JP2590701Y2 - Cam follower for engine valve train - Google Patents
Cam follower for engine valve trainInfo
- Publication number
- JP2590701Y2 JP2590701Y2 JP1990016174U JP1617490U JP2590701Y2 JP 2590701 Y2 JP2590701 Y2 JP 2590701Y2 JP 1990016174 U JP1990016174 U JP 1990016174U JP 1617490 U JP1617490 U JP 1617490U JP 2590701 Y2 JP2590701 Y2 JP 2590701Y2
- Authority
- JP
- Japan
- Prior art keywords
- roller
- shaft
- pair
- diameter surface
- engine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Valve-Gear Or Valve Arrangements (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） この考案に係るエンジンの動弁機構用カムフォロア装
置は、自動車の走行用等として使用されるエンジンの動
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。
特に、本考案は、この様な動弁機構中のローラの内径面
（内周面）と軸の外径面（外周面）との間に十分な潤滑
油が保持される様にして、上述の様なカムフォロア装置
の耐久性向上を図るものである。[Detailed description of the invention] (Industrial application field) The cam follower device for an engine valve operating mechanism according to the present invention is incorporated into a valve operating mechanism of an engine used for traveling of an automobile and the like, and a valve operating mechanism portion is provided. To reduce the fuel consumption rate during engine operation.
In particular, the present invention is designed to maintain sufficient lubricating oil between the inner diameter surface (inner peripheral surface) of the roller and the outer diameter surface (outer peripheral surface) of the shaft in such a valve operating mechanism. It is intended to improve the durability of the cam follower device as described above.
（従来の技術） 自動車の走行用等として使用されるエンジンには、各
種の構造のものがあるが、往復ピストン型エンジンの場
合は、一部の２サイクルエンジンを除き、総てクランク
シャフトの回転と同期して開閉する吸気弁及び排気弁を
設けている。これら吸気弁及び排気弁を駆動する為の動
弁機構としては各種の構造のものが存在するが、その１
例として、例えば第10図に示したSOHC型のものでは、ク
ランクシャフト１の1/2の速度で回転する（４サイクル
エンジンの場合）１本のカムシャフト２により、ロッカ
ーアーム３、３を介して吸気弁４及び排気弁５を往復駆
動する。クランクシャフト１と同期して回転するカムシ
ャフト２に固設したカム６、６は、ロッカーアーム３、
３の端部と摺接しつつ吸気弁４及び排気弁５を往復駆動
する。(Prior Art) There are various types of engines used for driving automobiles and the like. In the case of a reciprocating piston type engine, except for a part of a two-cycle engine, all rotations of a crankshaft are performed. An intake valve and an exhaust valve that open and close in synchronization with the intake valve are provided. There are various types of valve operating mechanisms for driving these intake valves and exhaust valves.
As an example, in the case of the SOHC type shown in FIG. 10, for example, a single camshaft 2 that rotates at half the speed of the crankshaft 1 (in the case of a four-cycle engine) through the rocker arms 3, 3 To drive the intake valve 4 and the exhaust valve 5 back and forth. The cams 6, 6 fixed to the camshaft 2 rotating in synchronization with the crankshaft 1 are rocker arms 3,
The intake valve 4 and the exhaust valve 5 are reciprocally driven while slidingly contacting the end of the valve 3.
ところで、近年、エンジン運転時に於けるカム６、６
の周面とロッカーアーム３、３等の相手側部材の対向部
分との摩擦力を低減し、エンジン運転時に於ける燃料消
費率の低減を図る為、上記対向部分に、カム６、６の回
転に伴なって回転するカムフォロア装置を設ける事が行
なわれる様になった。By the way, in recent years, the cam 6, 6
In order to reduce the frictional force between the peripheral surface of the shaft and the opposing parts of the opposing members such as the rocker arms 3 and 3 and to reduce the fuel consumption rate during engine operation, the cams 6 and 6 rotate on the opposing parts. With this, a cam follower device that rotates is provided.
即ち、第11〜12図に示す様に、カム６と対向するロッ
カーアーム３の端部に互いに間隔を開けて設けた１対の
支持壁部７、７に、軸８の両端部を支持固定し、この軸
８の周囲に、ころ９、９を介して短円筒状のローラ10を
設けている。そして、このローラ10の外周面とカム６の
外周面とを互いに当接させて、カム６の回転に伴ないロ
ーラ10が、軸８を中心として回転する様にしている。こ
の様なローラ10を設け、カム６とこれに対向する部材と
の間の摩擦を、滑り摩擦から転がり摩擦に変える事によ
り、燃料消費率の向上を図れる。That is, as shown in FIGS. 11 and 12, both ends of the shaft 8 are supported and fixed to a pair of support walls 7 provided at an end of the rocker arm 3 facing the cam 6 at intervals. A short cylindrical roller 10 is provided around the shaft 8 via rollers 9 and 9. The outer peripheral surface of the roller 10 and the outer peripheral surface of the cam 6 are brought into contact with each other so that the roller 10 rotates around the shaft 8 with the rotation of the cam 6. By providing such a roller 10 and changing the friction between the cam 6 and the member opposed thereto from the sliding friction to the rolling friction, the fuel consumption rate can be improved.
