JP2009019672A - Rocking bearing outer ring, rocking bearing and air disc brake device - Google Patents

Rocking bearing outer ring, rocking bearing and air disc brake device Download PDF

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Publication number
JP2009019672A
JP2009019672A JP2007181949A JP2007181949A JP2009019672A JP 2009019672 A JP2009019672 A JP 2009019672A JP 2007181949 A JP2007181949 A JP 2007181949A JP 2007181949 A JP2007181949 A JP 2007181949A JP 2009019672 A JP2009019672 A JP 2009019672A
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Japan
Prior art keywords
rocking bearing
outer ring
cage
rocking
bearing outer
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JP2007181949A
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Japanese (ja)
Inventor
Akihiko Katayama
昭彦 片山
Masaru Kuroda
優 黒田
Haruki Yamada
春樹 山田
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2007181949A priority Critical patent/JP2009019672A/en
Priority to CN2008800222669A priority patent/CN101688553B/en
Priority to US12/666,655 priority patent/US8632256B2/en
Priority to PCT/JP2008/059316 priority patent/WO2009001636A1/en
Priority to EP12176302.3A priority patent/EP2511560B1/en
Priority to EP08764439A priority patent/EP2159436B1/en
Publication of JP2009019672A publication Critical patent/JP2009019672A/en
Withdrawn legal-status Critical Current

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Abstract

<P>PROBLEM TO BE SOLVED: To provide a rocking bearing outer ring for regulating radial movement of rollers and a cage. <P>SOLUTION: The rocking bearing outer ring 12 comprises an arcuate raceway member 13 having a raceway surface 13a on its inner diameter face and a pair of flanges 14 extended from both end parts in the width direction of the raceway member 13 toward the inner side in the radial direction at an acute angle with respect to the raceway surface 13a. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は、揺動軸受用外輪、揺動軸受、およびエアディスクブレーキ装置に関するものである。   The present invention relates to a rocking bearing outer ring, a rocking bearing, and an air disc brake device.

従来の揺動軸受は、例えば、ＷＯ２００６／００２９０５Ａ１（特許文献１）に記載されている。同公報に記載されている揺動軸受は、内径面に軌道面を有する円弧形状である揺動軸受用外輪と、軌道面上に配置される複数のころと、複数のころを保持する保持器とを備える。また、ころおよび保持器の幅方向への移動を規制するために、揺動軸受用外輪の円周方向の全域にわたって幅方向両端部から径方向内側に突出する鍔部が形成されている。   A conventional rocking bearing is described in, for example, WO2006 / 002905A1 (Patent Document 1). The rocking bearing described in the publication includes an arcuate bearing outer ring having a raceway surface on an inner diameter surface, a plurality of rollers disposed on the raceway surface, and a cage that holds the plurality of rollers. With. In addition, in order to restrict the movement of the rollers and the cage in the width direction, flanges that protrude radially inward from both ends in the width direction are formed over the entire circumferential direction of the outer ring for the rocking bearing.

なお、同公報には、上記構成の揺動軸受が、大型商用車、トラック、またはバス等のエアディスクブレーキ装置に使用されると記載されている。
ＷＯ２００６／００２９０５Ａ１ The publication describes that the rocking bearing having the above-described configuration is used in an air disc brake device such as a heavy-duty commercial vehicle, a truck, or a bus.
WO2006 / 002905A1

上記した揺動軸受用外輪は、ころおよび保持器の幅方向への移動を規制する。しかしながら、この揺動軸受用外輪は、ころおよび保持器の径方向への移動を規制することができないので、搬送時や組立て時にころおよび保持器が揺動軸受用外輪の径方向に分離したり、位置ずれが発生するおそれがある。これは、組立て工数の増加や不良品の流出の原因となる。   The above-described rocking bearing outer ring restricts the movement of the rollers and the cage in the width direction. However, this rocking bearing outer ring cannot restrict the movement of the rollers and cage in the radial direction, so that the roller and cage are separated in the radial direction of the rocking bearing outer ring at the time of transportation or assembly. There is a risk of misalignment. This causes an increase in assembly man-hours and outflow of defective products.

そこで、この発明の目的は、ころおよび保持器の幅方向および径方向への移動を規制できる揺動軸受用外輪を提供することである。また、このような揺動軸受用外輪を採用することにより、ころおよび保持器が揺動軸受用外輪の幅方向および径方向に分離しない揺動軸受を提供することである。さらに、このような揺動軸受を採用することにより、生産性が良好なエアディスクブレーキ装置を提供することである。   SUMMARY OF THE INVENTION An object of the present invention is to provide a rocking bearing outer ring capable of restricting movement of rollers and cages in the width direction and radial direction. Another object of the present invention is to provide a rocking bearing in which the roller and the cage are not separated in the width direction and the radial direction of the rocking bearing outer ring by employing such a rocking bearing outer ring. Furthermore, the adoption of such a rocking bearing is to provide an air disc brake device with good productivity.

この発明に係る揺動軸受用外輪は、内径面に軌道面を有する円弧形状の軌道部材と、軌道部材の幅方向両端部から径方向内側に向かって、かつ軌道面に対して鋭角に延びる一対の鍔部とを備える。これにより、ころおよび保持器が揺動軸受用外輪の幅方向および径方向に抜けるのを防止することができると共に、揺動軸受用外輪の製造工程を簡素化することができる。   An outer ring for a rocking bearing according to the present invention includes an arc-shaped race member having a raceway surface on an inner diameter surface, and a pair extending radially inward from both ends in the width direction of the race member and extending at an acute angle with respect to the raceway surface. And a buttock. As a result, it is possible to prevent the rollers and the cage from being pulled out in the width direction and the radial direction of the rocking bearing outer ring, and to simplify the manufacturing process of the rocking bearing outer ring.

好ましくは、鍔部は、第１の鍔部と第１の鍔部と円周方向に隣接する位置に突出長さが相対的に小さい第２の鍔部とを含む。このように、鍔部の円周方向の一部について、その突出長さを減じることにより、揺動軸受用外輪の剛性が低下する。その結果、適切な予圧で揺動軸受用外輪をハウジングに密着させることができる。なお、本明細書中の「鍔部」には、第２の鍔部の突出長さが０ｍｍ、すなわち、第１の鍔部の円周方向に隣接する位置に第２の鍔部が形成されていない場合を含むものとする。   Preferably, the collar includes a first collar, a first collar, and a second collar having a relatively small protrusion length at a position adjacent to the circumferential direction. Thus, the rigidity of the outer ring for rocking bearings is reduced by reducing the protruding length of a part of the collar portion in the circumferential direction. As a result, the rocking bearing outer ring can be brought into close contact with the housing with an appropriate preload. In addition, the protrusion length of the 2nd collar part is 0 mm, and the 2nd collar part is formed in the position adjacent to the circumferential direction of a 1st collar part at "the collar part" in this specification. This includes cases where it is not.

この発明に係る揺動軸受は、上記記載の揺動軸受用外輪と、軌道面上に配置される複数のころと、複数のころを保持し、軌道面と一対の鍔部とで囲まれる領域に位置する保持器とを備える。そして、一対の鍔部の先端の距離は、保持器の最大幅寸法よりも短い。上記構成とすることにより、ころおよび保持器が揺動軸受用外輪の幅方向および径方向に抜けるのを防止することができる。   A rocking bearing according to the present invention includes a rocking bearing outer ring, a plurality of rollers disposed on a raceway surface, a plurality of rollers, and a region surrounded by the raceway surface and a pair of flanges. And a cage located at the same position. And the distance of the front-end | tip of a pair of collar part is shorter than the largest width dimension of a holder | retainer. With the above configuration, it is possible to prevent the rollers and the cage from coming off in the width direction and the radial direction of the rocking bearing outer ring.

