JP2009185849A

JP2009185849A - Rolling bearing unit

Info

Publication number: JP2009185849A
Application number: JP2008024700A
Authority: JP
Inventors: Hideki Koizumi; 秀樹小泉; Takashi Yamamoto; 高志山本
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2008-02-05
Filing date: 2008-02-05
Publication date: 2009-08-20

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing unit constructed to allow easy work for assembling seat plates 13A, 13B to suppress the axial displacement of cages 9a, 9b constituting tapered roller bearings 5a, 5b which rotatably supports whirling members 4a, 4b around eccentric cam portions 3a, 3b, while securing the supporting strength of both seat plates 13A, 13B and the amount of lubricating oil to be supplied to both tapered roller bearings 5a, 5b. <P>SOLUTION: Portions near the inner diameters of both seat plates 13A, 13B are held and fixed all over their peripheries between the axial inner end face of each of inner rings 12, 12 of the adjacent tapered roller bearings 2, 2 and the axial outer end face of each of the eccentric cam portions 3a, 3b. Cutouts 16, 16 are formed in a plurality of circumferential positions on portions near the outer diameters of both seat plates 13A, 13B in axial opposition to both cages 9a, 9b. The diameter of an inscribed circle between the cutouts 16, 16 is smaller than the inner diameter of each of rim portions 10, 10 of both cages 9a, 9b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は、回転動力を減速しつつ伝達する動力伝達装置に組み込む転がり軸受ユニットの改良に関する。具体的には、必要な機能を確保しつつ、偏心カム部の周囲に振れ回り部材を支持する為のころ軸受（ニードル軸受を含む、本明細書及び特許請求の範囲全体で同じ）に十分な潤滑油を流通させられる構造の実現を図るものである。 The present invention relates to an improvement in a rolling bearing unit incorporated in a power transmission device that transmits rotational power while decelerating. Specifically, it is sufficient for a roller bearing (including the needle bearing, including the needle bearing) to support the swinging member around the eccentric cam portion while ensuring the necessary functions. It is intended to realize a structure through which lubricating oil can be distributed.

回転運動を大きく減速しつつ伝達する、減速機構を備えた動力伝達装置として、特許文献１に記載された構造が知られている。この動力伝達装置は、高速で回転する入力軸の回転運動を、外周縁に外歯を形成した振れ回り部材（外歯歯車）の振れ回り運動に変換し、この振れ回り運動を、ピンと内歯とを介して外径側部材（内歯歯車）に伝達し、この外径側部材を固定した出力軸を低速で回転させるものである。この様な動力伝達装置で、上記入力軸の回転を上記振れ回り部材の振れ回り運動に変化する部分を従来は、図９〜１０に示す様に構成している。 A structure described in Patent Document 1 is known as a power transmission device including a speed reduction mechanism that transmits rotational motion while greatly decelerating. This power transmission device converts the rotational motion of the input shaft, which rotates at high speed, to the whirling motion of a whirling member (external gear) with external teeth formed on the outer peripheral edge. Is transmitted to the outer diameter side member (internal gear), and the output shaft to which the outer diameter side member is fixed is rotated at a low speed. In such a power transmission device, the portion where the rotation of the input shaft changes to the swinging motion of the swinging member is conventionally configured as shown in FIGS.

駆動源により回転駆動される回転軸１は、軸方向に離隔して配置された、それぞれが特許請求の範囲に記載した回転支持用転がり軸受である１対の円すいころ軸受２、２により、回転自在に支持されている。上記回転軸１の一部で、これら両円すいころ軸受２、２同士の間部分に、１対の偏心カム部３ａ、３ｂを固設（例えば一体形成）している。これら両偏心カム部３ａ、３ｂは、上記回転軸１の回転中心αに対し偏心した円筒状の外周面を有し、それぞれの外径が、この回転軸１のうちで上記両偏心カム部３ａ、３ｂに隣接する部分の外径よりも大きい。又、これら両偏心カム部３ａ、３ｂの中心軸β、γが上記回転軸１の回転中心αに対し偏心している方向は、この回転軸１の径方向に関して１８０度逆方向としている。 A rotating shaft 1 that is rotationally driven by a drive source is rotated by a pair of tapered roller bearings 2 and 2 that are spaced apart from each other in the axial direction and are rolling bearings for rotation support described in the claims. It is supported freely. A part of the rotating shaft 1 has a pair of eccentric cam portions 3a, 3b fixed (for example, integrally formed) between the two tapered roller bearings 2, 2. The two eccentric cam portions 3a and 3b have cylindrical outer peripheral surfaces that are eccentric with respect to the rotation center α of the rotary shaft 1, and the outer diameters of the two eccentric cam portions 3a of the rotary shaft 1 are the same. 3b is larger than the outer diameter of the portion adjacent to 3b. The direction in which the central axes β and γ of the eccentric cam portions 3 a and 3 b are eccentric with respect to the rotational center α of the rotary shaft 1 is 180 degrees opposite to the radial direction of the rotary shaft 1.

又、上記両偏心カム部３ａ、３ｂの周囲に振れ回り部材４ａ、４ｂを、それぞれ円筒ころ軸受５ａ、５ｂにより、回転自在に支持している。これら両円筒ころ軸受５ａ、５ｂは、それぞれ、上記両偏心カム部３ａ、３ｂの外周面である内輪軌道６ａ、６ｂと、上記両振れ回り部材４ａ、４ｂの内周面である外輪軌道７ａ、７ｂとの間に、複数個ずつの円筒ころ８ａ、８ｂを配置して成る。これら各円筒ころ８ａ、８ｂはそれぞれ、保持器９ａ、９ｂにより転動自在に保持している。これら両保持器９ａ、９ｂは、Ｍ形保持器と呼ばれるもので、金属板を曲げ形成する事により、断面略Ｍ字形で全体を円筒状に形成している。そして、軸方向両端部に設けた円輪状のリム部１０、１０同士の間に、柱部１１、１１とポケットとを、円周方向に関して交互に配置している。そして、これら各ポケット内に上記各円筒ころ８ａ、８ｂを、転動自在に保持している。 Further, the swinging members 4a and 4b are rotatably supported by the cylindrical roller bearings 5a and 5b around the eccentric cam portions 3a and 3b, respectively. These cylindrical roller bearings 5a and 5b are respectively provided with inner ring raceways 6a and 6b which are outer peripheral surfaces of the eccentric cam portions 3a and 3b, and outer ring raceways 7a which are inner peripheral surfaces of the swing-out members 4a and 4b. A plurality of cylindrical rollers 8a and 8b are arranged between the two and 7b. These cylindrical rollers 8a and 8b are held by rolls 9a and 9b so as to be freely rollable. These two cages 9a and 9b are called M-type cages, and are formed into a cylindrical shape with a substantially M-shaped cross section by bending a metal plate. And the pillar parts 11 and 11 and a pocket are alternately arrange | positioned regarding the circumferential direction between the ring-shaped rim | limb parts 10 and 10 provided in the axial direction both ends. And each said cylindrical roller 8a, 8b is hold | maintained in these each pocket so that rolling is possible.

