JPH11247845A - Bearing device for roller support - Google Patents

Bearing device for roller support

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Publication number
JPH11247845A
JPH11247845A JP4659198A JP4659198A JPH11247845A JP H11247845 A JPH11247845 A JP H11247845A JP 4659198 A JP4659198 A JP 4659198A JP 4659198 A JP4659198 A JP 4659198A JP H11247845 A JPH11247845 A JP H11247845A
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Japan
Prior art keywords
roller
surface
portion
diameter side
peripheral surface
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JP4659198A
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Japanese (ja)
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JP3815027B2 (en
Inventor
Toshiyuki Yamamoto
敏之 山本
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Nippon Seiko Kk
日本精工株式会社
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Publication of JP3815027B2 publication Critical patent/JP3815027B2/en
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Abstract

PROBLEM TO BE SOLVED: To prevent damaging to a contact part by preventing excessive bearing of the contact part and preventing application of an edge load on the contact part at the time of occurrence of misalignment.
SOLUTION: Cylindrical surface parts 13, 13a are respectively provided at an intermediate part in the axial direction of an outer peripheral surface of inner diametrical side and outer diametrical side both rollers 8a, 9a. Inclined surface parts 14, 14a are provided on both sides of both of these cylindrical surface parts 13, 13a. A contact area with a mating surface is secured by the cylindrical surface parts 13, 13a. Additionally, generation of an edge load on the contact part with the mating surface is prevented by the inclined surface parts 14, 14a at the time of occurrence of misalignment.
COPYRIGHT: (C)1999,JPO

Description

【発明の詳細な説明】 DETAILED DESCRIPTION OF THE INVENTION

【0001】 [0001]

【発明の属する技術分野】この発明に係るローラ支持用軸受装置は、例えばタペットローラ軸受としてエンジンの動弁機構中に組み込み、動弁機構部分の摩擦を少なくして、エンジン運転時に於ける燃料消費率の低減を図る為に利用する。 Roller support bearing device according to the Field of the Invention The present invention, for example, incorporated into a valve operating mechanism of the engine as a tappet roller bearings, with less friction of the valve mechanism portion, in fuel consumption during engine operation to use in order to reduce the rate.

【0002】 [0002]

【従来の技術】エンジン内部での摩擦低減を図り、燃焼消費率を低減する事を目的として、クランクシャフトと同期したカムシャフトの回転を給気弁及び排気弁の往復運動に変換する部分に、タペットローラ軸受を組み込む事が一般的に行われている。 Achieving friction reduction of the Related Art In an internal engine, with the aim of reducing the fuel consumption rate, the portion for converting the rotation of the camshaft in synchronism with the crank shaft into reciprocating motion of the air supply and exhaust valves, to incorporate the tappet roller bearing it is generally performed. 図7〜8は、実開平3−1 7-8, the actual No. 3-1
08806号公報に記載されたタペットローラ軸受を示している。 It shows a tappet roller bearing described in 08806 JP.

【0003】エンジンのクランクシャフトと同期して回転するカムシャフト1に固定したカム2に対向して、このカム2の動きを受けるロッカーアーム3を設けている。 [0003] opposite to the cam 2 fixed to the cam shaft 1 rotates synchronously with the engine crank shaft, and a rocker arm 3 which receives the movement of the cam 2 is provided. このロッカーアーム3の端部には1対の支持壁部4、4を、互いに間隔を開けて設けている。 The support wall portions 4 of the pair of the end portion of the rocker arm 3 is provided at a distance from each other. この1対の支持壁部4、4の間には、鋼製で中空又は中実の支持軸5を掛け渡している。 Between the support wall 4, 4 of the pair is passing over the support shaft 5 of the hollow or solid in steel. この支持軸5の両端は焼き入れする事なく、生のままとしており、支持軸5を固定する際には、この未焼き入れ部分を、上記1対の支持壁部4、 Without the put both ends of the support shaft 5 is baked, has a raw, when fixing the support shaft 5, the non-quenched portions, the pair of support walls 4,
4に形成した通孔7、7の内周面に向けてかしめ付ける。 Caulked toward the inner circumferential surface of the formed hole 7,7 to 4. 上述の様にして、1対の支持壁部4、4の間に掛け渡した支持軸5の周囲にはローラ6を、回転自在に支承しており、このローラ6の外周面を、上記カム2の外周面に当接させている。 In the manner described above, the roller 6 around the supporting shaft 5 which spanned between a pair of support wall portions 4, has supported rotatably, the outer peripheral surface of the roller 6, the cam and it is brought into contact with the outer peripheral surface of the two.

【0004】上述の様に構成するタペットローラ軸受によれば、ロッカーアーム3とカム2との間に働く摩擦力を低減し、エンジン運転時に於ける燃料消費率の低減を図れる。 [0004] According to the tappet roller bearing constructed as described above, to reduce the frictional force acting between the rocker arm 3 and the cam 2, thereby reducing the in fuel consumption during engine operation. この様なタペットローラ軸受の設置部分にはエンジン運転時に、エンジンオイルを供給する。 During engine operation in the mounting portion of such tappet roller bearing, for supplying engine oil. そして、 And,
このエンジンオイルによって、カム2の外周面とローラ6の外周面との間、及び支持軸5の外周面とローラ6の内周面との間を潤滑する。 This engine oil to lubricate the space between the inner circumferential surface of the outer circumferential surface and the roller 6 between, and the support shaft 5 between the outer peripheral surface and the outer peripheral surface of the roller 6 of the cam 2.