又、近年に於けるエンジンの高回転化に対応すべく、
カムフォロア部分の軽量化を図る為、例えば実開昭62−
203911号公報に開示されている様に、ロッカーアーム３
をアルミニウム合金により、ローラ10を比重の小さな
（軽い）セラミックにより、それぞれ造ると共に、ころ
９、９を省略し、上記セラミック製のローラ10を鋼製で
中空の軸８の周囲に直接、回転自在に支承する事が考え
られている。Also, in order to respond to the recent increase in engine speed,
In order to reduce the weight of the cam follower, for example,
As disclosed in JP 203911, rocker arm 3
The roller 10 is made of an aluminum alloy, the roller 10 is made of a ceramic having a small specific gravity (light), and the rollers 9 and 9 are omitted. The roller 10 made of ceramic is rotatable directly around a hollow shaft 8 made of steel. It is considered to be supported.
（考案が解決しようとする課題） ところが、単にセラミック製のローラ10を、鋼製の軸
８の周囲に回転自在に支承した場合、上記ローラ10の内
径面12と接触する軸８の外径面13の摩耗が進んでしま
う。この様な摩耗を防止する為、特開平１−153863号公
報には、軸８の外径面13、或はローラ10の内径面12に、
ヘリングボーン状の動圧溝を形成し、ローラ10の回転に
伴なって、上記外径面13と内径面12との間に油膜が形成
される様に構成する事により、上記両面12、13間の潤滑
を行なう技術が開示されている。(Problems to be Solved by the Invention) However, when the roller 10 made of ceramic is simply rotatably supported around the shaft 8 made of steel, the outer surface of the shaft 8 in contact with the inner surface 12 of the roller 10 Wear of 13 advances. In order to prevent such abrasion, Japanese Patent Application Laid-Open No. Hei 1-153863 discloses that the outer diameter surface 13 of the shaft 8 or the inner diameter surface 12 of the roller 10 is
By forming a herringbone-shaped dynamic pressure groove and forming an oil film between the outer diameter surface 13 and the inner diameter surface 12 with the rotation of the roller 10, the two surfaces 12, 13 are formed. A technique for performing lubrication between the two is disclosed.
ところが、軸８の外径面13やローラ10の内径面12は比
較的小径で周速が遅い為、エンジン回転数等の条件によ
っては、上記両面12、13間に十分な油膜が形成されず、
軸８の外径面13が摩耗する可能性を無視する事が出来な
い。この為、ロッカーアーム３と軸８との内側に潤滑油
の供給路を設け、この供給路を通じて、軸８の外径面13
とローラ10の内径面12との間に潤滑油を送り込む事も考
えられているが、供給路の加工が面倒で、製作費が嵩む
事が避けられない。However, since the outer diameter surface 13 of the shaft 8 and the inner diameter surface 12 of the roller 10 have a relatively small diameter and a low peripheral speed, a sufficient oil film is not formed between the two surfaces 12, 13 depending on conditions such as the engine speed. ,
The possibility that the outer diameter surface 13 of the shaft 8 is worn cannot be ignored. For this reason, a lubricating oil supply passage is provided inside the rocker arm 3 and the shaft 8, and the outer diameter surface 13 of the shaft 8 is passed through the supply passage.
It is considered that lubricating oil is fed between the roller and the inner diameter surface 12 of the roller 10, but it is unavoidable that the processing of the supply path is troublesome and the production cost increases.
本考案のエンジンの動弁機構用カムフォロア装置は、
特に面倒な加工を施す事なく、ローラの内径面と軸の外
径面との間に十分な量の潤滑油を保持出来る様にする事
により、軸の異常摩耗を防止するものである。The cam follower device for the valve train of the engine of the present invention is:
In particular, it is possible to maintain a sufficient amount of lubricating oil between the inner diameter surface of the roller and the outer diameter surface of the shaft without performing troublesome processing, thereby preventing abnormal wear of the shaft.
（課題を解決する為の手段） 本考案のエンジンの動弁機構用カムフォロア装置は何
れも、エンジンのクランクシャフトと同期して回転する
カムシャフトに固定されたカムと、このカムに対向して
設けられ、このカムの動きを受ける部材に間隔を開けて
形成した１対の支持壁部と、両端の未焼き入れ部分を上
記１対の支持壁部に形成した通孔の内径面に向けてかし
める事により、この１対の支持壁部の間に掛け渡す状態
で固定された鋼製の軸と、この軸の周囲に回転自在に支
承されたセラミック製のローラとから構成している。(Means for Solving the Problems) Each of the cam followers for the valve train of the engine of the present invention is provided with a cam fixed to a camshaft that rotates in synchronization with the crankshaft of the engine and a cam facing the cam. A pair of support walls formed at intervals on the member that receives the movement of the cam, and unhardened portions at both ends are directed toward the inner diameter surface of the through hole formed in the pair of support walls. By tightening, it comprises a steel shaft fixed in a state of being bridged between the pair of support walls, and a ceramic roller rotatably supported around the shaft.