好ましくは、保持器は、その幅方向端面に円周方向に連続する突条を有する。突条と鍔部とを係合させれば、保持器が揺動軸受用外輪の径方向に抜けるのを有効に防止することができる。   Preferably, a cage | basket has a protrusion continuous in the circumferential direction at the width direction end surface. By engaging the protrusion and the flange portion, it is possible to effectively prevent the cage from coming off in the radial direction of the outer ring for the rocking bearing.

好ましくは、鍔部は、曲げ加工によって形成される。これにより、鍔部を容易に形成することができる。   Preferably, the collar portion is formed by bending. Thereby, a collar part can be formed easily.

好ましくは、保持器は、ポリアミド４６と、５ｗｔ％〜２０ｗｔ％の繊維状充填材とを含む樹脂製保持器である。ポリアミド４６を母材とする樹脂製保持器を採用する場合、保持器に必要な機械的性質を得るためには、５ｗｔ％以上の繊維状充填材を添加する必要がある。一方、繊維状充填材の含有量が２０ｗｔ％を超えると、保持器の靭性が低下して脆くなる。また、成形時の粘性が高くなり、金型等を用いて保持器を形成することが困難となる。なお、繊維状充填材としては、例えば、炭素繊維やガラス繊維を採用することができる。   Preferably, the cage is a resin cage containing polyamide 46 and 5 wt% to 20 wt% fibrous filler. When a resin cage having a polyamide 46 as a base material is employed, it is necessary to add 5 wt% or more of fibrous filler in order to obtain mechanical properties necessary for the cage. On the other hand, when the content of the fibrous filler exceeds 20 wt%, the toughness of the cage is lowered and becomes brittle. Moreover, the viscosity at the time of shaping | molding becomes high, and it becomes difficult to form a holder | retainer using a metal mold | die etc. In addition, as a fibrous filler, carbon fiber and glass fiber are employable, for example.

この発明に係るエアディスクブレーキ装置は、上記のいずれかに記載の揺動軸受を備える。これにより、生産性が良好なエアディスクブレーキ装置を得ることができる。   An air disc brake device according to the present invention includes any one of the rocking bearings described above. Thereby, an air disc brake device with good productivity can be obtained.

この発明によれば、軌道部材の幅方向両端部から径方向内側に向かって、かつ軌道面に対して鋭角に延びる一対の鍔部を設けることにより、ころおよび保持器の幅方向および径方向への移動を規制できる揺動軸受用外輪を得ることができる。また、このような揺動軸受用外輪を採用することにより、ころおよび保持器が揺動軸受用外輪の径方向に抜けるのを防止した揺動軸受を得ることができる。さらに、このような揺動軸受を採用することにより、生産性が良好なエアディスクブレーキ装置を得ることができる。   According to the present invention, by providing the pair of flanges extending radially inward from both ends in the width direction of the race member and at an acute angle with respect to the raceway surface, in the width direction and the radial direction of the roller and the cage. It is possible to obtain a rocking bearing outer ring capable of restricting the movement of the rocking bearing. Further, by employing such a rocking bearing outer ring, it is possible to obtain a rocking bearing in which the rollers and the cage are prevented from coming off in the radial direction of the rocking bearing outer ring. Furthermore, by adopting such a rocking bearing, an air disc brake device with good productivity can be obtained.

図１〜図５を参照して、この発明の一実施形態に係る揺動軸受１１を説明する。図１は図２のＩ−Ｉにおける断面図、図２は揺動軸受１１の斜視図、図３は図２に示す揺動軸受用外輪１２の斜視図、図４は図３の矢印ＩＶの方向から見た矢視図、図５は図２に示す保持器１６の斜視図である。   A rocking bearing 11 according to an embodiment of the present invention will be described with reference to FIGS. 1 is a cross-sectional view taken along the line II of FIG. 2, FIG. 2 is a perspective view of the rocking bearing 11, FIG. 3 is a perspective view of the outer ring 12 for rocking bearing shown in FIG. FIG. 5 is a perspective view of the cage 16 shown in FIG. 2.

まず、図２を参照して、揺動軸受１１は、揺動軸受用外輪１２と、揺動軸受用外輪１２の軌道面上に配置される複数のころ１５と、複数のころ１５を保持する保持器１６とを備える。   First, referring to FIG. 2, the rocking bearing 11 holds a rocking bearing outer ring 12, a plurality of rollers 15 disposed on the raceway surface of the rocking bearing outer ring 12, and a plurality of rollers 15. And a cage 16.

次に、図１および図３を参照して、揺動軸受用外輪１２は、内径面に軌道面１３ａを有する円弧形状の軌道部材１３と、一対の鍔部１４とを備える。鍔部１４は、軌道部材１３の幅方向両端部から径方向内側に向かって、かつ軌道面１３ａに対して鋭角に延びている。また、軌道部材１３には、その円周方向両端部に外向き突出片１３ｂと、円周方向一方側端部（図３中の左側）に内向き突出片１３ｃと、円周方向他方側端部（図３中の右側）に爪部１３ｄとが形成されている。   Next, referring to FIG. 1 and FIG. 3, the rocking bearing outer ring 12 includes an arc-shaped track member 13 having a track surface 13 a on the inner diameter surface, and a pair of flanges 14. The flange 14 extends radially inward from both ends in the width direction of the track member 13 and extends at an acute angle with respect to the track surface 13a. Further, the track member 13 has outward protruding pieces 13b at both ends in the circumferential direction, inward protruding pieces 13c at one end in the circumferential direction (left side in FIG. 3), and the other end in the circumferential direction. A claw portion 13d is formed on the portion (right side in FIG. 3).

外向き突出片１３ｂは、軌道部材１３の円周方向両端面から径方向外側に向かって延びている。この外向き突出片１３ｂは、ハウジング（図示省略）に係合して、揺動軸受用外輪１２の円周方向の移動を規制する。   The outward projecting pieces 13b extend radially outward from both circumferential end surfaces of the track member 13. The outward projecting piece 13b engages with a housing (not shown) to restrict the circumferential movement of the rocking bearing outer ring 12.

また、内向き突出片１３ｃは、外向き突出片１３ｂの幅方向両側の２箇所から径方向内側に向かって延びている。この内向き突出片１３ｃは、保持器１６の円周方向端面に当接して保持器１６が揺動軸受用外輪１２の円周方向一方側に抜けるのを防止する。   Further, the inwardly projecting piece 13c extends radially inward from two places on both sides in the width direction of the outwardly projecting piece 13b. The inwardly projecting piece 13c abuts on the circumferential end surface of the cage 16 and prevents the cage 16 from being pulled out to one side in the circumferential direction of the outer ring 12 for rocking bearing.

爪部１３ｄは、軌道部材１３の幅方向端面から径方向内側に向かって延びている。爪部１３ｄは、保持器１６の突条１６ｄと係合して保持器１６が揺動軸受用外輪１２の円周方向他方側に抜けるのを防止する。   The claw portion 13 d extends from the end surface in the width direction of the track member 13 toward the inside in the radial direction. The claw portion 13d engages with the protrusion 16d of the retainer 16 to prevent the retainer 16 from coming off to the other side in the circumferential direction of the rocking bearing outer ring 12.