又、上記両偏心カム部３ａ、３ｂの軸方向外端面（互いに反対側の端面）と、前記両円すいころ軸受２、２を構成する内輪１２、１２の軸方向内端面（互いに対向する端面）との間に、座板１３ａ、１３ｂの内周縁部を挟持している。これら両座板１３ａ、１３ｂは、上記両円筒ころ軸受５ａ、５ｂを構成する上記両保持器９ａ、９ｂの軸方向の変位を抑える為に設けたもので、金属板を打ち抜く事により円輪状に形成している。即ち、上記両保持器９ａ、９ｂは、上記各円筒ころ８ａ、８ｂの自転中心が上記両偏心カム部３ａ、３ｂの中心軸β、γに対し傾斜する、所謂スキューに基づいて発生するスラスト力により、軸方向に変位する可能性がある。この様な場合にも、上記両保持器９ａ、９ｂの軸方向位置を適正位置に保持し、これら両保持器９ａ、９ｂに保持された上記各円筒ころ８ａ、８ｂの転動面が、上記内輪軌道６ａ、６ｂ及び上記外輪軌道７ａ、７ｂから外れない様にすべく、上記両座板１３ａ、１３ｂを設けている。 Further, the axially outer end surfaces (end surfaces opposite to each other) of the eccentric cam portions 3a, 3b and the axially inner end surfaces (end surfaces facing each other) of the inner rings 12, 12 constituting the tapered roller bearings 2, 2 are provided. The inner peripheral edge portions of the seat plates 13a and 13b are sandwiched therebetween. These seat plates 13a and 13b are provided to suppress the axial displacement of the cages 9a and 9b constituting the cylindrical roller bearings 5a and 5b, and are formed into an annular shape by punching a metal plate. Forming. That is, both the cages 9a and 9b have a thrust force generated based on a so-called skew in which the rotation centers of the cylindrical rollers 8a and 8b are inclined with respect to the central axes β and γ of the eccentric cam portions 3a and 3b. Therefore, there is a possibility of displacement in the axial direction. Even in such a case, the axial positions of the two cages 9a and 9b are held at appropriate positions, and the rolling surfaces of the cylindrical rollers 8a and 8b held by the two cages 9a and 9b are The both seat plates 13a and 13b are provided so as not to be separated from the inner ring raceways 6a and 6b and the outer ring raceways 7a and 7b.

これら両座板１３ａ、１３ｂは、内周縁部の円周方向の一部のみを、図９の右下部及び左上部に示す様に、上記両偏心カム部３ａ、３ｂの軸方向外端面と上記両内輪１２、１２の軸方向内端面との間で挟持している。具体的には、上記両偏心カム部３ａ、３ｂの軸方向外端面のうちで、これら両偏心カム部３ａ、３ｂの偏心量が多くなった部分（前記回転軸１の回転中心αからの距離が大きくなった部分）と上記両内輪１２、１２の軸方向内端面との間で挟持している。そして、上記両座板１３ａ、１３ｂの内周縁の円周方向の残部と、上記両内輪１２、１２の軸方向内端面の外周縁及び上記両偏心カム部３ａ、３ｂの軸方向外端面の外周縁との間に、図９の右上部及び左下部に示す様に、隙間１４ａ、１４ｂを形成している。具体的には、上記両偏心カム部３ａ、３ｂの軸方向外端面のうちで、これら両偏心カム部３ａ、３ｂの偏心量が少なくなった部分（前記回転軸１の回転中心αからの距離が小さくなった部分）の外周縁と、上記両座板１３ａ、１３ｂの内周縁との間に、上記両隙間１４ａ、１４ｂを設けている。これら両隙間１４ａ、１４ｂは、上記両円筒ころ軸受５ａ、５ｂに潤滑油を流通させる為のもので、それぞれが図１１〜１２に示す様な三日月形である。上記両隙間１４ａ（１４ｂ）の円周方向位置は、前記回転軸１の回転に伴う、上記両偏心カム部３ａ、３ｂの回転に伴って、図１３の（Ａ）→（Ｂ）→（Ｃ）→（Ｄ）→（Ａ）に示す様に円周方向に移動し、前記各円筒ころ８ａ、８ｂの公転運動に伴って、上記両円筒ころ軸受５ａ（５ｂ）の全周に亙って潤滑油を供給可能にする。 These two seat plates 13a and 13b are formed in such a manner that only a part of the inner peripheral edge in the circumferential direction is shown in the lower right and upper left in FIG. The inner rings 12 are sandwiched between the inner end faces in the axial direction of the inner rings 12. Specifically, of the axially outer end surfaces of the eccentric cam portions 3a and 3b, a portion where the eccentric amount of the eccentric cam portions 3a and 3b is increased (distance from the rotation center α of the rotary shaft 1). Between the inner ring 12 and the axial inner end surfaces of the inner rings 12 and 12. And the remaining part of the inner peripheral edge of the both seat plates 13a, 13b in the circumferential direction, the outer peripheral edge of the inner end face in the axial direction of the inner rings 12, 12 and the outer end face in the axial direction of the eccentric cam parts 3a, 3b. Between the periphery, gaps 14a and 14b are formed as shown in the upper right part and lower left part of FIG. Specifically, of the axially outer end surfaces of the eccentric cam portions 3a and 3b, a portion where the eccentric amount of the eccentric cam portions 3a and 3b is reduced (distance from the rotation center α of the rotary shaft 1). The gaps 14a and 14b are provided between the outer peripheral edge of the portion) and the inner peripheral edges of the seat plates 13a and 13b. These clearances 14a and 14b are for circulating lubricating oil through the cylindrical roller bearings 5a and 5b, and each has a crescent shape as shown in FIGS. The circumferential positions of both the gaps 14a (14b) are changed in accordance with the rotation of the eccentric cam portions 3a and 3b accompanying the rotation of the rotary shaft 1 (A) → (B) → (C ) → (D) → (A) and moves in the circumferential direction, and along the entire circumference of the cylindrical roller bearings 5a (5b) with the revolving motion of the cylindrical rollers 8a and 8b. Allow supply of lubricating oil.