特に、本考案のうち、請求項１に記載したエンジンの
動弁機構用カムフォロア装置に於いては、上記ローラの
内径面を表面粗さが0.2μmRa以下の平滑面としている。
又、上記軸の外径面で上記ローラの内径面と対向する部
分を焼き入れ硬化すると共に、少なくともこの部分にバ
レル加工により、表面粗さが0.08μmRa〜0.3μmRaの微
細な凹凸を形成している。そして、この構成により、上
記軸の外径面とローラの内径面との間の保油性能を向上
させている。In particular, according to the present invention, in the cam follower device for an engine valve operating mechanism according to the first aspect, the inner diameter surface of the roller is a smooth surface having a surface roughness of 0.2 μmRa or less.
Also, while quenching and hardening the portion of the outer diameter surface of the shaft facing the inner diameter surface of the roller, barrel forming at least this portion to form fine irregularities having a surface roughness of 0.08 μmRa to 0.3 μmRa. I have. With this configuration, the oil retaining performance between the outer diameter surface of the shaft and the inner diameter surface of the roller is improved.
また、請求項２に記載したエンジンの動弁機構用カム
フォロア装置に於いては、上記ローラの内径面の表面粗
さが0.05〜0.8μmRaの微細な凹凸を形成し、軸の外径面
で上記ローラの内径面と対向する部分を、表面粗さが0.
2μmRa以下の平滑面としている。Further, in the cam follower device for the valve operating mechanism of the engine according to claim 2, the surface roughness of the inner diameter surface of the roller is formed as fine irregularities of 0.05 to 0.8 μmRa, The part facing the inner diameter surface of the roller has a surface roughness of 0.
It has a smooth surface of 2 μmRa or less.
更に、請求項３に記載したエンジンの動弁機構用カム
フォロア装置に於いては、軸の外径面並びにローラの内
径面に、表面粗さが0.05〜0.8μmRaの微細な凹凸を形成
している。Further, in the cam follower device for an engine valve operating mechanism according to the third aspect, fine irregularities having a surface roughness of 0.05 to 0.8 μmRa are formed on the outer diameter surface of the shaft and the inner diameter surface of the roller. .
（作用） 上述の様に構成する本考案のエンジンの動弁機構用カ
ムフォロア装置は、ローラの内径面と軸の外径面との一
方又は双方に、表面粗さが0.05〜0.8μmRaの微細な凹凸
を形成している。この様な、表面粗さが0.05〜0.8μmRa
の微細な凹凸は、潤滑油の保持性能が優れている為、上
記内径面と外径面との間の潤滑を良好にして、軸の外径
面の異常摩耗を防止できる。(Effect) The cam follower device for an engine valve operating mechanism of the present invention configured as described above has a fine surface roughness of 0.05 to 0.8 μmRa on one or both of the inner surface of the roller and the outer surface of the shaft. Irregularities are formed. Such surface roughness is 0.05 ~ 0.8μmRa
Since the fine irregularities have excellent lubricating oil holding performance, lubrication between the inner diameter surface and the outer diameter surface can be improved, and abnormal wear of the outer diameter surface of the shaft can be prevented.
（実施例） 第１〜３図は、本考案の第一実施例を示している。本
考案のエンジンの動弁機構用カムフォロア装置は、前述
した従来のカムフォロア装置と同様に、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２に固定
された金属製のカム６に対向して設けられ、このカム６
の動きを受けるロッカーアーム３の端部に、１対の支持
壁部７、７を、互いに間隔を開けて形成している。そし
て、この１対の支持壁部７、７の間に、鋼製で中空の軸
８を、掛け渡す様に固定している。この軸８の両端は焼
き入れする事なく、生のままとしており、軸８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
７、７に形成した通孔11、11の内径面に向けてかしめ付
ける。(Embodiment) Figs. 1 to 3 show a first embodiment of the present invention. The cam follower device for the valve operating mechanism of the engine of the present invention is provided opposite to the metal cam 6 fixed to the camshaft 2 which rotates in synchronization with the crankshaft of the engine, similarly to the above-described conventional cam follower device. This cam 6
A pair of support walls 7, 7 are formed at an end of the rocker arm 3 which receives the above movement at intervals. A hollow shaft 8 made of steel is fixed between the pair of support walls 7 and 7 so as to bridge. Both ends of the shaft 8 are not quenched and are left raw. When the shaft 8 is fixed, the unquenched portion is formed by the through holes 11 formed in the pair of support walls 7 and 7. And crimped toward the inner diameter surface of 11.
