JP5499451B2 - Roller bearing of planetary gear mechanism - Google Patents

Roller bearing of planetary gear mechanism Download PDF

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JP5499451B2
JP5499451B2 JP2008224629A JP2008224629A JP5499451B2 JP 5499451 B2 JP5499451 B2 JP 5499451B2 JP 2008224629 A JP2008224629 A JP 2008224629A JP 2008224629 A JP2008224629 A JP 2008224629A JP 5499451 B2 JP5499451 B2 JP 5499451B2
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planetary gear
cage
roller bearing
rollers
peripheral surface
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JP2010060009A5 (en
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勝彦 千原
基司 河村
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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Description

この発明は遊星歯車機構のころ軸受に関する。   The present invention relates to a roller bearing for a planetary gear mechanism.

遊星歯車機構において、遊星歯車（プラネタリギヤ）は、キャリアに組み付けられる中心軸の外周にころ軸受を介して回転可能に支持される。そして、遊星歯車は、太陽歯車（サンギヤ）とリングギヤとの相互に噛み合った状態で、中心軸回りに自転しながら太陽歯車回りに公転するようになっている。
また、ころ軸受（針状ころ軸受も含む）は、遊星歯車の中心孔と中心軸との間に組み込まれる複数のころと、これら複数のころを転動可能に保持する保持器とを備えている。
なお、遊星歯車機構のころ軸受としては、例えば、特許文献１に開示されている。
特開平８−３１２６５０号公報 In the planetary gear mechanism, the planetary gear (planetary gear) is rotatably supported on the outer periphery of the central shaft assembled to the carrier via a roller bearing. The planetary gear revolves around the sun gear while rotating around the central axis while the sun gear (sun gear) and the ring gear mesh with each other.
The roller bearing (including the needle roller bearing) includes a plurality of rollers incorporated between the center hole and the center shaft of the planetary gear, and a cage that holds the plurality of rollers in a rollable manner. Yes.
In addition, as a roller bearing of a planetary gear mechanism, it is disclosed by patent document 1, for example.
JP-A-8-31650

ところで、前記した従来の遊星歯車機構のころ軸受において、保持器の外径寸法は、遊星歯車の中心孔の内径寸法よりも僅かに小さく設定され、同保持器の内径寸法は、中心軸の外径寸法よりも大きく設定される。そして、保持器の内周面と中心軸の外周面との間の隙間寸法が、保持器の外周面と遊星歯車の中心孔の内周面との間の隙間寸法よりも大きくなっている。
このため、遊星歯車が中心軸回りに自転しながら太陽歯車回りに公転する際の遠心力を保持器が受けると、その遠心力が作用する方向へ保持器が移動し、保持器の外周面の片側（保持器の移動方向の外周面の前側）が遊星歯車の中心孔の内周面に接触する。これによって、保持器の摺動抵抗が大きくなってトルク損失をまねく恐れがある。
また、ころ軸受の保持器が、遠心力を受けて自身の質量で楕円形に変形した場合には、保持器の外周面の片側が遊星歯車の中心孔の内周面に面接触するため、保持器の摺動抵抗が一層大きくなる。 By the way, in the above-described conventional planetary gear mechanism roller bearing, the outer diameter of the cage is set slightly smaller than the inner diameter of the center hole of the planetary gear, and the inner diameter of the cage is outside the center shaft. It is set larger than the diameter dimension. The gap dimension between the inner circumferential surface of the cage and the outer circumferential surface of the central shaft is larger than the gap dimension between the outer circumferential surface of the cage and the inner circumferential surface of the center hole of the planetary gear.
For this reason, when the cage receives the centrifugal force when the planetary gear rotates around the central axis and revolves around the sun gear, the cage moves in the direction in which the centrifugal force acts, and the outer peripheral surface of the cage One side (the front side of the outer peripheral surface in the moving direction of the cage) contacts the inner peripheral surface of the center hole of the planetary gear. As a result, the sliding resistance of the cage increases, which may cause torque loss.
Also, when the cage of the roller bearing is subjected to centrifugal force and deformed into an oval shape with its own mass, one side of the outer circumferential surface of the cage is in surface contact with the inner circumferential surface of the center hole of the planetary gear, The sliding resistance of the cage is further increased.