次に、図４を参照して、鍔部１４は、軌道部材１３の円周方向端部の一部にのみ形成されている。具体的には、軌道部材１３の円周方向の中央部領域（「揺動軸受１１の揺動中心を含む領域」を指す。）に位置している。そして、軌道部材１３の円周方向長さをＬ１、鍔部１４の円周方向長さをＬ２とすると、０．２≦Ｌ２／Ｌ１≦０．８を満たすように、鍔部１４の円周方向長さＬ２を設定する。 Next, referring to FIG. 4, the flange portion 14 is formed only at a part of the circumferential end portion of the track member 13. Specifically, the track member 13 is located in the central region in the circumferential direction (refers to “region including the swing center of the swing bearing 11”). Then, when the circumferential length of the race member 13 is L 1 and the circumferential length of the flange 14 is L 2 , the flange portion satisfies 0.2 ≦ L 2 / L 1 ≦ 0.8. 14 to set the circumferential length L 2 of the.

ここで、Ｌ２／Ｌ１≦０．８とすれば、揺動軸受用外輪１２の剛性を十分に低下させることができる。一方、Ｌ２／Ｌ１＜０．２とすれば、保持器１６の円周方向の長さに対しして鍔部１４の円周方向の長さが短すぎて、保持器１６の幅方向への移動を適切に規制することができなくなる。その結果、揺動軸受１１の円周方向に対する保持器１６の傾きが大きくなり、ころ１５および保持器１６の挙動が不安定となる。 Here, if L 2 / L 1 ≦ 0.8, the rigidity of the rocking bearing outer ring 12 can be sufficiently reduced. On the other hand, if L 2 / L 1 <0.2, the circumferential length of the flange portion 14 is too short with respect to the circumferential length of the cage 16, and the width direction of the cage 16 It will not be possible to properly regulate movement to As a result, the inclination of the cage 16 with respect to the circumferential direction of the rocking bearing 11 becomes large, and the behavior of the rollers 15 and the cage 16 becomes unstable.

そこで、上記構成のように鍔部１４を軌道部材１３の円周方向の一部に限定して形成することにより、適切な予圧で揺動軸受用外輪１２をハウジングに密着させることができると共に、保持器１６の幅方向への移動を適切に規制することができる。   Therefore, by forming the flange portion 14 limited to a part in the circumferential direction of the race member 13 as in the above configuration, the outer ring 12 for rocking bearing can be brought into close contact with the housing with an appropriate preload, and The movement of the cage 16 in the width direction can be appropriately restricted.

なお、図４においては、外向き突出片１３ｂ、内向き突出片１３ｃ、および爪部１３ｄの図示を省略している。また、爪部１３ｄは鍔部１４とは異なる役割を担っており、鍔部１４の円周方向長さＬ２には、爪部１３ｄを含まないものとする。 In FIG. 4, the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are not shown. Further, the claw portions 13d are different roles from the flange portion 14, the circumferential length L 2 of the flange portion 14, and does not include the claw portion 13d.

次に、図５を参照して、保持器１６は、円周方向に所定の間隔を設けて複数配置される柱部１６ａと、柱部１６ａの長手方向両端部に配置される円弧形状をなす一対の連結部１６ｂとを備える。また、隣接する柱部１６ａの間にころ１５を保持するポケット１６ｃが形成されている。さらに、連結部１６ｂの幅方向端面（「揺動軸受用外輪１２に組込んだときに鍔部１４に対面する壁面」を指す。）には円周方向に連続する突条１６ｄが形成されている。   Next, referring to FIG. 5, the retainer 16 has a plurality of pillar portions 16 a arranged at predetermined intervals in the circumferential direction, and an arc shape arranged at both longitudinal ends of the pillar portions 16 a. A pair of connecting portions 16b. A pocket 16c for holding the roller 15 is formed between the adjacent column portions 16a. Further, a protrusion 16d that is continuous in the circumferential direction is formed on the end surface in the width direction of the connecting portion 16b (referring to the “wall surface facing the flange 14 when assembled in the outer ring 12 for rocking bearing”). Yes.

さらに、保持器１６の円周方向両端部には、ポケット１６ｃが形成されていない空白領域１６ｅが設けられている。円周方向一方側（図２中の左側）の空白領域１６ｅは、保持器１６の円周方向の端面が内向き突出片１３ｃに衝突したときに、ポケット１６ｃの変形に伴うころ１５の回転不良を防止する。一方、円周方向他方側（図２中の右側）の空白領域１６ｅは、保持器１６が円周方向他方側に最大限偏ったときに、揺動軸受用外輪１２からはみ出す部分なので、ころ１５を配置することができない。   Further, blank regions 16e in which pockets 16c are not formed are provided at both circumferential ends of the cage 16. The blank area 16e on one side in the circumferential direction (left side in FIG. 2) is a rotation failure of the roller 15 due to the deformation of the pocket 16c when the circumferential end surface of the cage 16 collides with the inward protruding piece 13c. To prevent. On the other hand, the blank area 16e on the other side in the circumferential direction (right side in FIG. 2) is a portion that protrudes from the outer ring 12 for the oscillating bearing when the cage 16 is maximally biased toward the other side in the circumferential direction. Can not be placed.

上記構成の保持器１６は、例えば、樹脂材料を射出成形して形成される樹脂保持器とすることができる。具体的には、母材としてのポリアミド４６と、強化材としての繊維状充填材とを含む繊維強化プラスチック（ＦＲＰ）である。ここで、繊維状充填材としては、炭素繊維（ＣＦＲＰ）やガラス繊維（ＧＦＲＰ）を採用することができる。   The cage 16 having the above configuration can be, for example, a resin cage formed by injection molding of a resin material. Specifically, it is a fiber reinforced plastic (FRP) including polyamide 46 as a base material and a fibrous filler as a reinforcing material. Here, carbon fiber (CFRP) or glass fiber (GFRP) can be adopted as the fibrous filler.

なお、保持器１６に必要な機械的性質を得るためには、５ｗｔ％以上の繊維状充填材を添加する必要がある。一方、繊維状充填材の含有量が２０ｗｔ％を超えると、保持器の靭性が低下して脆くなる。また、成形時の粘性が高くなり、金型等を用いて保持器１６を形成することが困難となる。そこで、繊維状充填材の添加量は、５ｗｔ％〜２０ｗｔ％の範囲内とするのが望ましい。   In order to obtain the mechanical properties necessary for the cage 16, it is necessary to add 5 wt% or more of fibrous filler. On the other hand, when the content of the fibrous filler exceeds 20 wt%, the toughness of the cage is lowered and becomes brittle. Moreover, the viscosity at the time of shaping | molding becomes high and it becomes difficult to form the holder | retainer 16 using a metal mold | die. Therefore, it is desirable that the addition amount of the fibrous filler is in the range of 5 wt% to 20 wt%.