上述の様にして、１対の支持壁部７、７の間に掛け渡
す状態で固定された鋼製の軸８の周囲にはセラミック製
ローラ10を、回転自在に支承しており、このローラ10の
外径面を、上記カム６の外周面に当接させている。As described above, a ceramic roller 10 is rotatably supported around a steel shaft 8 fixed in a state of being bridged between the pair of support wall portions 7 and 7. The outer diameter surface of the cam 10 contacts the outer peripheral surface of the cam 6.
更に、本考案のエンジンの動弁機構用カムフォロア装
置に於いては、上記ローラ10の内径面12に、ホーニング
加工等、適当な表面加工を施す事により、上記内径面12
を、表面粗さが0.2μmRa以下の平滑面としている。Further, in the cam follower device for the valve operating mechanism of the engine according to the present invention, the inner diameter surface 12 of the roller 10 is subjected to an appropriate surface processing such as honing, thereby obtaining the inner diameter surface 12.
Is a smooth surface having a surface roughness of 0.2 μmRa or less.
又、上記１対の支持壁部７、７に固定された軸８の外
径面13の中間部で、上記ローラ10の内径面12と対向する
部分は、焼き入れ硬化している。これと共に、少なくと
もこの焼き入れ硬化部分に、バレル加工（タンブラ加工
を含む。）により、表面粗さが0.08μmRa〜0.3μmRaの
微細な凹凸を形成している。尚、軸８の外径面13の表面
粗さが上記所望値となる様に、バレル加工に使用するメ
ディア並びに加工速度、加工時間を適宣選択する。A portion of the shaft 8 fixed to the pair of support walls 7 and 7 at an intermediate portion of the outer diameter surface 13 of the shaft 8 and facing the inner diameter surface 12 of the roller 10 is hardened and hardened. At the same time, fine irregularities having a surface roughness of 0.08 μmRa to 0.3 μmRa are formed by barrel processing (including tumbling) at least in the hardened and hardened portion. The media used for barrel processing, the processing speed, and the processing time are appropriately selected so that the surface roughness of the outer diameter surface 13 of the shaft 8 has the desired value.
上述の様に構成する本考案のエンジンの動弁機構用カ
ムフォロア装置により、ロッカーアーム３とカム６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
消費率の向上を図る際の作用自体は、前述した従来のカ
ムフォロア装置と同様である。The cam follower for the valve train of the engine of the present invention configured as described above reduces the frictional force acting between the rocker arm 3 and the cam 6 and improves the fuel consumption rate during engine operation. The operation itself is the same as that of the above-described conventional cam follower device.
特に、本考案のエンジンの動弁機構用カムフォロア装
置の場合は、軸８の外径面13に微細な凹凸を形成してい
る為、上記外径面13とローラ10の内径面12との間の潤滑
油の保持性能が優れている。この結果、上記内径面12と
外径面13との間の潤滑が良好に行なわれ、上記外径面13
の一部で、内径面12と対向する部分が焼き入れ硬化され
て耐摩耗性が向上している事と相まって、ローラ10の回
転に伴なう軸８の外径面13の異常摩耗を防止できる。In particular, in the case of the cam follower device for the valve operating mechanism of the engine of the present invention, since fine irregularities are formed on the outer diameter surface 13 of the shaft 8, the gap between the outer diameter surface 13 and the inner diameter surface 12 of the roller 10 is formed. Has excellent lubricating oil retention performance. As a result, the lubrication between the inner diameter surface 12 and the outer diameter surface 13 is favorably performed, and the outer diameter surface 13
A part of the outer surface 13 of the shaft 8 caused by the rotation of the roller 10 is prevented from being abnormally worn, in combination with the fact that the portion facing the inner surface 12 is quenched and hardened to improve wear resistance. it can.
即ち、軸８の外径面13に、上述の様な条件を満たす微
細な凹凸を形成した場合、スライスレベルＲと負荷比Tp
との関係が、第４図に曲線ａ〜ｄに示す様になるのに対
し、従来から使用されていた軸８の外径面の場合、両者
Ｒ、Tpの関係が、同図に曲線ｅ〜ｇに示す様になる。That is, when fine irregularities satisfying the above conditions are formed on the outer diameter surface 13 of the shaft 8, the slice level R and the load ratio T p
Curve is to become as shown by the curve a~d in Figure 4, when the outer diameter surface of the shaft 8 which has been conventionally used, both R, the relationship of T p, FIG relationship between e to g.