上記各円筒ころ８ａ、８ｂのスキューに基づいて上記両保持器９ａ、９ｂが軸方向に変位する傾向になった場合も、上記両座板１３ａ、１３ｂの存在に基づき、この変位を抑える。即ち、何れかの保持器９ａ（９ｂ）が、他の保持器９ｂ（９ａ）から離れる方向に変位する傾向になると、当該保持器９ａ（９ｂ）のリム部１０と上記座板１３ａ（１３ｂ）とが当接して、それ以上この保持器９ａ（９ｂ）が軸方向に変位するのを阻止する。これに対して、何れかの保持器９ａ（９ｂ）が、他の保持器９ｂ（９ａ）に近付く方向に変位する傾向になると、当該保持器９ａ（９ｂ）のリム部１０とこの他の保持器９ｂ（９ａ）のリム部１０とが当接して、それ以上この保持器９ａ（９ｂ）が軸方向に変位するのを阻止する。そして、何れの場合も、上記両保持器９ａ、９ｂに保持された前記各円筒ころ８ａ、８ｂの転動面が、前記内輪軌道６ａ、６ｂ及び前記外輪軌道７ａ、７ｂから外れない様にする。 Even when both the cages 9a and 9b tend to be displaced in the axial direction based on the skews of the cylindrical rollers 8a and 8b, the displacement is suppressed based on the presence of the both seat plates 13a and 13b. That is, when any one of the cages 9a (9b) tends to be displaced away from the other cages 9b (9a), the rim portion 10 of the cage 9a (9b) and the seat plate 13a (13b). And the cage 9a (9b) is prevented from further displacement in the axial direction. On the other hand, when any one of the cages 9a (9b) tends to be displaced in a direction approaching the other cage 9b (9a), the rim portion 10 of the cage 9a (9b) and the other cages are retained. The rim portion 10 of the container 9b (9a) comes into contact with the container 9b (9a) to prevent the retainer 9a (9b) from being displaced further in the axial direction. In either case, the rolling surfaces of the cylindrical rollers 8a and 8b held by the cages 9a and 9b are prevented from being detached from the inner ring raceways 6a and 6b and the outer ring raceways 7a and 7b. .

上述の様な従来構造の場合、上記両円筒ころ軸受５ａ（５ｂ）への潤滑油の供給量を確保する事が難しい。この理由は、前記両隙間１４ａ、１４ｂの開口面積を確保する事が難しい為である。即ち、これら両隙間１４ａ、１４ｂは、図１１〜１２から明らかな通り、円周方向の長さ寸法Ｌは或る程度確保できるが、径方向の幅寸法Ｗを確保する事は難しい。この為、著しい場合には、上記両隙間１４ａ、１４ｂ部分がラビリンスシール的に機能する等により、これら両隙間１４ａ、１４ｂを通過する潤滑油の量を確保しにくい。上記幅寸法Ｗを大きくしてこれら両隙間１４ａ、１４ｂを通過する潤滑油の量を確保する事だけを考えれば、上記両座板１３ａ、１３ｂの内径を大きくしたり、前記両内輪１２、１２に対するこれら両座板１３ａ、１３ｂの偏心量を多くすれば良い。但し、この様な構造を採用した場合には、これら両座板１３ａ、１３ｂの内周縁部の円周方向の一部で、前記両偏心カム部３ａ、３ｂの軸方向外端面と前記両内輪１２、１２の軸方向内端面との間で挟持する部分の面積が狭くなり、上記両座板１３ａ、１３ｂの支持強度を確保しにくくなる。しかも、上記従来構造の場合には、上記両座板１３ａ、１３ｂを上記両内輪１２、１２に対し、適正方向に適正量だけ偏心した状態で組み付ける必要があり、組み付け作業が面倒になる。 In the case of the conventional structure as described above, it is difficult to ensure the supply amount of the lubricating oil to the both cylindrical roller bearings 5a (5b). This is because it is difficult to ensure the opening area of both the gaps 14a and 14b. That is, as is clear from FIGS. 11 to 12, these gaps 14 a and 14 b can secure a certain length L in the circumferential direction, but it is difficult to secure a width W in the radial direction. For this reason, in a remarkable case, it is difficult to ensure the amount of lubricating oil passing through both the gaps 14a and 14b because the gaps 14a and 14b function as labyrinth seals. Considering only increasing the width dimension W to ensure the amount of lubricating oil passing through the gaps 14a, 14b, the inner diameters of the seat plates 13a, 13b can be increased, or the inner rings 12, 12 can be increased. What is necessary is just to increase the amount of eccentricity of these both seat plates 13a and 13b. However, when such a structure is employed, the axially outer end surfaces of the eccentric cam portions 3a, 3b and the inner rings are part of the inner peripheral edge of the both seat plates 13a, 13b in the circumferential direction. The area of the portion sandwiched between the inner end surfaces 12 and 12 in the axial direction becomes narrow, and it becomes difficult to secure the support strength of the both seat plates 13a and 13b. Moreover, in the case of the conventional structure, it is necessary to assemble the both seat plates 13a and 13b with respect to the inner rings 12 and 12 while being eccentric in the proper direction by an appropriate amount, and the assembling work becomes troublesome.

特開２００６−３３６７０２号公報JP 2006-336702 A

本発明は、上述の様な事情に鑑みて、偏心カム部の周囲に振れ回り部材を回転自在に支持する為の円筒ころ軸受を構成する保持器の軸方向変位を抑える為の座板の組み付け作業が容易でこの座板の支持強度を確保でき、しかも上記円筒ころ軸受に供給する潤滑油の量を確保できる構造を実現すべく発明したものである。 In view of the circumstances as described above, the present invention is an assembly of a seat plate for suppressing axial displacement of a cage constituting a cylindrical roller bearing for rotatably supporting a swinging member around an eccentric cam portion. The present invention was invented to realize a structure that can easily work, ensure the supporting strength of the seat plate, and secure the amount of lubricating oil supplied to the cylindrical roller bearing.