次に、図１を参照して、保持器１６は、軌道面１３ａと一対の鍔部１４とで囲まれる領域に位置する。また、鍔部１４の先端の距離は、保持器１６の最大幅寸法よりも短く設定されている。具体的には、左右の突条１６ｄの頂点を結んだ位置が保持器１６の最大幅寸法となる。また、鍔部１４の先端は突条１６ｄよりも径方向内側に位置し、突条１６ｄを径方向内側から保持している。上記構成とすることにより、保持器１６が揺動軸受用外輪１２の径方向に抜けるのを防止する。   Next, referring to FIG. 1, the cage 16 is located in a region surrounded by the raceway surface 13 a and the pair of flanges 14. Further, the distance of the tip of the collar portion 14 is set to be shorter than the maximum width dimension of the cage 16. Specifically, the position connecting the vertices of the left and right protrusions 16d is the maximum width dimension of the cage 16. Moreover, the front-end | tip of the collar part 14 is located in radial direction inner side than the protrusion 16d, and is holding | maintaining the protrusion 16d from radial inside. With the above configuration, the retainer 16 is prevented from coming off in the radial direction of the rocking bearing outer ring 12.

次に、上記構成の揺動軸受用外輪１２の製造方法を説明する。   Next, the manufacturing method of the rocking | fluctuation bearing outer ring | wheel 12 of the said structure is demonstrated.

上記構成の揺動軸受用外輪１２は、例えば、鋼板をプレス加工して製造する。具体的には、まず、打ち抜き加工によって鋼板から略長方形状の平板を得る。次に、曲げ加工によって、軌道部材１３および鍔部１４を形成する。具体的には、平板の長手方向を所定の曲率に湾曲させることにより軌道部材１３を形成することができる。また、平板の短手方向の両端部を起点として軌道面１３ａに対して鋭角に折り曲げることにより鍔部１４を形成することができる。   The rocking bearing outer ring 12 having the above configuration is manufactured by, for example, pressing a steel plate. Specifically, first, a substantially rectangular flat plate is obtained from a steel plate by punching. Next, the track member 13 and the flange portion 14 are formed by bending. Specifically, the track member 13 can be formed by curving the longitudinal direction of the flat plate to a predetermined curvature. Moreover, the collar part 14 can be formed by bend | folding at an acute angle with respect to the track surface 13a from the both ends of the transversal direction of a flat plate.

なお、軌道部材１３の形成工程では複数回の曲げ加工を行い、徐々に所定の曲率に近づけていく。同様に、鍔部１４の形成工程でも複数回の曲げ加工を行い、少しずつ折り曲げていく。また、軌道部材１３を形成するための曲げ加工と、鍔部１４を形成するための曲げ加工とを交互に行い、徐々に揺動軸受用外輪１２の形状に近づけていくのが望ましい。このとき、鍔部１４を軌道部材１３の円周方向の一部に限定して形成するので、鍔部１４を軌道部材１３の円周方向全域に設ける場合と比較して、軌道部材１３および鍔部１４の形成が容易となる。   In the formation process of the race member 13, the bending process is performed a plurality of times, and gradually approaches a predetermined curvature. Similarly, in the step of forming the flange portion 14, bending is performed a plurality of times and bent little by little. In addition, it is desirable that the bending process for forming the race member 13 and the bending process for forming the flange portion 14 are alternately performed so as to gradually approximate the shape of the rocking bearing outer ring 12. At this time, since the flange portion 14 is formed so as to be limited to a part of the circumferential direction of the race member 13, the race member 13 and the flange portion are compared with the case where the flange portion 14 is provided in the entire circumferential direction of the race member 13. Formation of the part 14 becomes easy.

さらに、曲げ加工によって外向き突出片１３ｂ、内向き突出片１３ｃ、および爪部１３ｄを形成する。   Further, the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are formed by bending.

次に、所定の機械的性質を付与するために揺動軸受用外輪１２に熱処理を施す。具体的には、浸炭窒化処理や浸炭焼入れ処理を施す。これにより、表面は硬く、内部は軟らかく靭性の高い性質が得られる。さらに、上記の熱処理によって生じた残留応力や内部ひずみを低減し、靭性の向上や寸法を安定化させるために、上記の熱処理の後に焼戻を行うのが望ましい。   Next, heat treatment is applied to the outer ring 12 for rocking bearing in order to impart predetermined mechanical properties. Specifically, carbonitriding or carburizing and quenching is performed. Thereby, the surface is hard, the inside is soft, and the property with high toughness is obtained. Further, in order to reduce the residual stress and internal strain generated by the heat treatment and to improve the toughness and stabilize the dimensions, it is desirable to perform tempering after the heat treatment.

次に、軌道面１３ａとなる軌道部材１３の内径面の表面粗さを所定値以下にするために、揺動軸受用外輪１２にバレル研磨を施す。軌道面１３ａの表面粗さを所定値以下とすることにより、軌道面１３ａところ１５との間の摩擦抵抗を低減して、揺動時のトルク損失や発熱を抑制することができる。その結果、長寿命で信頼性の高い揺動軸受１１を得ることができる。   Next, in order to make the surface roughness of the inner diameter surface of the raceway member 13 which becomes the raceway surface 13a equal to or less than a predetermined value, barrel polishing is applied to the outer ring 12 for rocking bearing. By setting the surface roughness of the raceway surface 13a to a predetermined value or less, the frictional resistance between the raceway surface 13a and 15 can be reduced, and torque loss and heat generation during swinging can be suppressed. As a result, the rocking bearing 11 having a long life and high reliability can be obtained.

次に、上記構成の揺動軸受１１の組立て方法を説明する。   Next, an assembling method of the rocking bearing 11 having the above configuration will be described.

まず、保持器１６のポケット１６ｃにころ１５を組込む。そして、保持器１６を揺動軸受用外輪１２の軌道面１３ａに沿って挿入し、保持器１６を軌道面１３ａと一対の鍔部１４とで囲まれた領域に配置する。   First, the roller 15 is assembled in the pocket 16 c of the cage 16. Then, the cage 16 is inserted along the raceway surface 13 a of the rocking bearing outer ring 12, and the cage 16 is disposed in a region surrounded by the raceway surface 13 a and the pair of flange portions 14.

そして、予め揺動軸受用外輪１２の曲率半径をハウジングの曲率半径より大きく設定し、揺動軸受用外輪１２の曲率半径を小さくする方向に力（以下、「予圧」という。）を加えながら揺動軸受用外輪１２をハウジングに組込む。   Then, the curvature radius of the rocking bearing outer ring 12 is set in advance to be larger than the curvature radius of the housing, and the rocking is performed while applying a force (hereinafter referred to as “preload”) in the direction of decreasing the curvature radius of the rocking bearing outer ring 12. The outer ring 12 for the dynamic bearing is assembled in the housing.

ここで、上記の実施形態においては、鍔部１４を軌道部材１３の円周方向の一部にのみ形成することによって、揺動軸受用外輪１２の剛性を低下させている。その結果、適切な予圧で揺動軸受用外輪１２をハウジングに密着させることができる。   Here, in the above-described embodiment, the rigidity of the rocking bearing outer ring 12 is reduced by forming the flange portion 14 only in a part of the raceway member 13 in the circumferential direction. As a result, the rocking bearing outer ring 12 can be brought into close contact with the housing with an appropriate preload.

なお、上記の実施形態においては、外向き突出片１３ｂ、内向き突出片１３ｃ、および爪部１３ｄを設けた例を示したが、これらはこの発明の必須の構成要素ではなく、省略することができる。   In the above embodiment, the example in which the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are provided has been described, but these are not essential components of the present invention and may be omitted. it can.