尚、上記スライスレベルＲとは、表面の凹凸を表わす
曲線を架空の直線で切断する場合に、どの部分で切断す
るかを表わすもので、第５図に鎖線イで示す様に、最も
高い山の頂部に接する直線のスライスレベルを０％、同
図に鎖線ロで示す様に、最も深い谷の底部に接する直線
のスライスレベルを100％とし、両直線の間を100等分し
て％で表わした。Note that the slice level R indicates a portion to be cut when a curve representing surface irregularities is cut by an imaginary straight line, and as shown by a chain line a in FIG. The slice level of the straight line in contact with the top of the straight line is 0%, and the slice level of the straight line in contact with the bottom of the deepest valley is 100%. Expressed.
又、上記負荷比Tpは、或る架空の直線で表面の凹凸を
切断した場合に、この直線で切断される断面部分の長さ
（上記架空の直線迄表面が摩耗した場合に、負荷を受け
られる部分の長さ。）の割合を表わしたもので、例え
ば、第５図に示す様に、長さＥの範囲で評価を行ない、
長さａ、ｂ、ｃ、ｄ、ｅの５箇所で凹凸面の山が切断さ
れた場合、負荷比Tpは、次式で表される。Further, the load ratio T p is the length of a cross section cut by a certain imaginary straight line when the surface irregularities are cut (when the surface wears up to the imaginary straight line, the load is reduced). The length of the part that can be received.). For example, as shown in FIG.
Length a, b, if c, d, mountain uneven surface at five locations e is disconnected, the load ratio T p is expressed by the following equation.
Tp＝（ａ＋ｂ＋ｃ＋ｄ＋ｅ）/E この様なスライスレベルＲと負荷比Tpとを、潤滑の面
から見た場合、スライスレベルＲが小さい（０％に近
い）うちから、負荷比Tpが大きい事が好ましい。即ち、
スライスレベルＲが小さいうちから負荷比Tpが大きくな
るのは、表面に幅が狭く、深い凹部が存在する事を意味
し、この凹部が潤滑油溜として寄与する為、良好な潤滑
性能を得る事が出来る。And T p = (a + b + c + d + e) / E load ratio T p and such slice level R, when viewed from the surface of the lubricant, the slice level R is small (close to 0%) inner shell, the load ratio T p is greater Things are preferred. That is,
Slice load ratio T p of increase among level R is small, the narrower the surface, means that the deep recess is present, this recess to serve as a lubricating oil reservoir, obtain favorable lubricating performance I can do things.
この点を考慮しつつ、第４図を見た場合、本考案のカ
ムフォロア装置が、従来品に比べて、良好な潤滑性能を
発揮する事が解る。In view of FIG. 4 in consideration of this point, it can be seen that the cam follower device of the present invention exhibits better lubrication performance than the conventional product.
次に、第６〜７図は、本考案の第二実施例を示してい
る。上述の第一実施例が、ローラ10の内径面12を潤滑面
とし、軸８の外径面13（第１〜３図参照）に微細な凹凸
を形成していたのに対し、本実施例の場合には、上記内
径面12に表面粗さが0.05〜0.8μmRaの微細な凹凸を形成
している。軸８の外径面13で、上記ローラ10の内径面12
と対向する部分は、表面粗さが0.2μmRa以下の平滑面と
しても、或は表面粗さが0.05μmRa〜0.8μmRaの微細な
凹凸を形成しても良い。6 and 7 show a second embodiment of the present invention. In contrast to the above-described first embodiment in which the inner diameter surface 12 of the roller 10 is used as a lubrication surface and the outer diameter surface 13 of the shaft 8 (see FIGS. In the case of (1), fine irregularities having a surface roughness of 0.05 to 0.8 μmRa are formed on the inner diameter surface 12. The outer diameter surface 13 of the shaft 8 is
May be a smooth surface having a surface roughness of 0.2 μmRa or less, or fine irregularities having a surface roughness of 0.05 μmRa to 0.8 μmRa.
尚、ローラ10の内径面12に表面粗さが0.05〜0.8μmRa
の微細な凹凸を形成する作業は、ホーニング加工に使用
する砥石の粒度を適当に選定する事により行なう。そし
て、砥石の回転速度と軸方向移動速度との関係を適当に
選定する事により、上記内径面12に、第７図に示す様
な、斜格子状の溝を多数形成する。Incidentally, the inner surface 12 of the roller 10 has a surface roughness of 0.05 to 0.8 μm Ra.
The work of forming the fine irregularities is performed by appropriately selecting the grain size of the grindstone used for the honing process. By appropriately selecting the relationship between the rotation speed of the grinding wheel and the axial movement speed, a large number of oblique lattice-shaped grooves are formed on the inner diameter surface 12 as shown in FIG.
次に、第８図は、本考案の第三実施例を示している。
本実施例の場合には、ローラ10の両端部とロッカーアー
ム３の端部に形成した１対の支持壁部７、７の内側面と
の間に、鋼製のワッシャ14、14を設けている。そして、
これら両ワッシャ14、14により、セラミック製で固いロ
ーラ10の端面と、アルミニウム合金製で軟らかい支持壁
部７、７の内側面とが直接接触するのを防止し、各支持
壁部７、７の内側面が異常に摩耗するのを防止してい
る。Next, FIG. 8 shows a third embodiment of the present invention.