本発明の転がり軸受ユニットは、前述した従来から知られている転がり軸受ユニットと同様に、回転軸と、偏心カム部と、振れ回り部材と、複数個の円筒ころと、回転支持用転がり軸受と、座板とを備える。
上記偏心カム部は、上記回転軸の一部に固設されたもので、この回転軸の回転中心に対し偏心した円筒状の外周面を有し、外径がこの回転軸のうちで隣接する部分の外径よりも大きい。
又、上記振れ回り部材は、上記偏心カム部の周囲に配置されたもので、円筒状の内周面を有する。
又、上記各円筒ころは、上記偏心カム部の外周面と上記振れ回り部材の内周面との間に、保持器に転動自在に保持された状態で設けられている。
又、上記回転支持用転がり軸受は、上記回転軸のうちで軸方向に関して上記偏心カム部に隣接する部分に設けられて、上記回転軸を回転自在に支持する。
更に、上記座板は、上記回転支持用転がり軸受を構成する、上記回転軸に外嵌固定された内輪の軸方向端面と、上記偏心カム部の軸方向端面との間で挟持固定されている。
そして、上記座板の軸方向片側面と上記保持器の軸方向端面とを軸方向に対向させている。 The rolling bearing unit of the present invention includes a rotating shaft, an eccentric cam portion, a swinging member, a plurality of cylindrical rollers, a rolling support rolling bearing, and the rolling bearing unit known in the related art. And a seat plate.
The eccentric cam portion is fixed to a part of the rotation shaft, has a cylindrical outer peripheral surface that is eccentric with respect to the rotation center of the rotation shaft, and has an outer diameter adjacent to the rotation shaft. It is larger than the outer diameter of the part.
The swing member is disposed around the eccentric cam portion and has a cylindrical inner peripheral surface.
Each cylindrical roller is provided between the outer peripheral surface of the eccentric cam portion and the inner peripheral surface of the swinging member in a state of being rotatably held by a cage.
The rotation support rolling bearing is provided in a portion of the rotating shaft adjacent to the eccentric cam portion in the axial direction, and rotatably supports the rotating shaft.
Further, the seat plate is sandwiched and fixed between the axial end surface of the inner ring that is externally fitted and fixed to the rotary shaft, and the axial end surface of the eccentric cam portion, which constitutes the rolling support rolling bearing. .
And the axial direction one side surface of the said seat plate and the axial direction end surface of the said holder | retainer are made to oppose in an axial direction.

特に、本発明の転がり軸受ユニットに於いては、上記座板の内径寄り部分を、上記内輪の軸方向端面と上記偏心カム部の軸方向端面との間で全周に亙り挟持固定している。又、上記座板の外径寄り部分で上記保持器に軸方向対向する部分の円周方向複数個所に、切り欠き若しくは通孔を形成している。更に、これら各切り欠き若しくは通孔の内接円の直径を、上記保持器の内径よりも小さくしている。 In particular, in the rolling bearing unit of the present invention, the portion closer to the inner diameter of the seat plate is sandwiched and fixed over the entire circumference between the axial end surface of the inner ring and the axial end surface of the eccentric cam portion. . Further, notches or through-holes are formed at a plurality of locations in the circumferential direction at portions near the outer diameter of the seat plate and facing the cage in the axial direction. Furthermore, the diameter of the inscribed circle of each notch or through hole is made smaller than the inner diameter of the cage.

この様な本発明の転がり軸受ユニットを実施する場合に、例えば請求項２、３に記載した発明の様に、上記座板の外周縁の円周方向等間隔の複数個所に、この座板の径方向に関する寸法が互いに同じである切り欠きを形成する。
そして、例えば請求項２に記載した発明の様に、上記座板のうちでこれら各切り欠き部分の外径をｄ_W とし、保持器の内径をＲ_C とし、回転軸の回転中心に対する偏心カム部の外周面の中心の偏心量をδとした場合に、ｄ_W ＜Ｒ_C −２δを満たすべく、各部の寸法ｄ_W 、Ｒ_C 、２δを規制する。そして、好ましくは、Ｒ_C −２δ−ｄ_W ＞０．０５Ｒ_C とする。
或いは、請求項３に記載した発明の様に、上記座板のうちでこれら各切り欠き部分の外径をｄ_W とし、同じくこれら各切り欠きから外れた部分の外径をＤ_W とし、保持器の内径をＲ_C とし、同じく外径をＤ_C とし、回転軸の回転中心に対する偏心カム部の外周面の中心の偏心量をδとした場合に、Ｄ_W ≒（Ｒ_C ＋Ｄ_C ）／２＋２δ、言い換えれば、０．９｛（Ｒ_C ＋Ｄ_C ）／２＋２δ｝≦Ｄ_W ≦１．１｛（Ｒ_C ＋Ｄ_C ）／２＋２δ｝を満たすべく、各部の寸法ｄ_W 、Ｄ_W 、Ｒ_C 、Ｄ_C 、δを規制する。 When implementing such a rolling bearing unit of the present invention, for example, as in the second and third aspects of the invention, the seat plate is provided at a plurality of circumferentially equidistant positions on the outer periphery of the seat plate. Cutouts having the same radial dimension are formed.
Then, for example, as in the invention described in claim 2, the outer diameter of each of the notches in the seat plate is d _W , the inner diameter of the cage is _RC, and the eccentric cam with respect to the rotation center of the rotating shaft When the amount of eccentricity at the center of the outer peripheral surface of the part is δ, the dimensions d _W , R _C , and 2δ of each part are regulated so as to satisfy d _W <R _C −2δ. And, preferably, the _{_{R C -2δ-d W> 0.05R}} C.
Alternatively, as in the invention described in claim 3, the outer diameter of each notch portion in the above-mentioned seat plate is d _W and the outer diameter of the portion removed from each notch is D _W. If the inner diameter of the chamber is R _C , the outer diameter is also D _C, and the amount of eccentricity of the center of the outer peripheral surface of the eccentric cam portion with respect to the rotation center of the rotating shaft is δ, D _W ≈ (R _C + D _C ) / 2 + 2δ, in other words, 0.9 {(R _C + D _C ) / 2 + 2δ} ≦ D _W ≦ 1.1 {(R _C + D _C ) / 2 + 2δ}, dimensions d _W , D _W , R _{C of} each part , D _C and δ are regulated.