この発明の目的は、前記問題点に鑑み、保持器の外周面が遊星歯車の中心孔に接触することを阻止して保持器の摺動抵抗を低減することができる遊星歯車機構のころ軸受を提供することである。   In view of the above problems, an object of the present invention is to provide a planetary gear mechanism roller bearing capable of reducing the sliding resistance of the cage by preventing the outer peripheral surface of the cage from contacting the center hole of the planetary gear. Is to provide.

前記課題を解決するために、この発明の請求項１に係る遊星歯車機構のころ軸受は、遊星歯車機構の遊星歯車の中心孔と中心軸との間に組み込まれる複数のころと保持器とを備えたころ軸受であって、
前記保持器は、軸方向に所定間隔で配置された第１、第２の円環部と、これら第１、第２の円環部を連結すると共に、前記複数のころをそれぞれ個別に収納する複数のポケットを区画形成する複数の柱部とを備え、
前記保持器の内周面と前記中心軸の外周面との間の隙間寸法をＡとし、前記保持器の外周面と前記遊星歯車の中心孔の内周面との間の隙間寸法をＢとしたときに、「Ａ＜Ｂ」の関係となるように設定され、
前記ポケットの軸方向両端部の前記第１、第２の円環部の対向端面には、前記複数のころのピッチ円（ＰＣＤ）と、前記ころの両端面の径方向との交差部である前記ころの両端面中心部にそれぞれ接触して前記ころを転動案内する先尖り状の突起が形成されていることを特徴とする。 In order to solve the above problems, a roller bearing of a planetary gear mechanism according to claim 1 of the present invention includes a plurality of rollers and a cage incorporated between a center hole and a center shaft of a planetary gear of the planetary gear mechanism. A roller bearing provided,
The retainer connects the first and second annular portions arranged at predetermined intervals in the axial direction and the first and second annular portions, and individually accommodates the plurality of rollers. A plurality of pillars that define a plurality of pockets;
The clearance dimension between the inner peripheral surface of the cage and the outer peripheral surface of the central shaft is A, and the clearance dimension between the outer peripheral surface of the cage and the inner peripheral surface of the center hole of the planetary gear is B. Is set to have a relationship of “A <B”,
Opposite end surfaces of the first and second annular portions at both axial end portions of the pocket are intersections between pitch circles (PCD) of the plurality of rollers and radial directions of both end surfaces of the rollers. wherein the above pointed like projections that rolling guide said this filtrate to come in contact on both end surface center portion of the front Symbol rollers are formed.