また、上記の実施形態においては、軌道部材１３の円周方向一方側端部に内向き突出片１３ｃを、円周方向他方側端部に爪部１３ｄを設けた例を示したが、これに限ることなく、爪部１３ｄを省略して軌道部材１３の円周方向両端部に内向き突出片１３ｃを設けてもよいし、反対に、内向き突出片１３ｃを省略して軌道部材１３の円周方向両端部に爪部１３ｄを設けてもよい。   In the above embodiment, an example is shown in which the inwardly projecting piece 13c is provided at one end of the track member 13 in the circumferential direction, and the claw portion 13d is provided at the other end in the circumferential direction. Without limitation, the claw portions 13d may be omitted, and the inwardly protruding pieces 13c may be provided at both ends in the circumferential direction of the track member 13, or conversely, the inwardly protruding pieces 13c may be omitted and the circle of the track member 13 may be omitted. You may provide the nail | claw part 13d in the circumferential direction both ends.

また、上記の実施形態においては、保持器１６の幅方向端面に円周方向に連続する突条１６ｄを設けた例を示したが、この発明の必須の構成要素ではなく、省略することができる。   Moreover, in said embodiment, although the example which provided the protrusion 16d continuous in the circumferential direction in the width direction end surface of the holder | retainer 16 was shown, it is not an essential component of this invention and can be abbreviate | omitted. .

ただし、突条１６ｄを省略した場合、保持器１６の径方向への抜けを防止するためには、鍔部１４の先端が保持器１６より径方向内側に位置しなければならない。一方、図１に示すように、突条１６ｄを保持器１６の径方向外側に偏らせて設ければ、鍔部１４の突出長さを短くすることができる。したがって、鍔部１６の突出長さを短くする観点からは、保持器１６の幅方向端面に突条１６ｄを設けて、突出部１４ａと突条１６ｄとを係合させるのが望ましい。   However, when the protrusion 16d is omitted, in order to prevent the retainer 16 from coming off in the radial direction, the tip of the flange portion 14 must be positioned radially inward from the retainer 16. On the other hand, as shown in FIG. 1, if the protrusion 16d is provided so as to be biased radially outward of the cage 16, the protruding length of the flange 14 can be shortened. Therefore, from the viewpoint of shortening the protruding length of the flange portion 16, it is desirable to provide a protrusion 16 d on the end surface in the width direction of the cage 16 and engage the protrusion 14 a and the protrusion 16 d.

また、上記の実施形態においては、保持器１６をポリアミド４６によって形成した例を示したが、これに限ることなく、他の樹脂を採用してもよい。また、樹脂製保持器に限ることなく、鋼板をプレス加工して製造する金属製保持器等であってもよい。   In the above-described embodiment, an example in which the cage 16 is formed of the polyamide 46 has been described. However, the present invention is not limited to this, and other resins may be employed. Further, the present invention is not limited to the resin cage, and may be a metal cage that is manufactured by pressing a steel plate.

上記の実施形態においては、鍔部１４を軌道面１３ａに対して鋭角に曲げることにより、保持器１６が揺動軸受用外輪１２の径方向に抜けるのを防止する。ここで、保持器１６が揺動軸受用外輪１２の径方向に抜けるのを防止する他の方法を考える。   In the above embodiment, the cage 16 is bent at an acute angle with respect to the raceway surface 13 a, thereby preventing the cage 16 from coming off in the radial direction of the rocking bearing outer ring 12. Here, another method for preventing the cage 16 from coming off in the radial direction of the rocking bearing outer ring 12 will be considered.

具体的には、揺動軸受用外輪に軌道部材の幅方向端部から軌道面に対して直角に延びる鍔部と、鍔部の先端から軌道部材の幅方向内側に向かって延びる突出部とを設けて、突出部が保持器を径方向内側から保持するようにしてもよい。   Specifically, the outer ring for the rocking bearing is provided with a flange portion extending from the end in the width direction of the race member at a right angle to the raceway surface, and a protrusion extending from the tip of the flange portion toward the inner side in the width direction of the race member. It may be provided that the protrusion holds the cage from the inside in the radial direction.

上記構成の揺動軸受用外輪の製造方法は、軌道部材の両端部を起点とする曲げ加工によって鍔部を形成する工程と、鍔部の先端部近傍を起点とする曲げ加工によって鍔部の先端に突出部を形成する工程とを含む。一方、この発明の一実施形態に係る揺動軸受用外輪１２は、軌道部材１３の両端部を起点とする曲げ加工のみによって同様の効果を得ることができる。したがって、加工性の観点からは、この発明に係る揺動軸受用外輪１２を採用するのが望ましい。   The manufacturing method of the outer ring for a rocking bearing having the above-described configuration includes a step of forming a flange by bending starting from both ends of the race member, and a tip of the flange by bending starting from the vicinity of the tip of the flange. Forming a protrusion on the surface. On the other hand, the rocking bearing outer ring 12 according to an embodiment of the present invention can obtain the same effect only by bending work starting from both ends of the race member 13. Therefore, from the viewpoint of workability, it is desirable to employ the rocking bearing outer ring 12 according to the present invention.

上記の実施形態においては、鍔部１４を軌道部材１３の円周方向中央部領域に配置した例を示したが、これに限ることなく、任意の位置に任意の個数だけ設けることができる。図６を参照して、この発明の他の実施形態に係る揺動軸受用外輪２２を説明する。図６は揺動軸受用外輪２２の図４に対応する図である。なお、図３および図４に示した揺動軸受用外輪１２との共通点の説明は省略し、相違点を中心に説明する。   In the above-described embodiment, the example in which the collar portion 14 is disposed in the circumferential central region of the track member 13 has been described. However, the present invention is not limited to this, and an arbitrary number can be provided at any position. A rocking bearing outer ring 22 according to another embodiment of the present invention will be described with reference to FIG. FIG. 6 is a view corresponding to FIG. 4 of the outer ring 22 for rocking bearing. The description of the points common to the rocking bearing outer ring 12 shown in FIGS. 3 and 4 is omitted, and the differences will be mainly described.

図６を参照して、揺動軸受用外輪２２は、軌道部材２３と、鍔部２４ａ，２４ｂ（これらを総称して「鍔部２４」という。）とを含む。鍔部２４ａは軌道部材２３の円周方向一方側（図６中の左側）の端部領域に、鍔部２４ｂは軌道部材２３の円周方向他方側（図６中の右側）の端部領域にそれぞれ配置されている。   Referring to FIG. 6, rocking bearing outer ring 22 includes a race member 23 and flanges 24 a and 24 b (these are collectively referred to as “hook 24”). The flange 24a is an end region on one side in the circumferential direction of the track member 23 (left side in FIG. 6), and the flange 24b is an end region on the other side in the circumferential direction of the track member 23 (right side in FIG. 6). Respectively.

このように、鍔部２４ａ，２４ｂを任意の位置に設けた場合でも、軌道部材２３の円周方向長さＬ１と、鍔部２４の円周方向長さＬ２とが０．２≦Ｌ２／Ｌ１≦０．８を満たしていれば、適切な予圧で揺動軸受用外輪２２をハウジングに組込むことができる。なお、この場合における鍔部２４の円周方向長さＬ２は、鍔部２４ａの円周方向長さＬ３と鍔部２４ｂの円周方向長さＬ４との和に一致する。 Thus, the flange portion 24a, even in the case where the 24b at an arbitrary position, the circumferential length L 1 of the raceway member 23, circumferential flange portion 24 the length L 2 and is 0.2 ≦ L If 2 / L 1 ≦ 0.8 is satisfied, the rocking bearing outer ring 22 can be incorporated into the housing with an appropriate preload. Incidentally, the circumferential length L 2 of the flange portion 24 in this case corresponds to the sum of the circumferential length L 4 of the circumferential length L 3 and the flange portion 24b of the flange portion 24a.