【0005】尚、タペットローラ軸受の構成部品の材質としては、カム2を含むカムシャフト1は鋳鉄若しくは軸受鋼により、ローラ6及び支持軸5は高炭素クロム軸受鋼により、それぞれ造る事が、必要な強度を確保しつつ材料費、加工費を抑える面から、一般的に行われている。 [0005] Incidentally, as the material of the components of the tappet roller bearing, the camshaft 1 including a cam 2 by cast iron or bearing steel, the roller 6 and the support shaft 5 is high-carbon chromium bearing steel, be made respectively, need material costs while ensuring a strength, in terms of suppressing the processing costs, is generally performed. そして、各部材の周面同士の間の隙間寸法並びに表面粗さを工夫する事により、エンジン運転時に於ける各部材同士の摺接部の潤滑性を確保する様にしている。 Then, by devising the gap size and surface roughness between the adjacent peripheral surfaces of the members, and the like to ensure the lubrication of the sliding contact portions of the members to each other in during engine operation. この様な潤滑性確保をより確実に行う為、支持軸5を燐青銅により、ローラ6を高炭素クロム軸受鋼により、それぞれ造る事も、一部で行われている。 To do such a lubricity secured more reliably, by the support shaft 5 of phosphor bronze, by the roller 6 high carbon chromium bearing steel, also be made respectively, it has been made by some. 又、ロッカーアーム3及び支持軸5にエンジンオイル供給用の給油孔を開設する事も、例えば実開平4−32210号公報に記載されている様に、従来から提案されている。 Further, it is also, as is described in JP real-Open No. 4-32210 to open the oil supply hole for engine oil supplied to the rocker arm 3 and the support shaft 5, it has been proposed. 更に、ローラ6を窒化珪素等のセラミックにより造る事も、例えば特開平4−15296号公報、実開昭62−20391 Furthermore, it is also, for example, JP-A 4-15296 discloses building a roller 6 by a ceramic such as silicon nitride, Japanese Utility Model 62-20391
1号公報、実開平3−108806号公報等に記載されている様に、従来から提案されている。 1 discloses, as is described in the real Hei 3-108806 Patent Publication, have been proposed.

【0006】又、ローラの内外両周面と相手面との間の潤滑が不十分な場合でも、これら転がり接触或は滑り接触する面に、著しい摩耗や焼き付き等の損傷が発生する事を防止する為の考慮も、従来から各種提案されている。 [0006] Further, even when the lubrication between the inner and outer peripheral surfaces and mating surface of the roller is insufficient, preventing the surface of these rolling contact or sliding contact, that damage such as significant wear and seizure occurs consideration for also, have been proposed in the past. 例えば、特開昭59−183007号公報には、ローラの内外両周面に、軟窒化処理、酸化処理等の耐スカッフィング性表面処理を行なう事が記載されている。 For example, JP-A-59-183007, the inner and outer peripheral surfaces of the roller, nitrocarburizing treatment, it is described that performs a scuffing resistance surface treatment such as oxidation treatment.
又、実開昭60−12604〜5号公報には、ローラを支持する支持軸の外周面とこのローラの内周面との間に、スリーブ或はリングを設ける事が記載されている。 Also, the Japanese Unexamined Utility Model Publication No. 60-12604~5, between the outer peripheral surface of the support shaft which supports the roller and the inner circumferential surface of the roller, have been described by providing the sleeve or ring.
又、特開平8−74526号公報には、互いに対向するローラの内周面と支持軸の外周面とのうちの少なくとも一方に、摩擦低減用の表面処理層を形成する事が記載されている。 Further, JP-A-8-74526 discloses a in at least one of an inner peripheral surface and the outer circumferential surface of the support shaft of the roller which are opposed to each other, by forming a surface treatment layer for reducing friction .

【0007】又、ローラの回転抵抗を小さくする為に、 [0007] In addition, in order to reduce the rotational resistance of the roller,
このローラを二重構造とする事も、例えば実公昭46− Possible to the roller double structure also, for example, the actual Publication 46-
9606号公報に記載されている様に、従来から知られている。 As is described in 9606 JP, it is known in the art. 更には、特開平8−296412号公報には、 Furthermore, JP-A-8-296412,
この様に二重構造のローラを有する構造で、何れかのローラの周面を、軸方向中央部が膨らんだ断面円弧状に形成する事が記載されている。 In the structure having the roller of such a double structure, the peripheral surface of one of the rollers, be formed into an arcuate cross section bulging axial central portion is described. 図9(A)及び図10 FIGS. 9 (A) and 9 10
(A)に、この特開平8−296412号公報に記載された構造を示している。 (A), the shows the structure described in this Japanese Patent 8-296412 discloses. この構造では、ローラ6aは、 In this structure, the roller 6a is
内径側ローラ8と外径側ローラ9とを組み合わせて成る。 Comprising a combination of an inner diameter side roller 8 and the outer diameter side roller 9. このうちの内径側ローラ8は、内周面10を円筒面とし、外周面11を球状凸面としている。 The inner diameter side roller 8 of which is the inner peripheral surface 10 and a cylindrical surface, and the outer peripheral surface 11 and the spherical bulge. この様な内径側ローラ8は、ロッカーアーム3に設けた1対の支持壁部4、4の間に掛け渡した支持軸5の周囲に、回転自在に支持している。 Such internal diameter side roller 8 around the supporting shaft 5 which spanned between the support wall portions 4 of the pair provided on the rocker arm 3 is rotatably supported. 又、上記外径側ローラ9は、内外両周面とも円筒面とし、上記内径側ローラ8の周囲に、回転自在に支持している。 Also, the outside diameter side roller 9, and a cylindrical surface with the inner and outer peripheral surfaces, around the inner diameter side roller 8 is rotatably supported. この様に、内径側ローラ8の外周面の断面形状を、軸方向中央部が膨らんだ断面円弧状にする事により、図10(A)に示す様に、この内径側ローラ8を含むローラ6aを支持した支持軸5と、このローラ6aを構成する外径側ローラ9の外周面が当接する相手部材である、カムシャフト1の中心軸とが非平行になる、所謂ミスアライメントが発生した場合にも、上記ローラ6aを構成する内径側、外径側両ローラ8、9の周面の縁部と相手面とが極く狭い面積で当接する、所謂エッヂ当たりの発生を防止するとしている。 Thus, the cross-sectional shape of the outer peripheral surface of the inner diameter side roller 8, by which the circular-arc cross section bulging axial central portion, as shown in FIG. 10 (A), roller 6a including the inner diameter side roller 8 a support shaft 5 supporting the outer peripheral surface of the outer diameter side roller 9 constituting the roller 6a is mating member abutting, the central axis of the cam shaft 1 is non-parallel, if the so-called misalignment occurs also, and the inner diameter side constituting the roller 6a, and the edge portion of the peripheral surface of the outer diameter side between the rollers 8,9 and the mating surface contact with very small area, to prevent the occurrence of per-called edge.