前記構成によると、遊星歯車が中心軸回りに自転しながら太陽歯車回りに公転する際の遠心力を保持器が受けると、その遠心力が作用する方向へ保持器が移動する。この際、保持器が移動する方向の後側に位置する保持器の内周面の後側が中心軸の外周面に接触（当接）することによって保持器の移動が止められる。
このため、保持器の外周面の前側（移動方向の前側）が遊星歯車の中心孔の内周面に接触することを阻止することができ、保持器の摺動抵抗を小さく抑えることができる。
すなわち、保持器の内周面の周速は、同保持器の外周面の周速よりも遅いため、従来の保持器の外周面が遊星歯車の中心孔の内周面に接触する場合と比べ、保持器の摺動抵抗を小さく抑えることができ、この結果、保持器の摺動抵抗によるトルク損失を抑制することができる。
また、ポケットの軸方向両端部の第１、第２の円環部の対向端面にそれぞれ形成された先尖り状の突起が、複数のころのピッチ円（ＰＣＤ）と、ころの両端面の径方向との交差部であるころの両端面中心部に接触してころを転動案内することができるため、ポケットの軸方向両端部とのころの両端面との間の摺動抵抗を低減することができ、保持器の摺動抵抗によるトルク損失の低減や摩耗低減等に効果が大きい。 According to the above configuration, when the cage receives a centrifugal force when the planetary gear rotates around the central axis and revolves around the sun gear, the cage moves in a direction in which the centrifugal force acts. At this time, the movement of the cage is stopped when the rear side of the inner circumferential surface of the cage located on the rear side in the direction in which the cage moves contacts (contacts) the outer circumferential surface of the central shaft.
For this reason, it can prevent that the front side (front side of a moving direction) of the outer peripheral surface of a cage contacts the inner peripheral surface of the center hole of a planetary gear, and can suppress the sliding resistance of a cage small.
That is, since the peripheral speed of the inner peripheral surface of the cage is slower than the peripheral speed of the outer peripheral surface of the cage, the outer peripheral surface of the conventional cage is compared with the case where the outer peripheral surface of the cage contacts the inner peripheral surface of the center hole of the planetary gear. Thus, the sliding resistance of the cage can be kept small, and as a result, torque loss due to the sliding resistance of the cage can be suppressed.
The first axial end portions of the pocket, the second annular portion previously pointed shaped projections made form respectively on opposite end surfaces of, the pitch circle of the plurality of rollers and (PCD), the end surfaces of the roller The roller can be guided by rolling in contact with the center of both ends of the roller , which intersects the radial direction , reducing the sliding resistance between the both ends of the pocket in the axial direction of the pocket. This is effective in reducing torque loss and wear due to the sliding resistance of the cage.

請求項２に係る遊星歯車機構のころ軸受は、請求項１に記載の遊星歯車機構のころ軸受であって、
先尖り状の突起は、保持器の第１、第２の円環部及び複数の柱部の板厚寸法と同等の径方向の板厚寸法を有し、径方向視で先尖り状に形成されていることを特徴とする。 The roller bearing of the planetary gear mechanism according to claim 2 is the roller bearing of the planetary gear mechanism according to claim 1,
The pointed protrusion has a radial thickness equivalent to the thickness of the first and second annular portions and the plurality of pillars of the cage, and is formed in a pointed shape when viewed in the radial direction. It is characterized by being.

請求項３に係る遊星歯車機構のころ軸受は、請求項１又は２に記載の遊星歯車機構のころ軸受であって、
保持器の複数の柱部は、複数のころのピッチ円（ＰＣＤ）寸法よりも小径の軸方向中間部と、前記複数のころのピッチ円寸法よりも大径の軸方向両端部と、これら軸方向中間部及び軸方向両端部を連結する傾斜連結部とを有し、
前記軸方向両端部の端縁部には、段差状をなす小径の肩部がそれぞれ形成され、これら両肩部は、前記第１、第２の円環部と同径をなして一体に接続され、
前記第１、第２の円環部の軸方向端部には、径方向中心側へ曲げられた折曲縁が形成され、この折曲縁の先端が中心軸の外周面に接触可能とされていることを特徴とする。 Roller bearing according to claim 3 in engagement Ru planetary gear mechanism is a roller bearing of the planetary gear mechanism according to claim 1 or 2,
The plurality of column portions of the cage include an axial intermediate portion having a diameter smaller than the pitch circle (PCD) size of the plurality of rollers, axial end portions having a diameter larger than the pitch circle size of the plurality of rollers, An intermediate connecting portion and an inclined connecting portion for connecting both axial end portions,
A small-diameter shoulder having a step shape is formed at each end edge of the both axial ends, and both the shoulders are integrally connected with the same diameter as the first and second annular portions. And
A bent edge that is bent toward the radial center is formed at the axial ends of the first and second annular portions, and the tip of the bent edge can contact the outer peripheral surface of the central shaft. It is characterized by.