上述の様に構成する本発明の転がり軸受ユニットによれば、座板の組み付け作業の容易化と、この座板の支持強度の確保と、円筒ころ軸受に供給する潤滑油の量の確保とを、高次元で並立させられる。
即ち、上記座板の内径寄り部分を、内輪の軸方向端面と偏心カム部の軸方向端面との間で全周に亙り挟持固定する為、上記座板の内径を、回転軸のうちでこの偏心カム部に隣接する部分に外嵌できる大きさに規制さえすれば、上記座板の組み付け位置規制を容易に行なえる。そして、この座板を、上記内輪の軸方向端面と偏心カム部の軸方向端面との間で全周に亙り挟持する為、この座板の支持強度を十分に確保できる。
更に、この座板の外径寄り部分の円周方向複数個所に形成する切り欠き若しくは通孔の大きさは、上記支持強度に関係なく大きく（径方向に関する幅寸法を確保）できる。この為、上記切り欠き若しくは通孔を通じて上記円筒ころに十分量の潤滑油を供給できる。 According to the rolling bearing unit of the present invention configured as described above, the seat plate can be easily assembled, the support strength of the seat plate can be secured, and the amount of lubricating oil supplied to the cylindrical roller bearing can be secured. , Paralleled in a higher dimension.
That is, the inner diameter of the seat plate is clamped and fixed over the entire circumference between the axial end surface of the inner ring and the axial end surface of the eccentric cam portion. As long as the size of the seat plate is limited to a size that allows it to be fitted on the portion adjacent to the eccentric cam portion, the assembly position of the seat plate can be easily regulated. And since this seat plate is pinched over the perimeter between the axial direction end surface of the said inner ring | wheel and the axial direction end surface of an eccentric cam part, the support strength of this seat plate is fully securable.
Furthermore, the size of notches or through-holes formed at a plurality of locations in the circumferential direction near the outer diameter of the seat plate can be increased regardless of the support strength (a width dimension in the radial direction is ensured). For this reason, a sufficient amount of lubricating oil can be supplied to the cylindrical roller through the notch or the through hole.

［実施の形態の第１例］
図１〜６は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、１対の座板１３Ａ、１３Ｂの形状及び組み付け構造を工夫する事により、これら両座板１３Ａ、１３Ｂの組み付け作業の容易化と、これら両座板１３Ａ、１３Ｂの支持強度の確保と、１対の円筒ころ軸受５ａ、５ｂに供給する潤滑油の量の確保とを、高次元で並立させる点にある。その他の部分の構造及び作用は、前述の図９〜１３に示した従来構造と同様であるから、同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本発明の特徴部分を中心に説明する。 [First example of embodiment]
1 to 6 show a first example of an embodiment of the present invention. The feature of this example is that the shape and assembly structure of the pair of seat plates 13A and 13B are devised to facilitate the assembling work of both the seat plates 13A and 13B, and the both seat plates 13A and 13B. The securing of the support strength and the securing of the amount of lubricating oil supplied to the pair of cylindrical roller bearings 5a and 5b lie in high-order alignment. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 9 to 13 described above, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified. The description will focus on the features of

上記両座板１３Ａ、１３Ｂは、ステンレス鋼板、炭素鋼板等の鉄系合金板、或いは真鍮等の銅系合金板等の金属板を打ち抜き形成する事により、図６の（Ａ）又は（Ｂ）に示す様な、円輪状に加工している。即ち、上記両座板１３Ａ、１３Ｂは、中心部に円孔１５を、外周縁の円周方向等間隔複数個所（図示の例では４個所）に切り欠き１６、１６を、それぞれ形成している。上記円孔１５の内径Ｒ₁₅は、回転軸１の一部で偏心カム部３ａ、３ｂに隣接する部分の外径Ｄ₁ と同じか僅かに小さく（Ｒ₁₅≦Ｄ₁ ）して、上記両座板１３Ａ、１３Ｂを、これら両部分に、径方向に関する位置決めを図った状態で外嵌できる様にしている。 The both seat plates 13A and 13B are formed by stamping and forming a metal plate such as a ferrous alloy plate such as a stainless steel plate or a carbon steel plate, or a copper alloy plate such as brass, as shown in FIG. It is processed into an annular shape as shown in. That is, the both seat plates 13A and 13B are formed with circular holes 15 in the center and notches 16 and 16 at a plurality of circumferentially equidistant positions (four in the illustrated example). . The inner diameter R ₁₅ of the circular hole 15 is equal to or slightly smaller than the outer diameter D _{1 of} a part of the rotating shaft 1 adjacent to the eccentric cam portions 3a, 3b (R ₁₅ ≦ D ₁ ). The seat plates 13A and 13B can be externally fitted to these portions in a state where positioning in the radial direction is achieved.

又、上記両座板１３Ａ、１３Ｂのうちで、上記各切り欠き１６、１６から外れた外径寄り部分１７、１７の外径Ｄ_W は、上記両偏心カム部３ａ、３ｂの外周面である内輪軌道６ａ、６ｂの偏心運動に拘らず、上記各外径寄り部分１７、１７と、上記両円筒ころ軸受５ａ、５ｂに組み込む保持器９ａ、９ｂを構成する各リム部１０、１０のうち、上記両座板１３Ａ、１３Ｂ側に存在する１対のリム部１０、１０とが軸方向に対向し続ける様に、これら両リム部１０、１０の内径Ｒ_C との関係で規制している。言い換えれば、上記両座板１３Ａ、１３Ｂの外周縁が、上記両リム部１０、１０に対し最も径方向内側に変位した状態でも、これら両リム部１０、１０に確実に対向する様に、上記両寸法Ｄ_W 、Ｒ_C を規制している。 Of the both seat plates 13A and 13B, the outer diameters D _W of the outer diameter portions 17 and 17 that are out of the notches 16 and 16 are the outer peripheral surfaces of the eccentric cam portions 3a and 3b. Regardless of the eccentric motion of the inner ring raceways 6a, 6b, of the rim portions 10, 10 constituting the outer diameter portions 17, 17 and the cages 9a, 9b incorporated in the cylindrical roller bearings 5a, 5b, The pair of rim portions 10 and 10 existing on the side of both the seat plates 13A and 13B are restricted in relation to the inner diameter R _C of both the rim portions 10 and 10 so as to continue to face each other in the axial direction. In other words, even when the outer peripheral edges of the both seat plates 13A and 13B are displaced most radially inward with respect to the rim portions 10 and 10, the above rim portions 10 and 10 are surely opposed to each other. Both dimensions D _W and R _C are regulated.