【0008】 [0008]

【発明が解決しようとする課題】実開平4−32210 THE INVENTION Problems to be Solved] real-Open No. 4-32210
号公報、特開平4−15296号公報、実開昭62−2 JP, Hei 4-15296, JP-Utility Model 62-2
03911号公報、実開平3−108806号公報、特開昭59−183007号公報、実開昭60−1260 03911, JP-real-Open 3-108806, JP-Sho 59-183007, JP-Utility Model 60-1260
4〜5号公報、特開平8−74526号公報に記載された発明は、ローラと相手面との潤滑を良好にする技術、 4-5, JP invention described in JP-A-8-74526, a technique to improve the lubrication between the roller and the mating surface,
或は潤滑が不良の場合にも損傷防止を図る技術で、ミスアライメントが発生した場合の損傷防止を図れるものではない。 Or a technology that lubrication prevented from being damaged in the case of failure, do not attained the damage prevention when the misalignment occurs. 又、実公昭46−9606号公報に記載されている技術は、ローラの回転抵抗を小さくする為のもので、やはりミスアライメントが発生した場合の損傷防止を図れるものではない。 Further, the technique described in JP Utility Model 46-9606 is intended for reducing the rotational resistance of the roller does not attained the damage prevention when still misalignment occurs. 特開平8−296412号公報に記載された技術は、ミスアライメントが発生した場合にも、エッヂ当たりを防止できるが、代わりに、内径側ローラ8の外周面11と、外径側ローラ9の内周面12 The technique described in JP-A-8-296412, even when misalignment occurs, can be prevented per edge, instead, the outer peripheral surface 11 of the inner diameter side roller 8, of the outer diameter side roller 9 circumferential surface 12
との接触面積が狭くなり、接触部に加わる面圧が大きくなる。 Contact area between is narrowed, the surface pressure is increased applied to the contact portion.

【0009】即ち、上記内径側ローラ8の外周面11 [0009] That is, the outer peripheral surface 11 of the inner diameter side roller 8
が、断面円弧状の凸面である為、この外周面11と外径側ローラ9の内周面12とは、これら内径側、外径側両ローラ8、9の弾性変形を考慮しても、図9(B)及び図10(B)に斜線で示す様な、狭い面積でのみ当接する。 But since a cross-sectional arcuate convex, and the outer peripheral surface 11 and the inner circumferential surface 12 of the outer side roller 9, these inner diameter side, even considering the elastic deformation of the outer diameter side both rollers 8,9, Figure 9 (B) and the like shown by hatching FIG. 10 (B), the contacts only in a narrow area. そして、この斜線部分に於いて上記両周面11、1 Then, the both peripheral surfaces In this shaded area 11,1
2に、図9(C)及び図10(C)に示す様に大きな面圧が加わる。 2, applied a large contact pressure as shown in Fig. 9 (C) and FIG. 10 (C). 上記両周面11、12にこの様に大きな面圧が加わると、これら両周面11、12に、かじりや異常摩耗等の損傷を発生し易くなる為、好ましくない。 When a large surface pressure in this manner is applied to the both circumferential surfaces 11 and 12, these two circumferential surfaces 11 and 12, for easily generating a damage such as galling or abnormal wear, undesirable. 本発明は、この様な事情に鑑みて、ミスアライメントの発生時にエッヂ当たりを防止できる構造で、しかもローラの周面と相手面との当接部の面圧上昇を抑えられる構造を実現すべく発明したものである。 The present invention is, in view of such circumstances, a structure can prevent the contact edge in the event of misalignment, yet in order to realize a structure capable of suppressing the surface pressure increase in the contact portion between the peripheral surface and the mating surface of the roller it is obtained by the invention.

【0010】 [0010]

【課題を解決するための手段】本発明のローラ支持用軸受装置は、前述した従来のローラ支持用軸受装置と同様に、支持軸と、この支持軸の周囲に回転自在に支持された少なくとも1個のローラとから成り、このローラの外周面と他の部材の表面とを、当接状態等に係合させる状態で使用される。 Means for Solving the Problems] roller supporting bearing device of the present invention, like the conventional roller supporting bearing device described above, a support shaft, at least one rotatably supported around the support shaft consists of a number of rollers, the outer peripheral surface and the surface of the other member of the roller, is used in a state engaged with the abutment or the like. 特に、本発明のローラ支持用軸受装置に於いては、上記ローラの内外両周面のうちの少なくとも一方の周面の軸方向中央部に、このローラの中心軸と平行な円筒面部を設けると共に、この円筒面部を挟む軸方向両側部分に、それぞれがこの円筒面部から離れるに従って、この円筒面部を形成した周面が対向する相手面から離れる方向に僅かに傾斜した、1対の傾斜面部を設けている。 In particular, with the In the roller supporting bearing device of the present invention, the axially central portion of the at least one peripheral surface of the inner and outer peripheral surfaces of the roller, providing a central axis parallel to the cylindrical surface of the roller , axially opposite side portions sandwiching the cylindrical surface portion, according to each distance from the cylindrical surface portion, the formed peripheral surface of the cylindrical surface portion is slightly inclined in a direction away from the mating surface facing, provided inclined surface of the pair ing. 尚、本明細書で言う傾斜面部とは、後述する実施の形態からも明らかな様に、母線が直線である一般的なテーパ面だけでなく、母線が円弧状の曲面である先細面も含む。 Note that the inclined surface portion referred to herein, as is apparent from the embodiments described below, bus not only general tapered surface is straight, also includes tapered surface generatrix is ​​an arc-shaped curved surface .