In the case of the present embodiment, steel washers 14 are provided between both ends of the roller 10 and inner surfaces of a pair of support walls 7 formed at the ends of the rocker arm 3. I have. And
These two washers 14 prevent the end face of the hard roller 10 made of ceramic from coming into direct contact with the inner surface of the soft support wall 7 made of aluminum alloy. It prevents the inner surface from being abnormally worn.
尚、この場合に於いて好ましくは、ローラ10の両端面
を、表面粗さが0.2μmRa以下の平滑面として、ローラ10
の両端面とワッシャ14、14との間の摩擦係数を小さくし
たり、或は各ワッシャ14、14を軸８に対し回転自在に支
持する事により、上記ワッシャ14、14や支持壁部７、７
の内側面の摩耗を防止する。In this case, it is preferable that both end surfaces of the roller 10 be smooth surfaces having a surface roughness of 0.2 μmRa or less.
By reducing the friction coefficient between both end surfaces of the washer 14 and the washer 14 or by supporting the washer 14 and 14 rotatably with respect to the shaft 8, the washer 14 and 14 and the support wall portion 7 are supported. 7
To prevent wear of the inner surface of the car.
又、第９図に示す様に、ワッシャ14の内周縁に切り欠
き15、15を設け、この切り欠き15、15を通じて、上記ワ
ッシャ14の両側面と、ローラ10の両端面及び支持壁部
７、７の内側面との間に、潤滑油が送り込まれ易くすれ
ば、上記ワッシャ14、14や支持壁部７、７の内側面の磨
耗防止性能が向上する。As shown in FIG. 9, notches 15 and 15 are provided in the inner peripheral edge of the washer 14, and both side surfaces of the washer 14, both end surfaces of the roller 10 and the support wall portion 7 are formed through the notches 15 and 15. If the lubricating oil is easily fed between the inner surfaces of the washer 14, 7 and the inner surfaces of the support walls 7, 7, the performance of preventing the abrasion of the inner surfaces of the washers 14, 14 and the support walls 7, 7 is improved.
更に、ワッシャ14、14を焼き入れ硬化したり、各ワッ
シャ14、14の表面にバレル加工により、表面粗さが0.08
μmRa〜0.3μmRaの微細な凹凸を形成して、この表面に
於ける保油性能を向上させれば、上記ワッシャ14、14や
支持壁部７、７の内側面の磨耗防止を、より確実に図れ
る。Further, the washer 14, 14 is quenched and hardened, or the surface of each washer 14, 14 is barrel-processed to have a surface roughness of 0.08.
By forming fine irregularities of μmRa to 0.3 μmRa to improve the oil retaining performance on this surface, the wear of the washers 14 and 14 and the inner surfaces of the support walls 7 and 7 can be more reliably prevented. I can do it.
（考案の効果） 本考案のエンジンの動弁機構用カムフォロア装置は、
以上に述べた通り、互いに摺接する軸の外径面とローラ
の内径面との一方又は双方に、保油性能の優れた微細な
凹凸を形成する為、鋼製の軸とセラミック製のローラと
の間の潤滑を良好にして、セラミックに比べて軟らかい
軸が摩耗するのを防止し、この軸の耐久性を向上させる
事が出来る。(Effects of the Invention) The cam follower device for the valve operating mechanism of the engine of the invention is:
As described above, in order to form fine irregularities excellent in oil retention performance on one or both of the outer diameter surface of the shaft and the inner surface of the roller that are in sliding contact with each other, a steel shaft and a ceramic roller are used. The lubrication during this period can be improved to prevent the shaft that is softer than ceramic from being worn, thereby improving the durability of the shaft.
第１〜３図は本考案の第一実施例を示しており、第１図
は全体構成を示す、第11図のＡ−Ａ断面に相当する図、
第２図は第１図のＢ−Ｂ断面図、第３図は軸とローラと
の分解斜視図、第４図は潤滑性能に影響するスライスレ
ベルと負荷比との関係を示す線図、第５図は負荷比を説
明する為、表面の凹凸を拡大して示す断面図、第６〜７
図は本考案の第二実施例を示しており、第６図はローラ
の斜視図、第７図はローラの内径面の拡大図、第８図は
本考案の第三実施例を示す、第１図と同様の方向から切
断した断面図、第９図はワッシャの１例を示す斜視図、
第10図はエンジンの動弁機構の１例を示す斜視図、第11
図は第10図に示した動弁機構に組み込んだカムフォロア
装置の側面図、第12図は第11図のＣ−Ｃ断面図である。 1:クランクシャフト、2:カムシャフト、3:ロッカーアー
ム、4:吸気弁、5:排気弁、6:カム、7:支持壁部、8:軸、
9:ころ、10:ローラ、11:通孔、12:内径面、13:外径面、
14:ワッシャ、15:切り欠き。1 to 3 show a first embodiment of the present invention, and FIG. 1 shows the entire structure, and is a view corresponding to the AA section of FIG. 11,
2 is a sectional view taken along line BB of FIG. 1, FIG. 3 is an exploded perspective view of a shaft and a roller, FIG. 4 is a diagram showing a relationship between a slice level and a load ratio affecting lubrication performance. FIG. 5 is an enlarged sectional view showing unevenness on the surface to explain the load ratio, and FIGS.
