JP2002339944A - Connecting rod with bearing - Google Patents
Connecting rod with bearingInfo
- Publication number
- JP2002339944A JP2002339944A JP2001148886A JP2001148886A JP2002339944A JP 2002339944 A JP2002339944 A JP 2002339944A JP 2001148886 A JP2001148886 A JP 2001148886A JP 2001148886 A JP2001148886 A JP 2001148886A JP 2002339944 A JP2002339944 A JP 2002339944A
- Authority
- JP
- Japan
- Prior art keywords
- connecting rod
- roller
- bearing
- outer ring
- length
- 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.)
- Granted
Links
Landscapes
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、エンジンに用い
られる軸受付きコンロッドに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a connecting rod with a bearing used for an engine.
【０００２】[0002]
【従来の技術】従来、図８に示すように、コンロッド５
１の大端部５２および小端部５３の各穴に、シェルタイ
プの針状ころ軸受５５を圧入し、コンロッド幅ｄところ
５７の長さｃとをほぼ同一に設定したものが提案されて
いる（例えば、実開昭６４−３５２１６号）。このよう
に寸法ｃ，ｄの関係を設定することにより、大端部５２
３および小端部５３の張出し部分が小さく、その結果、
軽量化ができ、またコンロッド５１を金属平板のプレス
加工により製作することができる。2. Description of the Related Art Conventionally, as shown in FIG.
A shell-type needle roller bearing 55 is press-fitted into each of the large end portion 52 and the small end portion 53, and the connecting rod width d and the length c are set to be substantially the same. (For example, Japanese Utility Model Application Laid-Open No. 64-21616). By setting the relationship between the dimensions c and d in this way, the large end 52
3 and the overhang portion of the small end portion 53 are small, as a result,
The weight can be reduced, and the connecting rod 51 can be manufactured by pressing a flat metal plate.
【０００３】[0003]
【発明が解決しようとする課題】自動車用部品は、軽量
化の要求があり、コンロッドにおいても軽量化が強く要
求されている。このような軽量化の要求に応じるには、
コンロッド５１の幅ｄを狭くする必要がある。しかし、
コンロッド幅ｄの狭まりに合わせて、ころ５７の長さを
短くすると、ころ５７の単位長さに作用する負荷が大き
くなり、短寿命となる。コンロッドは、ピストンの爆発
的な往復動作をクランクに伝える部品であるため、軸受
に作用する荷重条件が厳しく、ころ長さを短くすると、
寿命に与える影響が大きい。There is a demand for weight reduction of automotive parts, and there is a strong demand for weight reduction of connecting rods. To meet these weight reduction requirements,
The width d of the connecting rod 51 needs to be reduced. But,
When the length of the roller 57 is shortened in accordance with the narrowing of the connecting rod width d, the load acting on the unit length of the roller 57 increases, and the life is shortened. Since the connecting rod is a part that transmits the explosive reciprocating motion of the piston to the crank, the load conditions acting on the bearing are severe, and if the roller length is shortened,
The effect on life is large.
【０００４】この発明の目的は、軽量化と長寿命化の両
方を実現することのできる軸受付きコンロッドを提供す
ることである。[0004] It is an object of the present invention to provide a connecting rod with a bearing capable of realizing both weight reduction and long life.
【０００５】[0005]
【課題を解決するための手段】この発明の軸受付きコン
ロッドは、ロッド部の両端に大端部と小端部とを有し、
これら大端部および小端部に貫通穴が設けられたコンロ
ッドと、外輪およびこの外輪の転走面に沿って転走する
複数のころを有し、上記各貫通穴に嵌合した軸受とを備
えた軸受付きコンロッドにおいて、上記ころの長さが、
上記コンロッドの貫通穴貫通方向の幅よりも長いことを
特徴とする。この構成によると、ころの長さをコンロッ
ド幅よりも長くしたため、コンロッド幅を狭めてコンロ
ッドの軽量化を図っても、ころ長さを確保し、軸受の長
寿命化が図れる。A connecting rod with a bearing according to the present invention has a large end and a small end at both ends of a rod portion.