【0011】 [0011]

【作用】上述の様に構成する本発明のローラ支持用軸受装置によれば、ミスアライメントの発生時にエッヂ当たりを防止し、しかもローラの周面と相手面との当接部の面圧上昇を抑える事ができる。 SUMMARY OF] According to the above roller supporting bearing device of the present invention constructed as to prevent the contact edge in the event of misalignment, yet the surface pressure increase in the contact portion between the peripheral surface and the mating surface of the roller it can be suppressed. 先ず、ローラの周面の軸方向中央部に設けた円筒面部の存在に基づき、この周面と相手面との当接面積を確保し、これら両面同士の当接部の面圧の上昇を抑えて、この当接部にかじりや異常摩耗等の損傷が発生するのを防止できる。 First, based on the presence of a cylindrical surface portion which is provided in the axially central portion of the peripheral surface of the roller, to ensure contact area between the circumferential surface and the mating surface, suppressing the increase of the surface pressure of the contact portion of both surfaces to each other Te, can prevent this the abutment to galling and damage of abnormal wear or the like occurs. 又、ミスアライメントの発生時には、1対の傾斜面部の存在に基づき、 Further, in the event of misalignment, based on the presence of the inclined surface portion of the pair,
ローラの中心軸と相手部材の中心軸とを不一致にしつつ、このローラの周面と相手面との当接状態を確保する。 While the central axis of the mating member of the roller in disagreement, to ensure contact between the circumferential surface and the mating surface of the roller. 上記円筒面部に対する上記傾斜面部の傾斜角度は僅かであるから、これら円筒面部と傾斜面部との境界部での面圧上昇は僅かであり、かじりや異常摩耗等の損傷には結び付きにくい。 Since the inclination angle of the inclined surface portion with respect to the cylindrical surface portion is small, the surface pressure increase at the boundary between these cylindrical surface portion inclined surface is slightly difficult ties for damage galling or abnormal abrasion.

【0012】 [0012]

【発明の実施の形態】図1〜2は、本発明の実施の形態の第1例を示している。 DETAILED DESCRIPTION OF THE INVENTION Figures 1-2 show a first example of an embodiment of the present invention. ロッカーアーム3の端部に設けた1対の支持壁部4、4の間に掛け渡した支持軸5の周囲にローラ6bを、回転自在に支承しており、このローラ6bの外周面を、カムシャフト1の中間部に固定したカム2の外周面に当接させている。 The rollers 6b around the supporting shaft 5 which spanned between the support wall portions 4 of the pair provided at the end of the rocker arm 3, has supported rotatably, the outer peripheral surface of the roller 6b, and it is brought into contact with the outer peripheral surface of the cam 2 fixed to an intermediate portion of the camshaft 1. 本例の場合にはこのローラ6bを、内径側ローラ8aと外径側ローラ9aとを組み合わせて成る。 In the case of this example the rollers 6b, comprising a combination of an inner diameter side roller 8a and the outer diameter side roller 9a.

【0013】このうちの内径側ローラ8aは、内周面1 [0013] internal diameter side roller 8a of this, the inner peripheral surface 1
0を円筒面とし、外周面11aの断面形状を山形としている。 0 is a cylindrical surface, and the sectional shape of the outer peripheral surface 11a Yamagata. 即ち、上記内径側ローラ8aの外周面11aの軸方向(図1〜2の左右方向)中央部に、この内径側ローラ8aの中心軸と平行な円筒面部13を設けている。 That is, the central portion (the left-right direction in FIGS. 1 and 2) the axial direction of the outer peripheral surface 11a of the inner diameter side roller 8a, are provided parallel to the center axis cylindrical surface portion 13 of the inner diameter side roller 8a.
又、上記外周面11aの残部で、この円筒面部13を挟む軸方向両側部分に、1対の傾斜面部14、14を設けている。 Also, in the remainder of the outer peripheral surface 11a, axially opposite side portions sandwiching the cylindrical surface portion 13 is provided with an inclined surface 14, 14 of the pair. これら各傾斜面部14、14は、クラウニング加工により形成するもので、それぞれが上記円筒面部1 Each of the inclined surface portions 14 and 14 is for forming a crowning, each said cylindrical surface 1
3から離れるに従って外径が小さくなる方向に僅かに傾斜した、円すい状凸面である。 Outer diameter with distance from the 3 is slightly inclined in the direction of smaller, a conical convex surface. 又、これら各傾斜面部1 Moreover, each of these inclined surface portion 1
4、14の大径側端部と上記円筒面部13の両端部との連続部には、超仕上加工やバレル加工等の後加工を施す事により、これら端部同士を断面円弧状の曲面により、 The continuous portion between the both end portions of the large diameter side end portion and the cylindrical surface portion 13 of 4,14, by subjecting a post-processing such as super finishing or barrel processing, the arcuate cross-section curved these end portions ,
滑らかに連続させている。 And smoothly made continuous. この様な内径側ローラ8a Such inner diameter side roller 8a
は、上記支持軸5の周囲に、回転自在に支持している。 Is around the support shaft 5 is rotatably supported.

【0014】又、上記外径側ローラ9aは、内周面12 [0014] Also, the outside diameter side roller 9a is an inner circumferential surface 12
を円筒面とし、外周面15を、上記内径側ローラ8aの外周面11aと同様に、断面山形としている。 It was a cylindrical surface, the outer peripheral surface 15, similarly to the outer peripheral surface 11a of the inner diameter side roller 8a, and a sectional chevron. 即ち、上記外径側ローラ9aの外周面15の軸方向中央部に、この外径側ローラ9aの中心軸と平行な円筒面部13aを設けると共に、この円筒面部13aを挟む軸方向両側部分に1対の傾斜面部14a、14aを、やはりクラウニング加工により設けている。 That is, the axially central portion of the outer peripheral surface 15 of the outer diameter side roller 9a, provided with a central axis parallel to the cylindrical surface portion 13a of the outer diameter side roller 9a, the axially opposite side portions sandwiching the cylindrical surface portion 13a 1 inclined surface portion 14a of the pair, the 14a, are also provided by the crowned. 又、これら各傾斜面部14 Moreover, each of these inclined surface portion 14
a、14aの大径側端部と上記円筒面部13aの両端部とも、断面円弧状の曲面により、滑らかに連続させている。 a, both end portions of the large diameter side end portion and the cylindrical surface 13a of 14a, the arcuate cross section curved face is smoothly made continuous. この様な外径側ローラ9aは、上記内径側ローラ8 Such outer diameter side roller 9a is the inner diameter side roller 8
aの周囲に、回転自在に支持している。 Around the a, it is rotatably supported.

【0015】上述の様な内径側ローラ8aと外径側ローラ9aとから成るローラ6bを組み込んで構成する、本例のローラ支持用軸受装置によれば、ミスアライメントの発生時にエッヂ当たりを防止し、しかも上記ローラ6 [0015] constituting incorporate roller 6b composed of such internal diameter side roller 8a described above and the outer diameter side roller 9a, according to the roller supporting bearing device of the present embodiment, to prevent contact edge in the event of misalignment , And the roller 6
bを構成する内径側ローラ8aの内外両周面10、11 Inner and outer peripheral surfaces of the inner diameter side roller 8a constituting the b 10, 11
a及び外径側ローラ9aの内外両周面12、15と相手面との当接部の面圧上昇を抑える事ができる。 It can be suppressed surface pressure increase in the contact portion between the inner and outer peripheral surfaces 12 and 15 and the mating surface of a and the outer diameter side roller 9a.