Fig. 6 shows a second embodiment of the present invention, Fig. 6 is a perspective view of the roller, Fig. 7 is an enlarged view of the inner diameter surface of the roller, and Fig. 8 shows a third embodiment of the present invention. FIG. 9 is a cross-sectional view taken from the same direction as FIG. 1, FIG. 9 is a perspective view showing one example of a washer,
FIG. 10 is a perspective view showing an example of a valve operating mechanism of an engine, and FIG.
The figure is a side view of the cam follower device incorporated in the valve mechanism shown in FIG. 10, and FIG. 12 is a sectional view taken along the line CC of FIG. 1: crankshaft, 2: camshaft, 3: rocker arm, 4: intake valve, 5: exhaust valve, 6: cam, 7: support wall, 8: shaft,
9: roller, 10: roller, 11: through hole, 12: inner diameter surface, 13: outer diameter surface,
14: Washer, 15: Notch.
Claims (3)
転するカムシャフトに固定されたカムと、このカムに対
向して設けられ、このカムの動きを受ける部材に間隔を
開けて形成した１対の支持壁部と、両端の未焼き入れ部
分を上記１対の支持壁部に形成した通孔の内径面に向け
てかしめる事により、この１対の支持壁部の間に掛け渡
す状態で固定された鋼製の軸と、この軸の周囲に回転自
在に支承されたセラミック製のローラとから成るエンジ
ンの動弁機構用カムフォロア装置であって、上記ローラ
の内径面を表面粗さが0.2μmRa以下の平滑面とし、上記
軸の外径面で上記ローラの内径面と対向する部分を焼き
入れ硬化すると共に、少なくともこの部分にバレル加工
により、表面粗さが0.08μmRa〜0.3μmRaの微細な凹凸
を形成する事で、上記軸の外径面とローラの内径面との
間の保油性能を向上させたエンジンの動弁機構用カムフ
ォロア装置。A pair of cams fixed to a camshaft that rotates in synchronization with a crankshaft of an engine, and a pair of members provided opposite to the cams and receiving the movement of the cams, are formed at intervals. The support wall and the unhardened portions at both ends are swaged toward the inner diameter surface of the through hole formed in the pair of support walls, and fixed in a state of being bridged between the pair of support walls. A cam follower for a valve train of an engine, comprising a steel shaft and a ceramic roller rotatably supported around the shaft, the inner surface of the roller having a surface roughness of 0.2 μmRa. The following smooth surface, quenching and hardening the portion of the outer surface of the shaft facing the inner surface of the roller, and at least this portion by barrel processing, the surface roughness of 0.08μmRa ~ 0.3μmRa fine irregularities By forming A cam follower for a valve train of an engine having improved oil retention performance between a radial surface and an inner diameter surface of a roller.
転するカムシャフトに固定されたカムと、このカムに対
向して設けられ、このカムの動きを受ける部材に間隔を
開けて形成した１対の支持壁部と、両端の未焼き入れ部
分を上記１対の支持壁部に形成した通孔の内径面に向け
てかしめる事により、この１対の支持壁部の間に掛け渡
す状態で固定された鋼製の軸と、この軸の周囲に回転自
在に支承されたセラミック製のローラとから成るエンジ
ンの動弁機構用カムフォロア装置であって、上記ローラ
の内径面に表面粗さが0.05〜0.8μmRaの微細な凹凸を形
成し、上記軸の外径面で上記ローラの内径面と対向する
部分を、表面粗さが0.2μmRa以下の平滑面とする事で、
上記軸の外径面とローラの内径面との間の保油性能を向
上させたエンジンの動弁機構用カムフォロア装置。2. A pair of cams fixed to a camshaft that rotates in synchronization with a crankshaft of an engine, and a pair of members provided opposed to the cams and formed with an interval between members that receive the movement of the cams. The support wall and the unhardened portions at both ends are swaged toward the inner diameter surface of the through hole formed in the pair of support walls, and fixed in a state of being bridged between the pair of support walls. A steel shaft and a ceramic roller rotatably supported around the shaft, the cam follower device for an engine valve operating mechanism, wherein the inner surface of the roller has a surface roughness of 0.05 to By forming fine irregularities of 0.8 μmRa, the part of the outer diameter surface of the shaft facing the inner diameter surface of the roller, by making the surface roughness 0.2 μmRa or less a smooth surface,
A cam follower for a valve train of an engine, wherein the oil retaining performance between the outer diameter surface of the shaft and the inner diameter surface of the roller is improved.