図７および図８を参照して、この発明のさらに他の実施形態に係る揺動軸受３１を説明する。なお、揺動軸受１１との共通点の説明は省略し、相違点を中心に説明する。また、図７は揺動軸受３１の斜視図、図８は揺動軸受用外輪３２の斜視図である。   With reference to FIGS. 7 and 8, a rocking bearing 31 according to still another embodiment of the present invention will be described. In addition, description of a common point with the rocking | fluctuation bearing 11 is abbreviate | omitted, and it demonstrates centering on difference. 7 is a perspective view of the rocking bearing 31, and FIG. 8 is a perspective view of the rocking bearing outer ring 32.

まず、図７を参照して、揺動軸受３１は、揺動軸受用外輪３２と、揺動軸受用外輪３２の内径面に沿って配置される複数のころ３５と、複数のころ３５を保持する保持器３６とを備える。なお、保持器３６は図５に示す保持器１６と共通するので、説明は省略する。   First, referring to FIG. 7, rocking bearing 31 holds rocking bearing outer ring 32, a plurality of rollers 35 disposed along the inner diameter surface of rocking bearing outer ring 32, and a plurality of rollers 35. And a retainer 36. In addition, since the holder | retainer 36 is common with the holder | retainer 16 shown in FIG. 5, description is abbreviate | omitted.

次に、図８を参照して、揺動軸受用外輪３２は、内径面に軌道面３３ａを有する円弧形状（この実施形態では中心角が１８０°の半円形状）の軌道部材３３と、軌道部材３３の幅方向両端部から径方向内側に突出して、ころ３５および保持器３６の幅方向の移動を規制する鍔部３４とを含む。   Next, referring to FIG. 8, the rocking bearing outer ring 32 includes a raceway member 33 having an arc shape (in this embodiment, a semicircular shape with a central angle of 180 °) having a raceway surface 33 a on the inner diameter surface, and a raceway. It includes a flange 34 that protrudes radially inward from both widthwise ends of the member 33 and restricts the movement of the rollers 35 and the cage 36 in the width direction.

軌道部材３３には、その円周方向両端部に外向き突出片３３ｂと、円周方向一方側端部（図８中の左側）に内向き突出片３３ｃと、円周方向他方側端部（図８中の右側）に爪部３３ｄとが設けられている。   The track member 33 has outwardly protruding pieces 33b at both ends in the circumferential direction, an inwardly protruding piece 33c at one end in the circumferential direction (left side in FIG. 8), and the other end in the circumferential direction ( A claw portion 33d is provided on the right side in FIG.

なお、外向き突出片３３ｂ、内向き突出片３３ｃ、および爪部３３ｄの構成および機能は、それぞれ外向き突出片１３ｂ、内向き突出片１３ｃ、および爪部１３ｄと共通するので、説明は省略する。また、図７のＩ−Ｉにおける断面図は図１と共通するので、説明は省略する。   The configuration and function of the outwardly projecting piece 33b, the inwardly projecting piece 33c, and the claw portion 33d are the same as those of the outwardly projecting piece 13b, the inwardly projecting piece 13c, and the claw portion 13d. . Further, the cross-sectional view taken along the line II in FIG. 7 is the same as that in FIG.

鍔部３４は、第１の鍔部３４ａと、第１の鍔部３４ａと円周方向に隣接する位置に第１の鍔部３４ａより突出長さが相対的に小さい第２の鍔部（図示せず）とを含む。ただし、この実施形態においては、第２の鍔部の突出長さが０ｍｍ、すなわち、第２の鍔部が設けられていない。また、第１の鍔部３４ａは、軌道部材３３の幅方向両端部から径方向内側に向かって、かつ軌道面３３ａに対して鋭角に延びている。   The collar part 34 includes a first collar part 34a and a second collar part having a relatively small protrusion length from the first collar part 34a at a position adjacent to the first collar part 34a in the circumferential direction (see FIG. Not shown). However, in this embodiment, the protruding length of the second flange portion is 0 mm, that is, the second flange portion is not provided. The first flange 34a extends radially inward from both ends in the width direction of the track member 33 and extends at an acute angle with respect to the track surface 33a.

上記構成としても、この発明の効果を得ることができる。また、鍔部３４の円周方向の一部について、その突出長さを減じることにより、揺動軸受用外輪３２の剛性を低下させることができる。その結果、適切な予圧で揺動軸受用外輪３２をハウジングに密着させることができる。   The effects of the present invention can also be obtained with the above configuration. Moreover, the rigidity of the outer ring 32 for rocking | fluctuation bearings can be reduced by reducing the protrusion length about a part of the circumferential direction of the collar part 34. FIG. As a result, the rocking bearing outer ring 32 can be brought into close contact with the housing with an appropriate preload.

揺動軸受用外輪３２の製造方法は揺動軸受用外輪１２と共通するので、詳しい説明は省略する。なお、この実施形態においては、鍔部３４を軌道部材３３の円周方向の一部に限定して形成する（隣接する第１の鍔部３４ａの間には鍔部の形成されていない領域が存在する）ので、鍔部を軌道部材の円周方向全域に設ける場合と比較して、軌道部材３３および鍔部３４の形成が容易となる。   Since the manufacturing method of the rocking bearing outer ring 32 is the same as that of the rocking bearing outer ring 12, detailed description thereof is omitted. In this embodiment, the flange portion 34 is formed so as to be limited to a part of the raceway member 33 in the circumferential direction (a region where no flange portion is formed between the adjacent first flange portions 34a). Therefore, the formation of the track member 33 and the flange portion 34 is facilitated as compared with the case where the flange portion is provided in the entire circumferential direction of the track member.

なお、上記の実施形態においては、複数の第１の鍔部３４ａを円周方向に所定の間隔を空けて配置した（第２の鍔部の突出長さが０ｍｍ）例を示したが、これに限ることなく、第１の鍔部３４ａと円周方向に隣接する位置に第２の鍔部を設けてもよい。第２の鍔部の突出長さを第１の鍔部３４ａより小さくすれば、従来の揺動軸受用外輪と比較して剛性を低下させることができる。   In the above-described embodiment, an example in which the plurality of first flange portions 34a are arranged at predetermined intervals in the circumferential direction (the protrusion length of the second flange portion is 0 mm) has been described. However, the second flange may be provided at a position adjacent to the first flange 34a in the circumferential direction. If the protruding length of the second flange portion is made smaller than that of the first flange portion 34a, the rigidity can be reduced as compared with the conventional outer ring for a rocking bearing.

さらには、上記の各実施形態においては、鍔部１４，２４，３４を軌道部材１３，２３，３３の一部にのみ形成した例を示したが、これに限ることなく、鍔部を軌道部材の円周方向全域に設けてもこの発明の効果を得ることができる。   Furthermore, in each of the above-described embodiments, the example in which the flange portions 14, 24, 34 are formed only on a part of the track members 13, 23, 33 has been shown. The effect of the present invention can be obtained even if it is provided in the entire circumferential direction.