【0016】先ず、上記ミスアライメントが発生していない状態で考える。 [0016] First of all, think in a state in which the above-mentioned misalignment does not occur. 上記内径側ローラ8aの内周面10 The inner peripheral surface of the inner diameter side roller 8a 10
と支持軸5の外周面とは、この内径側ローラ8aの内周面10のほぼ全長に亙って均一に当接する為、これら両周面同士の当接面積は十分に広くなり、当接部の面圧は限られたものとなる。 And the outer peripheral surface of the support shaft 5, to uniformly contact over substantially the entire length of the inner peripheral surface 10 of the inner diameter side roller 8a, the contact area between the both peripheral surfaces becomes sufficiently large, abutment the surface pressure of the parts are made is limited. 又、上記内径側ローラ8aの外周面11aと上記外径側ローラ9aの内周面12との当接部、並びに、この外径側ローラ9aの外周面15と前記カム2の外周面とは、これら内径側、外径側各ローラ8 Further, contact portion between the inner circumferential surface 12 of the outer peripheral surface 11a and the outer diameter side roller 9a of the inner diameter side roller 8a, and a peripheral surface 15 and the outer peripheral surface of the cam 2 in the outer diameter side roller 9a is these inner diameter side, the outer diameter the rollers 8
a、9aの外周面の軸方向中央部に設けた円筒面部1 a, cylindrical surface portion 1 provided at the axially central portion of the outer peripheral surface of 9a
3、13aの存在に基づき、上記外径側ローラ9aの内周面12及びカム2の外周面との当接面積を確保する。 Based on the presence of 3,13A, ensuring the contact area between the inner peripheral surface 12 and the outer peripheral surface of the cam 2 in the outer diameter side roller 9a.
即ち、この様にミスアライメントが発生していない状態では、上記各面12、13同士の当接部は、図1(B) That is, in the state in which misalignment Thus has not occurred, the contact portion between the surfaces 12 and 13, and FIG. 1 (B)
に斜線で示す様に広くなる。 It becomes wider as shown by hatching in. そして、この斜線部分に於いて上記各面に、図1(C)に示す様な面圧が作用する。 Then, the respective surfaces In this shaded area, the surface pressure such as shown in FIG. 1 (C) is applied. これら図1(B)(C)から明らかな通り、本例の構造によれば、上記各面同士の当接部の面積を広くしてこれら各当接部の面圧の上昇を抑え、これら各当接部にかじりや異常摩耗等の損傷が発生するのを防止できる。 These Figure 1 (B) (C) from As apparent, according to the structure of this example, suppressing the increase of the surface pressure of the contact portions and wide area of ​​the contact portion between the surfaces, these damage or abnormal abrasion galling to each contact portion can be prevented.

【0017】又、ミスアライメントの発生時には、図2 [0017] In addition, in the event of a misalignment, as shown in FIG. 2
(A)に示す様に、上記1対ずつの傾斜面部14、14 As (A), the slope of the in pairs above surface portion 14, 14
aの存在に基づき、上記ローラ6bを構成する内径側、 Based on the presence of a, the inner diameter side constituting the roller 6b,
外径側両ローラ8a、9aの中心軸と他の部材であるカムシャフト1の中心軸とを不一致にしつつ、これら内径側、外径側両ローラ8a、9aの内外両周面と相手面との当接状態を確保する。 Outer diameter the rollers 8a, while the mismatch between the central axis of the camshaft 1 is a central axis and the other member 9a, these inner diameter side, the outer diameter the rollers 8a, the inner and outer peripheral surfaces of 9a and the mating surface and to ensure the contact state. この際、上記内径側、外径側両ローラ8a、9aは、僅かに弾性変形する。 At this time, the inner diameter side, the outer diameter the rollers 8a, 9a are slightly elastically deformed. 上記各円筒面部13、13aに対する上記各傾斜面部14、14a Each inclined surface portion 14,14a for each cylindrical surface 13,13a
の傾斜角度は僅かであるから、これら各円筒面部13、 Since the angle of inclination is slight, respective cylindrical surface portion 13,
13aと各傾斜面部14、14aとの境界部での面圧上昇は僅かである。 13a and surface pressure increases at the boundary between the inclined surface portion 14,14a is slight. 即ち、これら各円筒面部13、13a That is, each of these cylindrical surface portion 13,13a
及び傾斜面部14、14aと相手面とは、上記内径側、 And The inclined surface portion 14,14a and the mating surface, the inner diameter side,
外径側両ローラ8a、9aの弾性変形を考慮すれば、図2(B)に斜線で示す様に、前述の図9〜10に示した従来構造に比べて広い面積で当接する。 Outer diameter the rollers 8a, considering the elastic deformation of 9a, as shown by hatching in FIG. 2 (B), abuts a large area as compared with the conventional structure shown in FIGS. 9-10 above. そして、この斜線部分に於いて上記各円筒面部13、13a及び傾斜面部14、14aと相手面とに、図2(C)に示す様な面圧が加わる。 Then, each of the above cylindrical surface 13,13a and the inclined surface portion 14,14a and the mating surface In this shaded area, applied surface pressure, such as shown in FIG. 2 (C). この図2(C)から明らかな通り、これら各面同士の当接部に加わる面圧の最大値は低く、これら各当接部に、かじりや異常摩耗等の損傷を生じにくい。 As is apparent from this FIG. 2 (C), the maximum value of the surface pressure applied to the contact portion of these surfaces to each other is low, these respective contact portions hardly cause damage such as galling or abnormal wear.