A connecting rod having a through hole at each of the large end and the small end, and a bearing having an outer ring and a plurality of rollers rolling along a rolling surface of the outer ring, and fitted into each of the through holes. In the connecting rod with bearing provided, the length of the rollers is
It is characterized in that it is longer than the width of the connecting rod in the direction of the through hole. According to this configuration, since the length of the rollers is longer than the width of the connecting rod, even if the width of the connecting rod is reduced to reduce the weight of the connecting rod, the roller length can be secured and the life of the bearing can be extended.
【０００６】この発明において、上記外輪の転走面内径
が開口側ほど大きくなるものであって、転走面内径の最
小径と、ころの端部における転走面内径との径差が、２
０μｍ以下となるようにしても良い。ころ長さがコンロ
ッド幅よりも長いころ軸受をコンロッドの穴に圧入した
場合に、転走面内径が開口側ほど大きくなるように外輪
が変形することがある。この場合に、ころ端部の位置に
おける転走面内径が転走面最小径よりも２０μｍよりも
大きくなるようでは、転走面がころ端部の位置でころを
支持しなくなる。そのため、上記径差を２０μｍ以下に
規定している。この２０μｍ以下という数値は、通常、
軸受の転走面精度として円筒度は２０μｍ以下とするこ
とが必要とされるため、その円筒度を確保する値とな
る。In the present invention, the inner diameter of the rolling surface of the outer ring becomes larger toward the opening, and the difference between the minimum diameter of the inner diameter of the rolling surface and the inner diameter of the rolling surface at the end of the roller is two.
It may be set to 0 μm or less. When a roller bearing whose roller length is longer than the connecting rod width is press-fitted into the hole of the connecting rod, the outer ring may be deformed so that the inner diameter of the rolling surface increases toward the opening. In this case, if the inner diameter of the rolling surface at the position of the roller end is larger than the minimum diameter of the rolling surface by 20 μm, the rolling surface will not support the roller at the position of the roller end. Therefore, the diameter difference is set to 20 μm or less. This value of 20 μm or less is usually
Since the cylindricity is required to be 20 μm or less as the rolling surface accuracy of the bearing, the value is a value that ensures the cylindricity.
【０００７】この発明において、上記コンロッドはロッ
ド部に凹所または穴を有するものとしても良い。このよ
うに凹所または穴を設けることにより、より一層の軽量
化が図れる。In the present invention, the connecting rod may have a recess or a hole in the rod portion. By providing the recesses or holes in this way, the weight can be further reduced.
【０００８】[0008]
【発明の実施の形態】この発明の第１の実施形態を図１
〜図３と共に説明する。この軸受付きコンロッドは、コ
ンロッド１の大端部３および小端部４の貫通穴５に、そ
れぞれ軸受６を嵌合させたものである。コンロッド１
は、ロッド部２の両端に大端部３と小端部４とを有し、
これら大端部３および小端部４に貫通穴５が設けられて
いる。軸受６は、外輪７およびこの外輪７の内径面から
なる転走面に沿って転走する複数のころ８を有し、各こ
ろ８はリング状の保持器９に保持されている。ころ８と
保持器９とは、互いに組立部品となる保持器付きころを
構成するものであり、この保持器付きころを外輪７に挿
入可能なようにしてある。外輪７は直円筒状のものとし
てある。FIG. 1 shows a first embodiment of the present invention.
3 will be described together with FIG. In this connecting rod with a bearing, bearings 6 are fitted into through holes 5 at the large end 3 and the small end 4 of the connecting rod 1, respectively. Connecting rod 1
Has a large end 3 and a small end 4 at both ends of the rod 2,
Through holes 5 are provided in the large end 3 and the small end 4. The bearing 6 has an outer ring 7 and a plurality of rollers 8 rolling along a rolling surface formed of an inner diameter surface of the outer ring 7, and each roller 8 is held by a ring-shaped retainer 9. The rollers 8 and the retainers 9 constitute rollers with retainers that are mutually assembled parts, and the rollers with retainers can be inserted into the outer race 7. The outer ring 7 has a straight cylindrical shape.