転するカムシャフトに固定されたカムと、このカムに対
向して設けられ、このカムの動きを受ける部材に間隔を
開けて形成した１対の支持壁部と、両端の未焼き入れ部
分を上記１対の支持壁部に形成した通孔の内径面に向け
てかしめる事により、この１対の支持壁部の間に掛け渡
す状態で固定された鋼製の軸と、この軸の周囲に回転自
在に支承されたセラミック製のローラとから成るエンジ
ンの動弁機構用カムフォロア装置であって、上記ローラ
の内径面並びに上記軸の外径面で上記ローラの内径面と
対向する部分に、表面粗さが0.05〜0.8μmRaの微細な凹
凸を形成する事で、上記軸の外径面とローラの内径面と
の間の保油性能を向上させたエンジンの動弁機構用カム
フォロア装置。3. A pair of cams fixed to a camshaft that rotates in synchronization with a crankshaft of an engine, and a pair of members provided opposed to the cams and formed with an interval between members that receive the movement of the cams. The support wall and the unhardened portions at both ends are swaged toward the inner diameter surface of the through hole formed in the pair of support walls, and fixed in a state of being bridged between the pair of support walls. A cam follower device for a valve operating mechanism of an engine, comprising a steel shaft provided and a ceramic roller rotatably supported around the shaft, the inner surface of the roller and the outer surface of the shaft. By forming fine irregularities with a surface roughness of 0.05 to 0.8 μm Ra on the part facing the inner diameter surface of the roller, the oil retention performance between the outer diameter surface of the shaft and the inner diameter surface of the roller is improved Cam follower device for the valve train of the engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990016174U JP2590701Y2 (en) | 1990-02-22 | 1990-02-22 | Cam follower for engine valve train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990016174U JP2590701Y2 (en) | 1990-02-22 | 1990-02-22 | Cam follower for engine valve train |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03108806U JPH03108806U (en) | 1991-11-08 |
| JP2590701Y2 true JP2590701Y2 (en) | 1999-02-17 |
Family
ID=31519459
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1990016174U Expired - Fee Related JP2590701Y2 (en) | 1990-02-22 | 1990-02-22 | Cam follower for engine valve train |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2590701Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010021223A1 (en) * | 2008-08-21 | 2010-02-25 | Ntn株式会社 | Cam follower for rocker arm, and cam follower device |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4846474B2 (en) * | 2006-03-10 | 2011-12-28 | エニカ株式会社 | Concealment label and concealment type sheet |
| JP4863805B2 (en) * | 2006-07-31 | 2012-01-25 | 王子タック株式会社 | Concealed seat |
| JP4865440B2 (en) * | 2006-07-31 | 2012-02-01 | 王子タック株式会社 | Concealment label, manufacturing method thereof, concealment type sheet |
| JP2008049618A (en) * | 2006-08-25 | 2008-03-06 | Oji Tac Hanbai Kk | Folding concealment type sheet |
| JP4970879B2 (en) * | 2006-09-06 | 2012-07-11 | 王子タック株式会社 | Adhesive label manufacturing apparatus and manufacturing method, and concealment type sheet manufacturing method |
| JP4755067B2 (en) * | 2006-10-31 | 2011-08-24 | 株式会社オティックス | Valve lifter |
| JP5104376B2 (en) * | 2008-02-15 | 2012-12-19 | 大日本印刷株式会社 | Concealment postcard preparation form |
| JP5086916B2 (en) * | 2008-03-17 | 2012-11-28 | 共同印刷株式会社 | Printed matter |
| JP5322576B2 (en) * | 2008-10-21 | 2013-10-23 | Ｎｔｎ株式会社 | Rocker arm assembly |
| JP5332642B2 (en) * | 2009-01-21 | 2013-11-06 | 日本精工株式会社 | Cam follower device |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62203911U (en) * | 1986-06-13 | 1987-12-26 | ||
| JP2636218B2 (en) * | 1986-06-13 | 1997-07-30 | 三菱自動車工業株式会社 | Rocker arm and method of manufacturing the same |
| JPS648510U (en) * | 1987-07-06 | 1989-01-18 | ||
| JPH01177967A (en) * | 1987-12-30 | 1989-07-14 | Hoya Corp | Barrel finishing method for inorganic hard body |
| JPH01166203U (en) * | 1988-05-11 | 1989-11-21 |
-
1990
- 1990-02-22 JP JP1990016174U patent/JP2590701Y2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010021223A1 (en) * | 2008-08-21 | 2010-02-25 | Ntn株式会社 | Cam follower for rocker arm, and cam follower device |
| JP2010048320A (en) * | 2008-08-21 | 2010-03-04 | Ntn Corp | Cam follower for rocker arm, and cam follower device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03108806U (en) | 1991-11-08 |
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