【0018】尚、本発明を実施する場合に、支持軸5と内径側ローラ8aと外径側ローラ9aとの材質は、特に限定しない。 [0018] In the case of carrying out the present invention, the material of the support shaft 5 and the inner diameter side roller 8a and the outer diameter side roller 9a is not particularly limited. 但し、耐久性とコストとを勘案した場合には、上記支持軸5は鋼製とし、(特に内径側ローラ8a However, when considering the durability and cost, the support shaft 5 is made of steel, (particularly the inner diameter side roller 8a
の内周面10と対向する)中間部を焼き入れ硬化したものが好ましい。 The inner peripheral surface 10 and opposing) those cured quenching the intermediate portion is preferably of. 又、外径側ローラ9aも、焼き入れ硬化した鋼製とする事が望ましい。 Further, the outer diameter side roller 9a also, it is preferable that the steel was hardened quenching. これに対して、内径側ローラ8aは、焼き入れ硬化した鋼製でも良いが、自己潤滑性を有する銅又は銅合金も、好ましく使用できる。 In contrast, the inner diameter side roller 8a is may be made of steel hardened quenching, copper or copper alloy having the self-lubricating property can also be preferably used.
又、上記内径側ローラ8aと外径側ローラ9aとの一方又は双方に、潤滑性を向上させたり、耐摩耗性を向上させる為の表面処理を施す事も、耐久性向上の面から好ましい。 Further, in one or both of the above inner diameter side roller 8a and the outer diameter side roller 9a, or to improve lubricity, is subjected to surface treatment for improving the wear resistance, preferred from the viewpoint of durability.

【0019】又、上記各傾斜面部14、14aの傾斜角度は、使用条件に応じて決定するが、自動車用のタペットローラ軸受として使用する場合で、10度以下にする。 [0019] Also, the inclination angle of each inclined surface portion 14,14a is determined according to use conditions, in case of using as a tappet roller bearing for automobiles, to less than 10 degrees. 例えば、上記内径側、外径側各ローラ8a、9aの軸方向端面から1mmだけ軸方向中央部に寄った位置で、 For example, the inner diameter side, the outer diameter the rollers 8a, at a position closer to the axial center portion by 1mm from the axial end surface of 9a,
上記各傾斜面部14、14aの落ち量(円筒面部13、 Fallen amount of the respective inclined surface portion 14, 14a (cylindrical surface portion 13,
13aを延長したと仮定した場合の仮想円筒面と各傾斜面部14、14aとの直径方向に亙る距離)が1〜20 Over the virtual cylindrical surface the diameter direction between the inclined surface portion 14,14a assuming that extended the 13a distance) from 1 to 20
μm程度になる様に、上記傾斜角度を規制する。 As is about μm, to regulate the inclination angle. 又、上記各傾斜面部14、14aを、母線形状の曲率半径が5 Moreover, the respective inclined surface portion 14, 14a, the radius of curvature of the generating line shape 5
00〜10000mm程度で、上記円筒面部13、13a In order 00~10000Mm, the cylindrical surface portion 13,13a
の端部から滑らかに連続する曲面とする事もできる。 It can also be a curved surface smoothly continuous from the end. この場合も、上記落ち量を上記範囲に規制する。 Also in this case, to regulate the above-mentioned fall amount in the range described above. 又、上記内径側、外径側両ローラ8a、9aの全長に対する上記各円筒面部13、13aの割合は、40〜70%の範囲で設計的に定める。 Also, the inner diameter side, the outer diameter the rollers 8a, the ratio of the respective cylindrical surface 13,13a with respect to the total length of the 9a is designed to define the range of 40% to 70%.

【0020】次に、図3は、本発明の実施の形態の第2 Next, FIG. 3, a second embodiment of the present invention
例を示している。 It shows an example. 本例の場合には、ローラ6cを構成する内径側ローラ8bの内周面10aの軸方向中間部に円筒面部13bを形成し、この内周面10aの残部でこの円筒面部13bを挟む位置に1対の傾斜面部14b、1 In the case of this example, a cylindrical surface portion 13b is formed in the axially intermediate portion of the inner peripheral surface 10a of the inner diameter side roller 8b constituting the roller 6c, a position sandwiching the cylindrical surface portion 13b in the remainder of the inner peripheral surface 10a a pair of inclined surface portions 14b, 1
4bを形成している。 To form a 4b. 又、外径側ローラ9bは、外周面15に円筒面部13a及び傾斜面部14a、14aを形成するだけでなく、内周面12aにも円筒面部13c及び傾斜面部14c、14cを形成している。 Further, the outer diameter side roller 9b is an outer peripheral surface 15 to the cylindrical surface 13a and the inclined surface portion 14a, not only form the 14a, cylindrical surface portion 13c and the inclined surface portion 14c to the inner circumferential surface 12a, forming a 14c. これら各傾斜面部14a、14b、14cは、内周面10a、12 Each of the inclined surface portions 14a, 14b, 14c is the inner circumferential surface 10a, 12
aに形成する傾斜面部14b、14cを、それぞれ円筒面部13b、13cから離れるに従って内径が大きくなる方向に傾斜させ、外周面15に形成する傾斜面部14 Inclined surface portion 14b to be formed in a, the 14c, respectively cylindrical surface portion 13b, is inclined in a direction in which the inner diameter increases with distance from 13c, the inclined surface portion 14 formed on the outer peripheral surface 15
a、14aは、円筒面部13aから離れるに従って外径が小さくなる方向に傾斜させている。 a, 14a are tilted in a direction in which the outer diameter decreases with increasing distance from the cylindrical surface portion 13a. この様な傾斜面部14a、14b、14cのうち、内周面10a、12a Such inclined surface portion 14a, 14b, of 14c, the inner circumferential surface 10a, 12a
に形成する傾斜面部14b、14cは、だらし加工と呼ばれる塑性加工により形成できる。 Inclined surface portion 14b to be formed, 14c may be formed by plastic processing called sloppy work. この様な構造を有する本例の場合も、上述した第1例の場合と同様に、各面同士の当接部の面積を広くしてこれら各当接部の面圧の上昇を抑え、これら各当接部にかじりや異常摩耗等の損傷が発生するのを防止できる。 In the case of this example also having such a structure, as in the first example described above, suppressing the increase of the surface pressure of the contact portions and wide area of ​​the contact portion between the surfaces, these damage or abnormal abrasion galling to each contact portion can be prevented.

【0021】次に、図4は、本発明の実施の形態の第3 Next, FIG. 4, a third embodiment of the present invention
例を示している。 It shows an example. 本例の場合には、ローラ6dを構成する内径側ローラ8cに、内周面10aだけでなく外周面11aにも、傾斜面部14、14を形成している。 In the case of this example, the inner diameter side roller 8c constituting the roller 6d, to the outer peripheral surface 11a as well as the inner peripheral surface 10a, and forms an inclined surface portion 14, 14. その他の構成及び作用は、上述した第2例の場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。 Other structures and operations are the same as in the case of the second example described above, the equivalent parts are denoted by the same reference numerals, and overlapping description is omitted.