【０００９】ころ８の長さＢは、コンロッド１の貫通穴
５の貫通方向の幅Ａよりも長くしてある。コンロッド１
は、大端部３および小端部４の幅を上記の幅Ａとし、ロ
ッド部２の部分の幅は上記の幅Ａよりも狭くしてある。
軸受６の外輪７の幅は、ころ８の長さＢよりも大きく形
成されている。なお、ここで言うころ８の長さＢは、こ
ろ８の全長のことであるが、ころ８の有効長さ、つまり
外周面が円筒形状を成している部分の長さを、コンロッ
ド幅Ａよりも長くすることが好ましい。ころ８の有効長
さは、ころ８の端部に面取部がある場合は、その面取部
の長さを除いた長さである。したがって、ころ有効長さ
は、外輪７の転走面が幾何学上の円筒面であると考えた
場合における転走面の有効幅に合致する。The length B of the roller 8 is longer than the width A of the connecting rod 1 in the through direction of the through hole 5. Connecting rod 1
Is such that the width of the large end 3 and the small end 4 is the width A, and the width of the rod 2 is smaller than the width A.
The width of the outer ring 7 of the bearing 6 is formed larger than the length B of the roller 8. Here, the length B of the roller 8 refers to the total length of the roller 8, and the effective length of the roller 8, that is, the length of the portion where the outer peripheral surface has a cylindrical shape is referred to as a connecting rod width A. It is preferable to make the length longer. The effective length of the roller 8 is a length excluding the length of the chamfered portion when the end of the roller 8 has a chamfered portion. Therefore, the effective roller length matches the effective width of the rolling surface when the rolling surface of the outer ring 7 is considered to be a geometric cylindrical surface.
【００１０】軸受６は、外輪７をコンロッド１の穴５に
圧入することにより、コンロッド１に取付けられてお
り、この圧入のため、外輪７の転走面は、その内径が開
口側ほど大きくなっている。転走面内径の最小径Ｄ
0 （図３）と、ころ８が外輪軸方向の中立位置にあると
きのころ８の端部における転走面内径ＤB との径差ΔＤ
は、所定値以下とする。この所定値は、外輪７の転走面
に要求される円筒度としてあり、数値で示すと、径差Δ
Ｄは２０μｍ以下とする。The bearing 6 is attached to the connecting rod 1 by press-fitting the outer ring 7 into the hole 5 of the connecting rod 1. Due to this press-fitting, the inner diameter of the rolling surface of the outer ring 7 increases toward the opening. ing. Minimum diameter D of rolling surface inner diameter
0 diameter difference ΔD between (Fig. 3), the rolling run face inner diameter D B at the ends of the roller 8 when the rollers 8 is in the neutral position of the outer ring axis
Is not more than a predetermined value. This predetermined value is the cylindricity required for the rolling surface of the outer ring 7, and expressed as a numerical value,
D is 20 μm or less.
【００１１】この構成によると、ころ８の長さＢをコン
ロッド幅Ａよりも長くしたため、コンロッド幅Ａを狭め
てコンロッド１の軽量化を図りながら、ころ長さＢを確
保し、軸受の長寿命化を図ることができる。According to this configuration, since the length B of the roller 8 is longer than the width A of the connecting rod, the roller length B is ensured while the connecting rod width A is narrowed to reduce the weight of the connecting rod 1, and the bearing has a long service life. Can be achieved.
【００１２】軸受寿命ところ長さＢの関係を説明する。
軸受寿命は、次式（１）により表される。 Ｌ＝〔１０6 ／（６０×ｎ）〕×（Ｃｒ／Ｆｒ）10/3 ……（１） ここで、Ｃｒ：動定格荷重 Ｆｒ：ラジアル荷重 ｎ：回転速度 Ｌ：寿命時間The relationship between the bearing life and the length B will be described.