次に、図９および図１０を参照して、この発明の一実施形態に係るエアディスクブレーキ装置７１を説明する。なお、図９はエアディスクブレーキ装置７１の概略断面図、図１０は制動機構８０の部分拡大図である。   Next, an air disc brake device 71 according to an embodiment of the present invention will be described with reference to FIGS. 9 and 10. 9 is a schematic sectional view of the air disc brake device 71, and FIG. 10 is a partially enlarged view of the braking mechanism 80.

まず、図９を参照して、エアディスクブレーキ装置７１は、タイヤ（図示省略）と一体回転するブレーキディスク７２（「ロータ」ともいう）と、一対のブレーキパッド７３，７４と、ブレーキシリンダ７５と、制動機構８０とを主に備える。   First, referring to FIG. 9, an air disc brake device 71 includes a brake disc 72 (also referred to as “rotor”) that rotates integrally with a tire (not shown), a pair of brake pads 73 and 74, and a brake cylinder 75. The brake mechanism 80 is mainly provided.

一対のブレーキパッド７３，７４は、ブレーキディスク７２の軸方向に隣接する位置に配置されている。また、ブレーキディスク７２とブレーキパッド７３，７４との間には、非制動状態（ブレーキペダルを踏み込んでいない状態を指す）において、所定の隙間が設けられている。   The pair of brake pads 73 and 74 are disposed at positions adjacent to the brake disk 72 in the axial direction. In addition, a predetermined gap is provided between the brake disc 72 and the brake pads 73 and 74 in a non-braking state (referring to a state where the brake pedal is not depressed).

ブレーキシリンダ７５は、容積が可変の空気室７６と、空気室７６への空気の供給および排出を行う吸排気口７７と、空気室７６の容積の変化に伴って軸方向（「図９中の矢印Ａの方向およびその反対方向」を指す）に移動するアクチュエータロッド７８と、アクチュエータロッド７８を空気室７６の容積を減じる方向に付勢する弾性部材としてのコイルばね７９とを含む。   The brake cylinder 75 includes an air chamber 76 having a variable volume, an intake / exhaust port 77 that supplies and discharges air to and from the air chamber 76, and an axial direction (“in FIG. An actuator rod 78 that moves in the direction of arrow A and the opposite direction thereof, and a coil spring 79 as an elastic member that urges the actuator rod 78 in a direction that reduces the volume of the air chamber 76.

制動機構８０は、一方側端部に揺動部材８１を有し、他方側端部でアクチュエータロッド７８と連結し、揺動部材８１の揺動中心Ｇを中心として回動する回動レバー８２と、揺動部材８１を揺動自在に支持するこの発明の一実施形態に係る揺動軸受１１と、揺動部材８１の揺動中心Ｇから外れた位置に取り付けられて、軸方向（「図９中の矢印Ｂの方向およびその反対方向」を指す）に移動するトラバース８３と、トラバース８３をブレーキパッド７３，７４から遠ざける方向に付勢する弾性部材としてのコイルばね８４とを含む。   The brake mechanism 80 has a swing member 81 at one end, is connected to the actuator rod 78 at the other end, and rotates around a swing center G of the swing member 81. The swinging bearing 11 according to an embodiment of the present invention that swingably supports the swinging member 81 is attached to a position deviated from the swinging center G of the swinging member 81 in the axial direction (see FIG. 9). And a coil spring 84 as an elastic member that urges the traverse 83 in a direction away from the brake pads 73 and 74.

上記構成のエアディスクブレーキ装置７１は、例えば、大型商用車、トラック、またはバス等の大型で大きな制動力を必要とする車両等に採用される。   The air disk brake device 71 having the above-described configuration is employed in, for example, a large vehicle requiring a large braking force, such as a large commercial vehicle, a truck, or a bus.

上記構成のエアディスクブレーキ装置７１の動作を説明する。まず、ブレーキペダル（図示省略）を踏み込むと、吸排気口７７から空気室７６に空気が供給され、空気室７６の容積が増大する。空気室７６の容積の増大に伴って、アクチュエータロッド７８がコイルばね７９の弾性力に逆らって矢印Ａの方向に移動する。アクチュエータロッド７８に押された回動レバー８２は、揺動中心Ｇの周りを反時計回りに回動する（回動後の回動レバー８２の位置を図１０に一点鎖線で示す）。揺動部材８１の揺動中心Ｇから外れた位置に取り付けられたトラバース８３は、コイルばね８４の弾性力に逆らって矢印Ｂの方向に移動する。これにより、ブレーキパッド７３，７４がブレーキディスク７２に押し付けられて、タイヤの回転が制動される。   The operation of the air disc brake device 71 configured as described above will be described. First, when a brake pedal (not shown) is depressed, air is supplied from the intake / exhaust port 77 to the air chamber 76, and the volume of the air chamber 76 increases. As the volume of the air chamber 76 increases, the actuator rod 78 moves in the direction of arrow A against the elastic force of the coil spring 79. The turning lever 82 pushed by the actuator rod 78 turns counterclockwise around the swing center G (the position of the turning lever 82 after turning is indicated by a one-dot chain line in FIG. 10). A traverse 83 attached at a position off the swing center G of the swing member 81 moves in the direction of arrow B against the elastic force of the coil spring 84. As a result, the brake pads 73 and 74 are pressed against the brake disc 72, and the rotation of the tire is braked.

一方、ブレーキペダルを緩めると、空気室７６内の空気が吸排気口７７から排出され、空気室７６の容積が減少する。空気室７６の容積の減少に伴って、コイルばね７９がアクチュエータロッド７８を矢印Ａと反対方向に移動させる。アクチュエータロッド７８に連結された回動レバー８２は、揺動中心Ｇの周りを時計回りに回動する。そして、コイルばね８４がトラバース８３を矢印Ｂと反対方向に移動させる。これにより、ブレーキディスク７２とブレーキパッド７３，７４との間に所定の隙間が形成されて、タイヤの制動が解除される。   On the other hand, when the brake pedal is loosened, the air in the air chamber 76 is discharged from the intake / exhaust port 77, and the volume of the air chamber 76 decreases. As the volume of the air chamber 76 decreases, the coil spring 79 moves the actuator rod 78 in the direction opposite to the arrow A. The rotation lever 82 connected to the actuator rod 78 rotates clockwise around the swing center G. The coil spring 84 moves the traverse 83 in the direction opposite to the arrow B. As a result, a predetermined gap is formed between the brake disc 72 and the brake pads 73 and 74, and the braking of the tire is released.

上記構成のエアディスクブレーキ装置７１において、揺動部材８１を揺動自在に支持する軸受として、この発明の一実施形態に係る揺動軸受１１を採用することにより、生産性が良好なエアディスクブレーキ装置７１を得ることができる。   In the air disc brake device 71 configured as described above, the air disc brake having good productivity can be obtained by adopting the rocking bearing 11 according to the embodiment of the present invention as a bearing that supports the rocking member 81 in a swingable manner. A device 71 can be obtained.

以上、図面を参照してこの発明の実施形態を説明したが、この発明は、図示した実施形態のものに限定されない。図示した実施形態に対して、この発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。   As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

この発明は、揺動軸受用外輪、揺動軸受、およびエアディスクブレーキ装置に有利に利用される。   The present invention is advantageously used in an outer ring for a rocking bearing, a rocking bearing, and an air disc brake device.