前記構成によると、遠心力が作用する方向へ保持器が移動する際には、保持器の折曲縁の先端が中心軸の外周面に接触するため、中心軸の外周面に対する保持器の接触面積が折曲縁の先端で小さく抑えることができる。この結果、低トルク化、摩耗低減等に効果が大きい。   According to the above configuration, when the cage moves in the direction in which the centrifugal force acts, the tip of the bent edge of the cage comes into contact with the outer peripheral surface of the central axis. The area can be kept small at the end of the bent edge. As a result, it is highly effective in reducing torque and reducing wear.

この発明を実施するための最良の形態について実施例にしたがって説明する。   The best mode for carrying out the present invention will be described in accordance with an embodiment.

〔実施例１〕
この発明の実施例１を図面にしたがって説明する。
図１はこの発明の実施例１に係る遊星歯車機構を簡略化して示す説明図である。図２は遊星歯車と中心軸との間にころ軸受が組み付けられた状態を示す縦断面図である。図３は保持器を示す横断面図である。図４は保持器を示す縦断面図である。図５は保持器のポケットを外径側から示す展開図である。図６は遠心力が作用する方向へ保持器が移動した状態を示す説明図である。 [Example 1]
A first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is an explanatory diagram showing a simplified planetary gear mechanism according to Embodiment 1 of the present invention. FIG. 2 is a longitudinal sectional view showing a state in which the roller bearing is assembled between the planetary gear and the central shaft. FIG. 3 is a cross-sectional view showing the cage. FIG. 4 is a longitudinal sectional view showing the cage. FIG. 5 is a developed view showing the pocket of the cage from the outer diameter side. FIG. 6 is an explanatory view showing a state in which the cage is moved in the direction in which the centrifugal force acts.

図１に示すように、自動車のオートマチックトランスミッションに採用される遊星歯車機構１は、周知のように、太陽歯車（サンギヤ）２、リングギヤ３及び複数（図１では３つ）の遊星歯車（プラネタリギヤ）４を備えて構成される。
図２に示すように、遊星歯車４は、キャリア８に組み付けられる中心軸６の外周にころ軸受（針状ころ軸受も含む）１０を介して回転可能に支持される。
そして、遊星歯車４は、太陽歯車２とリングギヤ３との相互に噛み合った状態で、中心軸６回りに自転しながら太陽歯車２回りに公転するようになっている。 As shown in FIG. 1, a planetary gear mechanism 1 employed in an automatic transmission of an automobile includes a sun gear (sun gear) 2, a ring gear 3, and a plurality of (three in FIG. 1) planetary gears (planetary gears). 4 is configured.
As shown in FIG. 2, the planetary gear 4 is rotatably supported on the outer periphery of the center shaft 6 assembled to the carrier 8 via a roller bearing (including a needle roller bearing) 10.
The planetary gear 4 revolves around the sun gear 2 while rotating around the central axis 6 while the sun gear 2 and the ring gear 3 mesh with each other.

ころ軸受１０は、遊星歯車４の中心孔５の内周面を外輪軌道面とし、中心軸６の外周面を内輪軌道として、これら両者間の環状の隙間に組み込まれた複数のころ１１と、これら複数のころ１１を転動可能に保持する保持器２０とを備えている。   The roller bearing 10 includes a plurality of rollers 11 incorporated in an annular clearance between the planetary gear 4 and the inner peripheral surface of the center hole 5 as an outer ring raceway surface, and the outer peripheral surface of the center shaft 6 as an inner ring raceway. A cage 20 that holds the plurality of rollers 11 in a rollable manner is provided.