好ましくは、上記両座板１３Ａ、１３Ｂのうちで上記各切り欠き１６、１６部分の外径をｄ_W とし、同じくこれら各切り欠き１６、１６から外れた部分の外径をＤ_W とし、上記両保持器９ａ、９ｂの内径である、上記両座板１３Ａ、１３Ｂ側に存在する１対のリム部１０、１０の内径をＲ_C とし、同じく外径をＤ_C とし、回転軸１の回転中心αに対する上記両偏心カム部３ａ、３ｂの外周面である内輪軌道６ａ、６ｂの中心（これら両偏心カム部３ａ、３ｂの中心軸）β、γの偏心量を、それぞれδとした場合に、Ｄ_W ≒（Ｒ_C ＋Ｄ_C ）／２＋２δ、言い換えれば、０．９｛（Ｒ_C ＋Ｄ_C ）／２＋２δ｝≦Ｄ_W ≦１．１｛（Ｒ_C ＋Ｄ_C ）／２＋２δ｝を満たすべく、各部の寸法ｄ_W 、Ｄ_W 、Ｒ_C 、Ｄ_C 、δを規制する。この様にこれら各部の寸法ｄ_W 、Ｄ_W 、Ｒ_C 、Ｄ_C 、δを規制すれば、上記両座板１３Ａ、１３Ｂの外周縁が上記両リム部１０、１０に対し最も径方向内側に変位した状態でも、上記両座板１３Ａ、１３Ｂにより上記両リム部１０、１０を、円周方向に関して均等に支承して、これら両リム部１０、１０を含む上記両保持器９ａ、９ｂ、延ては、これら両保持器９ａ、９ｂに保持された各円筒ころ８ａ、８ｂの自転軸が、正規の方向に対し傾斜する事を十分に防止できる。 Preferably, the outer diameter of each of the notches 16 and 16 in the both seat plates 13A and 13B is d _W, and the outer diameter of the portion removed from each of the notches 16 and 16 is D _W , both retainers 9a, an inner diameter of 9b, the both seat plate 13A, a pair existing in the 13B side inner diameter of the rim portions 10 and R _C, also the outer diameter of D _C, the rotation of the rotary shaft 1 When the centers of the inner ring raceways 6a and 6b that are the outer peripheral surfaces of the eccentric cam portions 3a and 3b with respect to the center α (center axes of the eccentric cam portions 3a and 3b) β and γ are respectively set to δ. D _W ≈ (R _C + D _C ) / 2 + 2δ, in other words 0.9 {(R _C + D _C ) / 2 + 2δ} ≦ D _W ≦ 1.1 {(R _C + D _C ) / 2 + 2δ} The dimensions d _W , D _W , R _C , D _C , and δ of each part are regulated. In this way, if the dimensions d _W , D _W , R _C , D _C , and δ of each part are regulated, the outer peripheral edges of the both seat plates 13A and 13B are most radially inward with respect to the rim parts 10 and 10. Even in the displaced state, both the rim portions 10 and 10 are supported evenly in the circumferential direction by the both seat plates 13A and 13B, and both the cages 9a and 9b including the both rim portions 10 and 10 are extended. Thus, it is possible to sufficiently prevent the rotation shafts of the cylindrical rollers 8a and 8b held by the two cages 9a and 9b from being inclined with respect to the normal direction.

又、上記両座板１３Ａ、１３Ｂのうちで、上記各切り欠き１６、１６部分の外径ｄ_W は、上記偏心運動に拘らず、これら各切り欠き１６、１６部分の外周縁が、上記両リム部１０、１０の内周縁よりも径方向内方に存在し続ける（これら外周縁と内周縁との間に隙間１４Ａ、１４Ｂが存在し続ける）様に、これら両リム部１０、１０の内径Ｒ_C との関係で規制している。
具体的には、上記各切り欠き１６、１６部分の外径ｄ_W 、即ち、これら各切り欠き１６、１６の内接円の直径を、上記両リム部１０、１０の内径Ｒ_C よりも小さく（ｄ_W ＜Ｒ_C ）している。更に、上記両内輪軌道６ａ、６ｂの偏心量をδとした場合に、ｄ_W ＜Ｒ_C −２δを満たすべく、各部の寸法ｄ_W 、Ｒ_C 、２δを規制している。そして、好ましくは、Ｒ_C −２δ−ｄ_W ＞０．０５Ｒ_C としている。 Of the both seat plates 13A and 13B, the outer diameter d _W of each of the notches 16 and 16 portions is the outer peripheral edge of each of the notches 16 and 16 portions regardless of the eccentric motion. The inner diameters of both the rim portions 10 and 10 are such that they remain radially inward from the inner peripheral edges of the rim portions 10 and 10 (the gaps 14A and 14B continue to exist between the outer and inner peripheral edges). Regulated in relation to _RC .
Specifically, the outer diameter d _{W of} each of the notches 16 and 16, that is, the diameter of the inscribed circle of each of the notches 16 and 16 is smaller than the inner diameter R _C of both the rim portions 10 and 10. (D _W <R _C ). Further, when the eccentric amount of both the inner ring raceways 6a and 6b is δ, the dimensions d _W , R _C , and 2δ of each part are regulated so as to satisfy d _W <R _C −2δ. And, preferably, it has a _{_{R C -2δ-d W> 0.05R}} C.

上述の様に、上記各部の寸法ｄ_W 、Ｒ_C 、２δを規制すれば、上記各切り欠き１６、１６部分の外周縁と上記両リム部１０、１０の内周縁との間に、図５に示す様に、常に隙間１４Ａ、１４Ｂが存在する状態となる。尚、これら各隙間１４Ａ、１４Ｂの径方向に関する幅寸法Ｗの最小値は、０．５mm以上確保する。この幅寸法Ｗが０．５mm未満の場合には、上記隙間１４Ａ、１４Ｂ部分がラビリンスシール的に機能する等により、これら両隙間１４Ａ、１４Ｂを通過する潤滑油の量を確保する面から不利になる。これに対して、上記幅寸法Ｗを過大にすると、上記両座板１３Ａ、１３Ｂの内径寄り部分で上記各切り欠き１６、１６の内径側に存在する部分の、径方向に関する幅寸法が短くなって、上記両座板１３Ａ、１３Ｂの強度及び剛性確保が難しくなる。 As described above, if the dimensions d _W , R _C , and 2δ of each part are restricted, the gap between the outer peripheral edge of each of the notches 16 and 16 and the inner peripheral edge of both the rim parts 10 and 10 is shown in FIG. As shown, the gaps 14A and 14B always exist. Note that the minimum value of the width dimension W in the radial direction of each of the gaps 14A and 14B is secured to 0.5 mm or more. When the width dimension W is less than 0.5 mm, the gaps 14A and 14B function as a labyrinth seal, which is disadvantageous in terms of securing the amount of lubricating oil that passes through both the gaps 14A and 14B. Become. On the other hand, if the width dimension W is excessively large, the width dimension in the radial direction of a portion existing on the inner diameter side of each of the notches 16 and 16 near the inner diameter of the both seat plates 13A and 13B is shortened. Thus, it is difficult to ensure the strength and rigidity of the both seat plates 13A and 13B.