【0022】次に、図5は、本発明の実施の形態の第4 Next, FIG. 5, a fourth embodiment of the present invention
例を示している。 It shows an example. 本例の場合には、ローラ6eを構成する内径側ローラ8cとして上述した第3例と同様のものを、外径側ローラ9aとして前述した第1例と同様のものを、それぞれ使用している。 In the case of this example, those similar to the third example described above as the inner diameter side roller 8c constituting the roller 6e, those similar to the first example described above as the outer diameter side roller 9a, using respectively . 更に、本例の場合には、 Further, in the case of this example,
上記内径側ローラ8cと外径側ローラ9aとの間に、中間ローラ16を設けて、上記ローラ6eを3相構造としている。 Between the inner diameter side roller 8c and the outer diameter side roller 9a, an intermediate roller 16 is provided, and a three-phase structure the roller 6e. この中間ローラ16は、上記外径側ローラ9a The intermediate roller 16, the outside diameter side roller 9a
と同様に、内周面17を円筒面とし、外周面18の軸方向中間部に円筒面部13dを、軸方向両端部に傾斜面部14d、14dを、それぞれ設けている。 Similar to the inner peripheral surface 17 and a cylindrical surface, a cylindrical surface portion 13d in the axial direction intermediate portion of the outer peripheral surface 18, the inclined surface portion 14d in the axial direction both end portions, the 14d, are provided, respectively. この様な本例の場合には、上記ローラ6eの内部に設ける滑り面の数を増やし、これら各滑り面毎の滑り量を少なくし、潤滑条件を改良して、摩耗の低減を図れる。 Such in the case of this example, increasing the number of sliding surfaces provided inside the roller 6e, to reduce the slip amount of each respective sliding surfaces, to improve the lubrication conditions, thereby reducing wear. その他の構成及び作用は、上述した各例の場合と同様である。 Other configurations and operations are the same as in the case of the example described above.

【0023】次に、図6は、本発明の実施の形態の第5 Next, FIG. 6, the fifth embodiment of the present invention
例を示している。 It shows an example. 本例は、単体のローラ6fを使用している。 This example uses a single roller 6f. そして、このローラ6fの内周面19の軸方向中間部に円筒面部13eを、軸方向両端部に傾斜面部14 Then, a cylindrical surface portion 13e in the axial direction intermediate portion of the inner peripheral surface 19 of the roller 6f, axially inclined end portions face 14
e、14eを、それぞれ設けている。 e, the 14e, are provided, respectively. 又、外周面20の軸方向中間部に円筒面部13fを、軸方向両端部に傾斜面部14f、14fを、それぞれ設けている。 Further, the cylindrical surface portion 13f in the axial direction intermediate portion of the outer peripheral surface 20, the inclined surface portion 14f in the axial direction both end portions, a 14f, are provided, respectively. この様な本例の場合も、上述した各例の場合と同様に、対向する各面同士の当接部の面積を広くしてこれら各当接部の面圧の上昇を抑え、これら各当接部にかじりや異常摩耗等の損傷が発生するのを防止できる。 Also case of this example, as in the case of the example described above, suppressing the increase of the surface pressure of the contact portions and wide area of ​​the abutment surfaces facing each other, each of these equivalents damage such as galling or abnormal wear contact portion can be prevented.

【0024】 [0024]

【発明の効果】本発明のローラ支持用軸受装置は、以上に述べた通り構成され作用するので、特に組み付け精度を高くする事なく、安価に製作でき、しかも優れた耐久性を有するカムフォロア装置の実現に寄与できる。 Roller supporting bearing device of the present invention exhibits, because they act configured as described above, without increasing the particular assembly accuracy, inexpensive to manufacture, yet the cam follower device having excellent durability It can contribute to the realization.

【図面の簡単な説明】 BRIEF DESCRIPTION OF THE DRAWINGS

【図1】本発明の実施の形態の第1例を、ミスアライメントが発生していない状態で示しており、(A)は断面図、(B)は当接面積を表す為、当接部を(A)の下方から見た図、(C)は当接部の面圧分布を示す線図。 The first example of an embodiment of the invention, FIG shows a state in which misalignment is not generated, (A) is a sectional view, (B) is to represent the contact area, the contact portion FIG viewed from below of (a), (C) is diagram showing a surface pressure distribution of the contact portion.

【図2】本発明の実施の形態の第1例を、ミスアライメントが発生した状態で示しており、(A)は断面図、 The first example of an embodiment of the present invention; FIG shows a state in which misalignment has occurred, (A) is a sectional view,
(B)は当接面積を表す為、当接部を(A)の下方から見た図、(C)は当接部の面圧分布を示す線図。 (B) is to represent the contact area, view of the abutment from below of (A), (C) is diagram showing a surface pressure distribution of the contact portion.

【図3】本発明の実施の形態の第2例を示す断面図。 Sectional view showing a second example of embodiment of the present invention; FIG.

【図4】同第3例を示す断面図。 4 is a cross-sectional view showing the same third example.

【図5】同第4例を示す断面図。 5 is a sectional view showing the same fourth example.

【図6】同第5例を示す断面図。 6 is a sectional view showing the same fifth example.

【図7】タペットローラ軸受の部分切断平面図。 Figure 7 is a partial cut plan view of the tappet roller bearing.

【図8】図7のX−X断面図。 [8] X-X cross-sectional view of FIG. 7.

【図9】従来構造の1例を、ミスアライメントが発生していない状態で示しており、(A)は断面図、(B)は当接面積を表す為、当接部を(A)の下方から見た図、 [9] An example of the conventional structure, is shown in a state where the misalignment is not generated, the (A) is a sectional view, (B) is to represent the contact area, the contact portion (A) view from below,
(C)は当接部の面圧分布を示す線図。 (C) is diagram showing a surface pressure distribution of the contact portion.