図４と図５に示すように、保持器２０は、軸方向に所定間隔を隔てる第１、第２の円環部２２、２４と、これら第１、第２の円環部２２、２４を連結すると共に、複数のころ１１をそれぞれ個別に収納する複数のポケット２３を区画形成する複数の柱部３０とを一体に備えている。
また、この実施例１においては、図４に示すように、保持器２０の第１、第２の円環部２２、２４の軸方向端部には、径方向の中心側へ曲げられた折曲縁２１、２３が形成され、折曲縁２１、２３の先端（内径端）が中心軸６の外周面に接触可能とされている。
なお、保持器２０は、鋼板のプレス加工、切削加工、合成樹脂材の射出成形等によって形成される。 As shown in FIGS. 4 and 5, the cage 20 includes first and second annular portions 22 and 24 that are spaced apart from each other in the axial direction, and the first and second annular portions 22 and 24. A plurality of column portions 30 are provided integrally with the plurality of pockets 23 that are connected to each other and that respectively define a plurality of pockets 23 for individually storing the plurality of rollers 11.
Further, in the first embodiment, as shown in FIG. 4, the axial ends of the first and second annular portions 22 and 24 of the cage 20 are bent toward the center in the radial direction. Curved edges 21 and 23 are formed, and the tips (inner diameter ends) of the bent edges 21 and 23 can contact the outer peripheral surface of the central shaft 6.
The cage 20 is formed by pressing or cutting a steel plate, injection molding of a synthetic resin material, or the like.

また、図４に示すように、保持器２０の複数の柱部３０は、複数のころ１１のピッチ円（ＰＣＤ）寸法よりも小径の軸方向中間部３１と、複数のころ１１のピッチ円寸法よりも大径の軸方向両端部３２、３３と、これら軸方向中間部３１及び軸方向両端部３２、３３を連結する傾斜連結部３６、３７とを有している。
さらに、軸方向両端部３２、３３の端縁部には、段差状をなす小径の肩部３４、３５がそれぞれ形成され、これら両肩部３４、３５は、第１、第２の円環部２２、２４と同径をなして一体に接続されている。
また、図３〜図５に示すように、各ポケット２５内のころ１１を抜け止めするために、隣接する柱部３０の相対する面の軸方向中間部３１及び軸方向両端部３２、３３の端面には、ポケット２５内に向けて対向状に突出する抜止爪４０、４１がそれぞれ突出されている。 As shown in FIG. 4, the plurality of column portions 30 of the cage 20 include an axial intermediate portion 31 having a smaller diameter than the pitch circle (PCD) size of the plurality of rollers 11 and the pitch circle size of the plurality of rollers 11. And both end portions 32 and 33 in the axial direction having larger diameters and inclined connection portions 36 and 37 for connecting the intermediate portion 31 in the axial direction and both end portions 32 and 33 in the axial direction.
Further, shoulders 34 and 35 having a small diameter are formed on the edge portions of the axial end portions 32 and 33, respectively, and these shoulder portions 34 and 35 are formed by the first and second annular portions, respectively. 22 and 24 have the same diameter and are integrally connected.
Also, as shown in FIGS. 3 to 5, in order to prevent the rollers 11 in each pocket 25 from coming off, the axial intermediate portion 31 and the axial end portions 32, 33 of the opposing surfaces of the adjacent column portions 30 are opposed to each other. On the end surface, retaining claws 40 and 41 projecting in an opposing manner into the pocket 25 are respectively projected.

保持器２０の外周面が、遊星歯車４の中心孔５の内周面に接触することを防止するために、図３と図４に示すように、保持器２０の軸方向両端部の折曲縁２１、２３の先端と中心軸６の外周面との間の隙間寸法をＡとし、保持器２０の軸方向両端部３２、３３の外周面と遊星歯車４の中心孔５の内周面との間の隙間寸法をＢとしたときに、「Ａ＜Ｂ」の関係となるように設定されている。
また、この実施例１において、図３〜図５に示すように、ポケット２５の軸方向両端部（第１、第２の円環部２２、２４の対向端面）には、ころ１１の両端面中心部に接触してころ１１を転動案内する先尖り状の突起４５、４６がそれぞれ形成されている。 In order to prevent the outer peripheral surface of the cage 20 from coming into contact with the inner peripheral surface of the center hole 5 of the planetary gear 4, as shown in FIG. 3 and FIG. The clearance dimension between the tips of the edges 21 and 23 and the outer peripheral surface of the central shaft 6 is A, and the outer peripheral surfaces of the axial end portions 32 and 33 of the cage 20 and the inner peripheral surface of the central hole 5 of the planetary gear 4 Is set such that “A <B”.
Further, in the first embodiment, as shown in FIGS. 3 to 5, both end surfaces of the roller 11 are provided at both end portions in the axial direction of the pocket 25 (opposing end surfaces of the first and second annular portions 22 and 24). Pointed protrusions 45 and 46 are formed, which contact the center portion and guide the rollers 11 to roll.