上述の様に構成する本例の転がり軸受ユニットによれば、上記両座板１３Ａ、１３Ｂの組み付け作業の容易化と、これら両座板１３Ａ、１３Ｂの支持強度の確保と、前記両円筒ころ軸受５ａ、５ｂに供給する潤滑油の量の確保とを、高次元で並立させられる。
即ち、上記両座板１３Ａ、１３Ｂの内径は、前記回転軸１のうちで前記両偏心カム部３ａ、３ｂに隣接する部分にがたつきなく外嵌自在な大きさとしている。従って、上記両座板１３Ａ、１３Ｂの内径寄り部分を、それぞれ円すいころ軸受２、２を構成する内輪１２、１２の軸方向内端面と前記両偏心カム部３ａ、３ｂの軸方向外端面との間で全周に亙り挟持固定する際に、別途、上記座板１３Ａ、１３Ｂの径方向位置を規制する為の作業を行う必要がない。この為、これら両座板１３Ａ、１３Ｂを所定位置に組み付ける作業を容易に行える。そして、これら両座板１３Ａ、１３Ｂを、上記両内輪１２、１２の軸方向内端面と上記両偏心カム部３ａ、３ｂの軸方向外端面との間で全周に亙り挟持する事により、上記両座板１３Ａ、１３Ｂを、十分に大きな強度で支持できる。 According to the rolling bearing unit of the present example configured as described above, the assembly work of the both seat plates 13A, 13B is facilitated, the support strength of the both seat plates 13A, 13B is ensured, and the both cylindrical roller bearings. Ensuring the amount of lubricating oil supplied to 5a and 5b can be arranged side by side in a high dimension.
In other words, the inner diameters of the both seat plates 13A and 13B are set to a size such that the portions adjacent to the eccentric cam portions 3a and 3b in the rotating shaft 1 can be fitted freely without rattling. Accordingly, the inner diameter portions of the both seat plates 13A, 13B are respectively formed between the axial inner end surfaces of the inner rings 12, 12 constituting the tapered roller bearings 2, 2, and the axial outer end surfaces of the eccentric cam portions 3a, 3b. There is no need to separately perform a work for restricting the radial positions of the seat plates 13A and 13B when sandwiching and fixing over the entire circumference. For this reason, the operation | work which assembles these both seat boards 13A and 13B in a predetermined position can be performed easily. Then, by sandwiching both the seat plates 13A, 13B over the entire circumference between the axial inner end surfaces of the inner rings 12, 12 and the axial outer end surfaces of the eccentric cam portions 3a, 3b, Both seat plates 13A and 13B can be supported with sufficiently large strength.

これら両座板１３Ａ、１３ｂのうちで前記各切り欠き１６、１６の外周縁と、前記両リム部１０、１０の内周縁との間にそれぞれ設けた上記両隙間１４Ａ、１４Ｂは、それぞれが図３〜４に示す様な円弧形で、径方向に関する幅寸法は、円周方向両端まで十分に確保される。又、上記両隙間１４Ａ（１４Ｂ）の円周方向位置は、前記回転軸１の回転に伴う、上記両偏心カム部３ａ、３ｂの回転に伴って、図５の（Ａ）→（Ｂ）→（Ｃ）→（Ｄ）→（Ａ）に示す様に円周方向に移動し、前記両円筒ころ軸受５ａ、５ｂの周方向複数個所から同時に潤滑油を供給する。この為、これら両円筒ころ５ａ、５ｂへの潤滑油の供給量を十分に確保できる。 Of the both seat plates 13A and 13b, the gaps 14A and 14B provided between the outer peripheral edges of the notches 16 and 16 and the inner peripheral edges of the rim portions 10 and 10 are respectively illustrated. In the arc shape as shown in 3-4, the width dimension in the radial direction is sufficiently secured to both ends in the circumferential direction. Further, the circumferential position of both the gaps 14A (14B) is changed from (A) to (B) in FIG. 5 as the eccentric cam portions 3a and 3b rotate along with the rotation of the rotary shaft 1. As shown in (C) → (D) → (A), it moves in the circumferential direction, and lubricating oil is supplied simultaneously from a plurality of locations in the circumferential direction of the cylindrical roller bearings 5a, 5b. For this reason, the supply amount of the lubricating oil to the two cylindrical rollers 5a and 5b can be sufficiently secured.

［実施の形態の第２例］
図７〜８は、本発明の実施の形態の第２例を示している。本例の場合には、座板１３Ｃの径方向中間部外径寄り部分の円周方向等間隔複数個所に、それぞれが円周方向に長い円弧形の透孔１８、１８を形成している。そして、これら各透孔１８、１８を、常に、保持器９ｂを構成するリム部１０の内径側に開口させる様に、各部の寸法を規制している。切り欠き１６、１６が透孔１８、１８に変わった点以外の構成及び作用は、上述した実施の形態の第１例の場合と同様である。 [Second Example of Embodiment]
7 to 8 show a second example of the embodiment of the present invention. In the case of this example, arc-shaped through-holes 18 and 18 that are long in the circumferential direction are formed at a plurality of circumferentially equidistant portions in the portion near the outer diameter of the intermediate portion in the radial direction of the seat plate 13C. . And the dimension of each part is controlled so that these each through-holes 18 and 18 may always be opened to the internal diameter side of the rim | limb part 10 which comprises the holder | retainer 9b. Except for the point that the notches 16 and 16 are changed to the through holes 18 and 18, the configuration and operation are the same as those in the first example of the embodiment described above.

本発明を実施する場合に、切り欠き１６、１６の形状は特に問わない。図６の（Ａ）に示す様な円弧形であっても、（Ｂ）に示す様な角形であっても良い。又、上記各切り欠き１６、１６の数に就いても、複数であれば良く、４個所に限定されず、３個所、５個所、６個所に形成する事もできる。更に、回転軸１を支持する為の回転支持用転がり軸受は、図示の様な円すいころ軸受に限らず、玉軸受、自動調心ころ軸受等、他の転がり軸受であっても良い。 When carrying out the present invention, the shape of the notches 16, 16 is not particularly limited. It may be an arc shape as shown in FIG. 6A or a square shape as shown in FIG. Further, the number of the notches 16 and 16 is not limited to four, and may be formed at three, five, and six places. Further, the rolling support rolling bearing for supporting the rotating shaft 1 is not limited to the tapered roller bearing as shown in the figure, but may be other rolling bearings such as a ball bearing and a self-aligning roller bearing.