図２のＩ−Ｉにおける断面図である。It is sectional drawing in II of FIG. この発明の一実施形態に係る揺動軸受の斜視図である。1 is a perspective view of a rocking bearing according to an embodiment of the present invention. 図２に示す揺動軸受用外輪の斜視図である。It is a perspective view of the outer ring | wheel for rocking | fluctuation bearings shown in FIG. 図３の矢印ＩＶの方向から見た矢視図である。FIG. 4 is an arrow view seen from the direction of arrow IV in FIG. 3. 図２に示す保持器の斜視図である。It is a perspective view of the holder | retainer shown in FIG. 図４の他の実施形態を示す図である。It is a figure which shows other embodiment of FIG. この発明の他の実施形態に係る揺動軸受の斜視図である。It is a perspective view of the rocking | fluctuation bearing which concerns on other embodiment of this invention. 図７に示す揺動軸受用外輪の斜視図である。It is a perspective view of the outer ring | wheel for rocking | fluctuation bearings shown in FIG. この発明の一実施形態に係るエアディスクブレーキ装置を示す図である。It is a figure showing an air disc brake device concerning one embodiment of this invention. 図９の部分拡大図である。FIG. 10 is a partially enlarged view of FIG. 9.

符号の説明Explanation of symbols

１１，３１ 揺動軸受、１２，２２，３２ 揺動軸受用外輪、１３，２３，３３ 軌道部材、１３ａ，３３ａ 軌道面、１３ｂ，３３ｂ 外向き突出片、１３ｃ，３３ｃ 内向き突出片、１３ｄ，３３ｄ 爪部、１４，２４ａ，２４ｂ，３４，３４ａ 鍔部、１５，３５ ころ、１６，３６ 保持器、１６ａ，３６ａ 柱部、１６ｂ，３６ｂ 連結部、１６ｃ，３６ｃ ポケット、１６ｄ，３６ｄ 突条、１６ｅ，３６ｅ 空白領域、７１ エアディスクブレーキ装置、７２ ブレーキディスク、７３，７４ ブレーキパッド、７５ ブレーキシリンダ、７６ 空気室、７７ 吸排気口、７８ アクチュエータロッド、７９，８４ コイルばね、８０ 制動機構、８１ 揺動部材、８２ 回転レバー、８３ トラバース。   11, 31 Oscillating bearing, 12, 22, 32 Oscillating bearing outer ring, 13, 23, 33 Race member, 13a, 33a Race surface, 13b, 33b Outward projecting piece, 13c, 33c Inward projecting piece, 13d, 33d Claw part, 14, 24a, 24b, 34, 34a collar part, 15, 35 roller, 16, 36 cage, 16a, 36a pillar part, 16b, 36b connecting part, 16c, 36c pocket, 16d, 36d ridge, 16e, 36e Blank area, 71 Air disc brake device, 72 Brake disc, 73, 74 Brake pad, 75 Brake cylinder, 76 Air chamber, 77 Air intake / exhaust port, 78 Actuator rod, 79, 84 Coil spring, 80 Braking mechanism, 81 Swing member, 82 rotation lever, 83 traverse.

Claims (7)

内径面に軌道面を有する円弧形状の軌道部材と、
前記軌道部材の幅方向両端部から径方向内側に向かって、かつ前記軌道面に対して鋭角に延びる一対の鍔部とを備える、揺動軸受用外輪。 An arc-shaped raceway member having a raceway surface on the inner diameter surface;
A rocking bearing outer ring comprising: a pair of flanges extending radially inward from both ends in the width direction of the race member and extending at an acute angle with respect to the raceway surface. 前記鍔部は、第１の鍔部と、前記第１の鍔部と円周方向に隣接する位置に突出長さが相対的に小さい第２の鍔部とを含む、請求項１に記載の揺動軸受用外輪。   The said collar part is a 1st collar part, The 2nd collar part whose protrusion length is relatively small in the position adjacent to the said 1st collar part and the circumferential direction of Claim 1 characterized by the above-mentioned. Outer ring for rocking bearing. 請求項１または２に記載の揺動軸受用外輪と、
前記軌道面上に配置される複数のころと、
前記複数のころを保持し、前記軌道面と前記一対の鍔部とで囲まれる領域に位置する保持器とを備え、
前記一対の鍔部の先端の距離は、前記保持器の最大幅寸法よりも短い、揺動軸受。 An outer ring for a rocking bearing according to claim 1 or 2,
A plurality of rollers arranged on the raceway surface;
Holding the plurality of rollers, and comprising a cage located in a region surrounded by the raceway surface and the pair of flanges,
The distance between the tips of the pair of flanges is a swing bearing that is shorter than the maximum width of the cage. 前記保持器は、その幅方向端面に円周方向に連続する突条を有する、請求項３に記載の揺動軸受。   The rocking bearing according to claim 3, wherein the cage has a ridge that is continuous in a circumferential direction on an end surface in a width direction thereof. 前記鍔部は、曲げ加工によって形成される、請求項３または４に記載の揺動軸受。   The rocking bearing according to claim 3 or 4, wherein the flange is formed by bending. 前記保持器は、ポリアミド４６と、５ｗｔ％〜２０ｗｔ％の繊維状充填材とを含む樹脂製保持器である、請求項３〜５のいずれかに記載の揺動軸受。   The rocking bearing according to any one of claims 3 to 5, wherein the cage is a resin cage including a polyamide 46 and a fibrous filler of 5 wt% to 20 wt%. 請求項３〜６のいずれかに記載の揺動軸受を備える、エアディスクブレーキ装置。   An air disc brake device comprising the rocking bearing according to claim 3.
JP2007181949A 2007-06-28 2007-07-11 Rocking bearing outer ring, rocking bearing and air disc brake device Withdrawn JP2009019672A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2007181949A JP2009019672A (en) 2007-07-11 2007-07-11 Rocking bearing outer ring, rocking bearing and air disc brake device
CN2008800222669A CN101688553B (en) 2007-06-28 2008-05-21 Rocking bearing outer ring, rocking bearing, air disc brake device, fitting structure for rocking bearing outer ring
US12/666,655 US8632256B2 (en) 2007-06-28 2008-05-21 Rocking bearing outer ring, rocking bearing, air disc brake device, and fitting structure of rocking bearing outer ring
PCT/JP2008/059316 WO2009001636A1 (en) 2007-06-28 2008-05-21 Rocking bearing outer ring, rocking bearing, air disc brake device, fitting structure for rocking bearing outer ring
EP12176302.3A EP2511560B1 (en) 2007-06-28 2008-05-21 Rocking bearing and fitting structure of rocking bearing outer ring
EP08764439A EP2159436B1 (en) 2007-06-28 2008-05-21 Rocking bearing outer ring, rocking bearing, air disc brake device, fitting structure for rocking bearing outer ring

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007181949A JP2009019672A (en) 2007-07-11 2007-07-11 Rocking bearing outer ring, rocking bearing and air disc brake device

Publications (1)

Publication Number Publication Date
JP2009019672A true JP2009019672A (en) 2009-01-29

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JP2007181949A Withdrawn JP2009019672A (en) 2007-06-28 2007-07-11 Rocking bearing outer ring, rocking bearing and air disc brake device

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011007092A (en) * 2009-06-25 2011-01-13 Jtekt Corp Rocker arm

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011007092A (en) * 2009-06-25 2011-01-13 Jtekt Corp Rocker arm

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