【図10】従来構造の1例を、ミスアライメントが発生した状態で示しており、(A)は断面図、(B)は当接面積を表す為、当接部を(A)の下方から見た図、 [10] An example of the conventional structure, is shown in a state in which misalignment has occurred, from the lower (A) is a sectional view, (B) is to represent the contact area, the contact portion (A) I saw the figure,
(C)は当接部の面圧分布を示す線図。 (C) is diagram showing a surface pressure distribution of the contact portion.

【符号の説明】 DESCRIPTION OF SYMBOLS

1 カムシャフト 2 カム 3 ロッカーアーム 4 支持壁部 5 支持軸 6、6a、6b、6c、6d、6e、6f ローラ 7 通孔 8、8a、8b、8c 内径側ローラ 9、9a、9b 外径側ローラ 10、10a 内周面 11、11a 外周面 12、12a 内周面 13、13a、13b、13c、13d、13e、13 1 camshaft 2 cam 3 rocker arm 4 supporting wall 5 support shaft 6,6a, 6b, 6c, 6d, 6e, 6f roller 7 holes 8, 8a, 8b, 8c inner diameter side roller 9, 9a, 9b outer diameter side rollers 10,10a inner peripheral surface 11,11a outer peripheral surface 12,12a inner peripheral surface 13,13a, 13b, 13c, 13d, 13e, 13
f 円筒面部 14、14a、14b、14c、14d、14e、14 f cylindrical surface portion 14,14a, 14b, 14c, 14d, 14e, 14
f 傾斜面部 15 外周面 16 中間ローラ 17 内周面 18 外周面 19 内周面 20 外周面 Within f inclined surface portion 15 outer circumferential surface 16 within the intermediate roller 17 peripheral surface 18 outer peripheral surface 19 peripheral surface 20 outer peripheral surface

Claims (1)

    【特許請求の範囲】 [The claims]
  1. 【請求項1】 支持軸と、この支持軸の周囲に回転自在に支持された少なくとも1個のローラとから成り、このローラの外周面と他の部材の表面とを係合させる状態で使用されるローラ支持用軸受装置に於いて、上記ローラの内外両周面のうちの少なくとも一方の周面の軸方向中央部に、このローラの中心軸と平行な円筒面部を設けると共に、この円筒面部を挟む軸方向両側部分に、それぞれがこの円筒面部から離れるに従って、この円筒面部を形成した周面が対向する相手面から離れる方向に僅かに傾斜した、1対の傾斜面部を設けた事を特徴とするローラ支持用軸受装置。 And 1. A support shaft consists of at least one roller rotatably supported around the support shaft, is used in a state to engage the outer peripheral surface and the surface of the other member of the roller in that roller bearing apparatus for supporting, in the axial center portion of at least one peripheral surface of the inner and outer peripheral surfaces of the roller, provided with a central axis parallel to the cylindrical surface of the roller, the cylindrical surface portion axially opposite side portions sandwiching, according to the respective leaves from the cylindrical surface portion, the peripheral surface formed with the cylindrical surface portion is slightly inclined in a direction away from the mating surface facing, and characterized in that a slope portion of a pair roller bearing apparatus for supporting to.
JP04659198A 1998-02-27 1998-02-27 Roller support bearing device Expired - Lifetime JP3815027B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP04659198A JP3815027B2 (en) 1998-02-27 1998-02-27 Roller support bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP04659198A JP3815027B2 (en) 1998-02-27 1998-02-27 Roller support bearing device

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JPH11247845A true JPH11247845A (en) 1999-09-14
JP3815027B2 JP3815027B2 (en) 2006-08-30

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002241915A (en) * 2001-02-20 2002-08-28 Hitachi Metals Ltd Bearing unit in molten metal bath
JP2007333025A (en) * 2006-06-13 2007-12-27 Nsk Ltd Manufacturing method of rolling/sliding component
JP2008008182A (en) * 2006-06-28 2008-01-17 Ntn Corp Tappet roller bearing structure
JP2008128310A (en) * 2006-06-30 2008-06-05 Shangyin Sci & Technol Co Ltd Linear guideway structure equipped with synchronous operating ball piece
JP2009092061A (en) * 2007-09-19 2009-04-30 Toyota Central R&D Labs Inc Slide member and roller rocker arm type valve gear
JP2009250078A (en) * 2008-04-03 2009-10-29 Ozak Seiko Co Ltd Fuel injection pump device
JP2013043509A (en) * 2011-08-23 2013-03-04 Jtekt Corp Position adjustable steering device
WO2013108433A1 (en) * 2012-01-19 2013-07-25 日本精工株式会社 Cam follower device
JP2014019385A (en) * 2012-07-23 2014-02-03 Heisei Jidosha:Kk Movable bumper
EP2907982A1 (en) * 2014-02-14 2015-08-19 Caterpillar Energy Solutions GmbH Cam follower for an internal combustion engine

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002241915A (en) * 2001-02-20 2002-08-28 Hitachi Metals Ltd Bearing unit in molten metal bath
JP4725759B2 (en) * 2001-02-20 2011-07-13 日立金属株式会社 Bearing device in molten metal bath
JP2007333025A (en) * 2006-06-13 2007-12-27 Nsk Ltd Manufacturing method of rolling/sliding component
JP4572875B2 (en) * 2006-06-13 2010-11-04 日本精工株式会社 Manufacturing method of rolling sliding parts
JP2008008182A (en) * 2006-06-28 2008-01-17 Ntn Corp Tappet roller bearing structure
JP2008128310A (en) * 2006-06-30 2008-06-05 Shangyin Sci & Technol Co Ltd Linear guideway structure equipped with synchronous operating ball piece
JP2009092061A (en) * 2007-09-19 2009-04-30 Toyota Central R&D Labs Inc Slide member and roller rocker arm type valve gear
JP2009250078A (en) * 2008-04-03 2009-10-29 Ozak Seiko Co Ltd Fuel injection pump device
JP2013043509A (en) * 2011-08-23 2013-03-04 Jtekt Corp Position adjustable steering device
WO2013108433A1 (en) * 2012-01-19 2013-07-25 日本精工株式会社 Cam follower device
CN103635663A (en) * 2012-01-19 2014-03-12 日本精工株式会社 Cam follower device
JP2014019385A (en) * 2012-07-23 2014-02-03 Heisei Jidosha:Kk Movable bumper
EP2907982A1 (en) * 2014-02-14 2015-08-19 Caterpillar Energy Solutions GmbH Cam follower for an internal combustion engine

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