本発明の実施の形態の第１例を示す部分断面図。The fragmentary sectional view which shows the 1st example of embodiment of this invention. 図１の右半部拡大図。The right half part enlarged view of FIG. 図１のイ−イ視図。FIG. 同ロ−ロ視図。FIG. 回転軸の回転に伴う各隙間の移動状況を示す、図３と同様の図。The figure similar to FIG. 3 which shows the movement condition of each clearance gap accompanying rotation of a rotating shaft. 座板に設けた切り欠きの形状の２例を示す半部側面図。The half part side view which shows two examples of the shape of the notch provided in the seat plate. 本発明の実施の形態の第２例を示す部分断面図。The fragmentary sectional view which shows the 2nd example of embodiment of this invention. 座板の側面図。The side view of a seat board. 従来構造の１例を示す部分断面図。The fragmentary sectional view which shows one example of the conventional structure. 図９の右半部拡大図。The right half part enlarged view of FIG. 図９のハ−ハ視図。FIG. 同ニ−ニ視図。The same knee view. 回転軸の回転に伴う各隙間の移動状況を示す、図１１と同様の図。The figure similar to FIG. 11 which shows the movement condition of each clearance gap accompanying rotation of a rotating shaft.

符号の説明Explanation of symbols

１回転軸
２円すいころ軸受
３ａ、３ｂ偏心カム部
４ａ、４ｂ振れ回り部材
５ａ、５ｂ円筒ころ軸受
６ａ、６ｂ内輪軌道
７ａ、７ｂ外輪軌道
８ａ、８ｂ円筒ころ
９ａ、９ｂ保持器
１０リム部
１１柱部
１２内輪
１３ａ、１３ｂ、１３Ａ、１３Ｂ、１３Ｃ座板
１４ａ、１４ｂ、１４Ａ、１４Ｂ隙間
１５円孔
１６切り欠き
１７外径寄り部分
１８通孔 DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Tapered roller bearing 3a, 3b Eccentric cam part 4a, 4b Swing member 5a, 5b Cylindrical roller bearing 6a, 6b Inner ring raceway 7a, 7b Outer ring raceway 8a, 8b Cylindrical roller 9a, 9b Cage 10 Rim part 11 Column Part 12 Inner ring 13a, 13b, 13A, 13B, 13C Seat plate 14a, 14b, 14A, 14B Clearance 15 Circular hole 16 Notch 17 Outer diameter portion 18 Through hole

Claims

回転軸と、この回転軸の一部に固設された、この回転軸の回転中心に対し偏心した円筒状の外周面を有し、外径がこの回転軸のうちで隣接する部分の外径よりも大きい偏心カム部と、この偏心カム部の周囲に配置された、円筒状の内周面を有する振れ回り部材と、これら偏心カム部の外周面と振れ回り部材の内周面との間に、保持器に転動自在に保持された状態で設けられた複数個の円筒ころと、上記回転軸のうちで軸方向に関して上記偏心カム部に隣接する部分に設けられて、上記回転軸を回転自在に支持する回転支持用転がり軸受と、この回転支持用転がり軸受を構成する、上記回転軸に外嵌固定された内輪の軸方向端面と上記偏心カム部の軸方向端面との間で挟持固定された座板とを備え、この座板の軸方向片側面と上記保持器の軸方向端面とを軸方向に対向させた転がり軸受ユニットに於いて、上記座板の内径寄り部分を、上記内輪の軸方向端面と上記偏心カム部の軸方向端面との間で全周に亙り挟持固定しており、上記座板の外径寄り部分で上記保持器に軸方向対向する部分の円周方向複数個所に、切り欠き若しくは通孔を形成すると共に、これら各切り欠き若しくは通孔の内接円の直径を、上記保持器の内径よりも小さくした事を特徴とする転がり軸受ユニット。 A rotating shaft and a cylindrical outer peripheral surface that is fixed to a part of the rotating shaft and is eccentric with respect to the rotation center of the rotating shaft, and an outer diameter of the adjacent portion of the rotating shaft A larger eccentric cam portion, a swirling member having a cylindrical inner peripheral surface disposed around the eccentric cam portion, and between the outer peripheral surface of the eccentric cam portion and the inner peripheral surface of the swirling member A plurality of cylindrical rollers provided in a state of being rotatably held by a cage, and a portion of the rotating shaft adjacent to the eccentric cam portion in the axial direction. A rotation-supporting rolling bearing that is rotatably supported, and an axial end surface of the inner ring that is externally fitted and fixed to the rotating shaft and the axial end surface of the eccentric cam portion that constitute the rotating support rolling bearing. A fixed seat plate, one axial side surface of the seat plate and the axial direction of the cage In a rolling bearing unit with the end face facing in the axial direction, the portion near the inner diameter of the seat plate is clamped and fixed over the entire circumference between the axial end face of the inner ring and the axial end face of the eccentric cam portion. In addition, notches or through-holes are formed at a plurality of circumferential positions in a portion near the outer diameter of the seat plate and axially opposed to the retainer, and inscribed in the notches or through-holes. A rolling bearing unit characterized in that the diameter of the circle is smaller than the inner diameter of the cage.

座板の外周縁の円周方向等間隔の複数個所に、この座板の径方向に関する寸法が互いに同じである切り欠きが形成されており、この座板のうちでこれら各切り欠き部分の外径をｄ_W とし、保持器の内径をＲ_C とし、回転軸の回転中心に対する偏心カム部の外周面の中心の偏心量をδとした場合に、ｄ_W ＜Ｒ_C −２δを満たす、請求項１に記載した転がり軸受ユニット。 Notches having the same radial dimension are formed at a plurality of circumferentially equidistant positions on the outer peripheral edge of the seat plate, and outside of the notch portions of the seat plate. When the diameter is d _W , the inner diameter of the cage is R _C, and the amount of eccentricity of the center of the outer peripheral surface of the eccentric cam portion with respect to the rotation center of the rotating shaft is δ, d _W <R _C −2δ is satisfied. Item 6. The rolling bearing unit according to Item 1.

座板の外周縁の円周方向等間隔の複数個所に、この座板の径方向に関する寸法が互いに同じである切り欠きが形成されており、この座板のうちでこれら各切り欠き部分の外径をｄ_W とし、同じくこれら各切り欠きから外れた部分の外径をＤ_W とし、保持器の内径をＲ_C とし、同じく外径をＤ_C とし、回転軸の回転中心に対する偏心カム部の外周面の中心の偏心量をδとした場合に、Ｄ_W ≒（Ｒ_C ＋Ｄ_C ）／２＋２δを満たす、請求項１〜２のうちの何れか１項に記載した転がり軸受ユニット。 Notches having the same radial dimension are formed at a plurality of circumferentially equidistant positions on the outer peripheral edge of the seat plate, and outside of the notch portions of the seat plate. The diameter is d _W , the outer diameter of the part removed from each notch is D _W , the inner diameter of the cage is R _C , the outer diameter is also D _C, and the eccentric cam portion with respect to the rotation center of the rotating shaft The rolling bearing unit according to claim 1, wherein D _w ≈ (R _C + D _C ) / 2 + 2δ is satisfied, where δ is the amount of eccentricity at the center of the outer peripheral surface.