end face of the roller, and this roller end face The position of contact with the end face of the pocket opposite to the center is shifted from the axial center of the roller,
The radial clearance between the cage and the race is δ _pa m, the circumferential clearance between the pocket and the roller is δ _pc m, and the radial distance from the central axis of the pocket at the apex position of the convex portion is When δ ₁ m, the circumferential distance from the central axis of the pocket at the apex position of the convex portion is δ ₂ m, and the contact circle radius am in contact between the roller end face and the cage pocket surface,

A roller with a radial cage, characterized by In claim 5 or 6,
The contact circle radius a [m] in the roller / cage pocket surface contact is

When the distance from the pocket central axis of the convex vertex position,

A roller with a thrust cage, characterized by
However:
δ _pa : Axial clearance between roller and cage pocket (for rolling element guide type cage) [m]
Axial clearance between cage and raceway (for raceway guide type cage) [m]
δ _pc : circumferential clearance between roller and cage pocket [m]
ρ: Roller density [kg / m ³ ]
D: Roller diameter [m]
Lr: Roller length [m]
D _m : Roller pitch circle diameter [m]
R: Equivalent radius of curvature at roller / cage pocket surface contact [m]
E: Equivalent Young's modulus in roller / cage pocket surface contact [Pa]
It is. The contact circle radius a [m] in the roller / cage pocket surface contact according to claim 4,

When
The amount of deviation δ [m] between the center of curvature of a part or the whole of the roller end surface and the roller axis is expressed by a ≦ δ ≦ 10a
A roller with a thrust cage, characterized by
However,
ρ: Roller density [kg / m ³ ]
D: Roller diameter [m]
Lr: Roller length [m]
D _m : Roller pitch circle diameter [m]
R: Equivalent radius of curvature at roller / cage pocket surface contact [m]
E: Equivalent Young's modulus in roller / cage pocket surface contact [Pa]
It is. 5. The contact circle radius in the roller / cage pocket surface contact is a [m], a part or all of the roller end surface is curved, and the center of curvature is shifted from the roller axis, and the amount of shift δ is a ≦ δ ≦ 10a
Roller with a radial cage, characterized by incorporating a roller.   A roller bearing comprising the roller with a retainer according to any one of claims 1 to 10.   A planetary gear mechanism in which the roller with a retainer according to any one of claims 1 to 10 is incorporated.   11. A multi-stage transmission for an automobile, wherein the roller with a thrust retainer according to claim 1 is incorporated.   A power transmission mechanism for a hybrid vehicle, wherein the roller with a thrust cage according to any one of claims 1 to 10 is incorporated.

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