上述したように構成されるこの実施例１に係る遊星歯車機構のころ軸受において、遊星歯車４が、その中心軸６の軸回りに自転しながら太陽歯車２の歯車回りに公転する際の遠心力を保持器２０が受けると、その遠心力が作用する方向（図６において矢印Ｐ方向）へ保持器２０が移動する。この際、保持器２０が移動する方向の後側に位置する同保持器２０の内周面（この実施例１では折曲縁２１、２３の先端）の後側が中心軸６の外周面に接触（当接）することによって保持器２０の移動が止められる。
このため、保持器２０の外周面（この実施例１では柱部３０の軸方向両端部３２、３３の外周面）の前側（移動方向の前側）が遊星歯車４の中心孔５の内周面に接触することを阻止することができ、保持器２０の摺動抵抗を小さく抑えることができる。
すなわち、保持器２０の内周面の周速は、同保持器２０の外周面の周速よりも遅いため、従来の保持器の外周面が遊星歯車の中心孔の内周面に接触する場合と比べ、保持器２０の摺動抵抗を小さく抑えることができ、この結果、保持器２０の摺動抵抗によるトルク損失を抑制することができる。 In the roller bearing of the planetary gear mechanism according to the first embodiment configured as described above, the centrifugal force when the planetary gear 4 revolves around the gear of the sun gear 2 while rotating around the axis of the central shaft 6. Is received by the cage 20, the cage 20 moves in the direction in which the centrifugal force acts (direction of arrow P in FIG. 6). At this time, the rear side of the inner peripheral surface of the retainer 20 located at the rear side in the moving direction of the retainer 20 (the front ends of the bent edges 21 and 23 in this embodiment 1) contacts the outer peripheral surface of the central shaft 6. The movement of the cage 20 is stopped by (contact).
Therefore, the front side (front side in the moving direction) of the outer peripheral surface of the cage 20 (the outer peripheral surfaces of the axial end portions 32 and 33 of the column 30 in this embodiment 1) is the inner peripheral surface of the center hole 5 of the planetary gear 4. Can be prevented, and the sliding resistance of the cage 20 can be kept small.
That is, since the peripheral speed of the inner peripheral surface of the cage 20 is slower than the peripheral speed of the outer peripheral surface of the cage 20, the outer peripheral surface of the conventional cage contacts the inner peripheral surface of the center hole of the planetary gear. As a result, the sliding resistance of the cage 20 can be reduced, and as a result, torque loss due to the sliding resistance of the cage 20 can be suppressed.

また、この実施例１において、遠心力が作用する方向へ保持器２０が移動する際には、保持器２０の折曲縁２１、２３の先端が中心軸６の外周面に接触する。このため、中心軸６の外周面に対する保持器２０の接触面積を折曲縁２１、２３の先端で小さく抑えることができる。この結果、低トルク化、摩耗低減等に効果が大きい。   Further, in the first embodiment, when the cage 20 moves in the direction in which the centrifugal force acts, the tips of the bent edges 21 and 23 of the cage 20 come into contact with the outer peripheral surface of the central shaft 6. For this reason, the contact area of the retainer 20 with respect to the outer peripheral surface of the central shaft 6 can be kept small at the tips of the bent edges 21 and 23. As a result, it is highly effective in reducing torque and reducing wear.

また、この実施例１において、図５に示すように、ポケット２５の軸方向両端部の第１、第２の円環部２２、２４の折曲縁２１、２３に先尖り状の突起４５、４６がそれぞれ形成され、これら突起４５、４６の先端がころ１１の両端面中心部に接触してころ１１を転動案内することができる。
このため、ポケット２５の軸方向両端部をなす第１、第２の円環部２２、２４の対向端面と、ころ１１の両端面との間の摺動抵抗を低減することができ、これによって、保持器２０の摺動抵抗によるトルク損失を良好に低減することができる。 Further, in the first embodiment, as shown in FIG. 5, pointed protrusions 45 on the bent edges 21 and 23 of the first and second annular portions 22 and 24 at both axial ends of the pocket 25, 46 are formed, and the tips of the protrusions 45 and 46 can contact the center portions of both end faces of the roller 11 to roll and guide the roller 11.
For this reason, the sliding resistance between the opposing end surfaces of the first and second annular portions 22 and 24 forming both end portions in the axial direction of the pocket 25 and both end surfaces of the roller 11 can be reduced. The torque loss due to the sliding resistance of the cage 20 can be satisfactorily reduced.

例えば、太陽歯車２及びリングギヤ３と、遊星歯車４とが、はす歯によって噛み合わされる場合、遊星歯車４の自転及び公転によるモーメントがころ１１の中心軸線を傾かせる方向へ作用する。これによって、従来ではころの端面がポケットの軸方向両端部に接触して大きい摺動抵抗を発生させるが、この実施例１では、前述したように、突起４５、４６の先端がころ１１の両端面の中心部に接触することによって、当該分に生じる摺動抵抗が、従来と比べて極めて小さくなり、トルク損失の低減に効果が大きい。   For example, when the sun gear 2, the ring gear 3, and the planetary gear 4 are engaged with each other by a helical tooth, a moment due to rotation and revolution of the planetary gear 4 acts in a direction in which the central axis of the roller 11 is inclined. Thus, conventionally, the end face of the roller comes into contact with both end portions in the axial direction of the pocket and generates a large sliding resistance. By contacting the central portion of the surface, the sliding resistance generated by that amount becomes extremely smaller than that of the conventional case, and the effect of reducing torque loss is great.

なお、この発明は前記実施例１に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々なる形態で実施することもできる。   In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can also be implemented with a various form.

この発明の実施例１に係る遊星歯車機構を簡略化して示す説明図である。It is explanatory drawing which simplifies and shows the planetary gear mechanism which concerns on Example 1 of this invention. 同じく遊星歯車と中心軸との間にころ軸受が組み付けられた状態を示す縦断面図である。It is a longitudinal section showing the state where a roller bearing was similarly assembled between a planetary gear and a central axis. 同じく保持器を示す横断面図である。It is a cross-sectional view which similarly shows a retainer. 同じく保持器を示す縦断面図である。It is a longitudinal section showing a cage similarly. 同じく保持器のポケットを外径側から示す展開図である。It is an expanded view which similarly shows the pocket of a holder | retainer from an outer diameter side. 同じく遠心力が作用する方向へ保持器が移動した状態を示す説明図である。It is explanatory drawing which shows the state which the holder | retainer moved to the direction where a centrifugal force acts similarly.

１ 遊星歯車機構
２ 太陽歯車
３ リングギヤ
４ 遊星歯車
１０ ころ軸受
１１ ころ
２０ 保持器
２１ 第１の円環部
２３ 第２の円環部
２５ ポケット
３０ 柱部
４５、４６ 突起 DESCRIPTION OF SYMBOLS 1 Planetary gear mechanism 2 Sun gear 3 Ring gear 4 Planetary gear 10 Roller bearing 11 Roller 20 Cage 21 1st ring part 23 2nd ring part 25 Pocket 30 Pillar part 45, 46 Protrusion

Claims (3)

遊星歯車機構の遊星歯車の中心孔と中心軸との間に組み込まれる複数のころと保持器とを備えたころ軸受であって、
前記保持器は、軸方向に所定間隔で配置された第１、第２の円環部と、これら第１、第２の円環部を連結すると共に、前記複数のころをそれぞれ個別に収納する複数のポケットを区画形成する複数の柱部とを備え、
前記保持器の内周面と前記中心軸の外周面との間の隙間寸法をＡとし、前記保持器の外周面と前記遊星歯車の中心孔の内周面との間の隙間寸法をＢとしたときに、「Ａ＜Ｂ」の関係となるように設定され、
前記ポケットの軸方向両端部の前記第１、第２の円環部の対向端面には、前記複数のころのピッチ円（ＰＣＤ）と、前記ころの両端面の径方向との交差部である前記ころの両端面中心部にそれぞれ接触して前記ころを転動案内する先尖り状の突起が形成されていることを特徴とする遊星歯車機構のころ軸受。 A roller bearing comprising a plurality of rollers and a cage assembled between a central hole and a central shaft of a planetary gear of a planetary gear mechanism,
The retainer connects the first and second annular portions arranged at predetermined intervals in the axial direction and the first and second annular portions, and individually accommodates the plurality of rollers. A plurality of pillars that define a plurality of pockets;
The clearance dimension between the inner peripheral surface of the cage and the outer peripheral surface of the central shaft is A, and the clearance dimension between the outer peripheral surface of the cage and the inner peripheral surface of the center hole of the planetary gear is B. Is set to have a relationship of “A <B”,
Opposite end surfaces of the first and second annular portions at both axial end portions of the pocket are intersections between pitch circles (PCD) of the plurality of rollers and radial directions of both end surfaces of the rollers. roller bearing of the planetary gear mechanism, characterized in that above pointed like projections that rolling guide said this filtrate to come in contact on both end surface center portion of the front Symbol rollers are formed. 請求項１に記載の遊星歯車機構のころ軸受であって、A roller bearing of the planetary gear mechanism according to claim 1,
先尖り状の突起は、保持器の第１、第２の円環部及び複数の柱部の板厚寸法と同等の径方向の板厚寸法を有し、径方向視で先尖り状に形成されていることを特徴とする遊星歯車機構のころ軸受。  The pointed protrusion has a radial thickness equivalent to the thickness of the first and second annular portions and the plurality of pillars of the cage, and is formed in a pointed shape when viewed in the radial direction. A roller bearing of a planetary gear mechanism characterized by being made. 請求項１又は２に記載の遊星歯車機構のころ軸受であって、
保持器の複数の柱部は、複数のころのピッチ円（ＰＣＤ）寸法よりも小径の軸方向中間部と、前記複数のころのピッチ円寸法よりも大径の軸方向両端部と、これら軸方向中間部及び軸方向両端部を連結する傾斜連結部とを有し、
前記軸方向両端部の端縁部には、段差状をなす小径の肩部がそれぞれ形成され、これら両肩部は、前記第１、第２の円環部と同径をなして一体に接続され、
前記第１、第２の円環部の軸方向端部には、径方向中心側へ曲げられた折曲縁が形成され、この折曲縁の先端が中心軸の外周面に接触可能とされていることを特徴とする遊星歯車機構のころ軸受。 A roller bearing of the planetary gear mechanism according to claim 1 or 2 ,
The plurality of column portions of the cage include an axial intermediate portion having a diameter smaller than the pitch circle (PCD) size of the plurality of rollers, axial end portions having a diameter larger than the pitch circle size of the plurality of rollers, An intermediate connecting portion and an inclined connecting portion for connecting both axial end portions,
A small-diameter shoulder having a step shape is formed at each end edge of the both axial ends, and both the shoulders are integrally connected with the same diameter as the first and second annular portions. And
A bent edge that is bent toward the radial center is formed at the axial ends of the first and second annular portions, and the tip of the bent edge can contact the outer peripheral surface of the central shaft. A roller bearing of a planetary gear mechanism, characterized in that
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