The bearing life is represented by the following equation (1). L = [10 6 / (60 × n)] × (Cr / Fr) 10/3 (1) where Cr: dynamic load rating Fr: radial load n: rotation speed L: life time
【００１３】また、（１）式のＣｒは、次の（２）式に
より表される。 Ｃｒ＝ｆｃ（ｉ cosα）0.78Ｚ2/3 Ｄａ1.07ｌａ0.78 ……（２） ここで、ｆｃ：軸受の種類と材料によって決まる係数 ｉ：ころが有効に働いている列の数 α：接触角 Ｚ：１列あたりのころの数 Ｄａ：ころの直径 ｌａ：ころの接触長さ よって、ころの接触長さｌａを長くすれば、寿命が向上
する。ころの接触長さｌａは、外輪転走面が幾何学上の
円筒面であるとすると、上記のころ有効長さとなる。こ
ろ長さＢを長くすれば、ころの接触長さｌａも長くな
り、したがって軸受寿命が向上する。The Cr in the equation (1) is expressed by the following equation (2). Cr = fc (icosα) 0.78 Z 2/3 Da 1.07 la 0.78 (2) where, fc: coefficient determined by the type and material of the bearing i: number of rows in which rollers work effectively α: contact angle Z: Number of rollers per row Da: Roller diameter la: Roller contact length Accordingly, the longer the roller contact length la, the longer the life. The contact length la of the roller is the above-mentioned roller effective length when the outer ring rolling surface is a geometric cylindrical surface. If the roller length B is increased, the contact length la of the roller is also increased, and the bearing life is improved.
【００１４】この実施形態では、ころ長さＢをコンロッ
ド幅Ａよりも長くしたため、上記のように軽量化を図り
ながら、軸受寿命を向上させることができるが、ころ長
さＢがコンロッド幅Ａよりも長いと、ころ軸受６をコン
ロッド１の貫通穴５に圧入した場合に、図４に誇張して
示すように、転走面内径が開口側ほど大きくなるように
外輪７が変形する。この場合に、ころ端部の位置におけ
る転走面内径ＤB （図３）が転走面最小径Ｄ0 に比べて
２０μｍよりも大きな径差ΔＤが生じるようでは、転走
面がころ端部の位置でころ８を支持しなくなり、ころ長
さＢを長くしても、実際には、ころ接触長さｌａを十分
に長くすることができない。そこで、上記径差ΔＤを２
０μｍ以下に規定している。この２０μｍ以下という数
値は、通常、軸受の転走面精度として円筒度は２０μｍ
以下とすることが必要とされるため、その円筒度を確保
する値とした。このように径差ΔＤを規定したため、上
記のように外輪７の転走面の開口側の内径が大きくなる
形状でありながら、長寿命化が確保される。なお、外輪
７の転走面の内径は、開口側ほど大きくなる形状である
ため、ころ８の端部に大きな荷重が働く状態（いわゆる
エッジロード）となることはなく、回転トルクが異常に
大きくなることもない。In this embodiment, since the roller length B is longer than the connecting rod width A, the bearing life can be improved while the weight is reduced as described above, but the roller length B is larger than the connecting rod width A. If the roller bearing 6 is press-fitted into the through hole 5 of the connecting rod 1, the outer race 7 is deformed so that the inner diameter of the rolling surface becomes larger toward the opening side, as shown in FIG. In this case, the roller rolling run side inner diameter D at the position of the end portion B (Fig. 3) is is like a large diameter difference ΔD occur than 20μm compared to rolling contact surface minimum diameter D 0, rolling run surface roller end portion When the roller 8 is no longer supported at the position (2) and the roller length B is increased, the roller contact length la cannot actually be sufficiently increased. Therefore, the diameter difference ΔD is set to 2
It is defined as 0 μm or less. The numerical value of 20 μm or less usually means that the cylindricity is 20 μm as the rolling contact surface accuracy of the bearing.
Since it is necessary to set the following, the value was set to ensure the cylindricity. Since the diameter difference ΔD is defined in this manner, a long life can be ensured even though the inner diameter of the outer raceway 7 on the opening side of the rolling surface is increased as described above. Since the inner diameter of the rolling surface of the outer ring 7 is larger toward the opening side, a state in which a large load acts on the end of the roller 8 (so-called edge load) does not occur, and the rotational torque is abnormally large. It won't be.
【００１５】径差ΔＤを２０μｍ以下に抑えるには、外
輪７に剛性の高いものを用いることが効果的である。す
なわち、径差ΔＤを２０μｍ以下に抑えることができる
だけの高い剛性を持つ外輪７を使用する。このような剛
性を持つ外輪７としては、例えば直円筒状の削り出しタ
イプの外輪において、肉厚がある程度厚いものとする。
外輪７の肉厚は、コンロッド１の貫通穴５との締代に応
じて設定する。外輪７の材質は、軸受鋼であっても、低
炭素鋼であっても良い。なお、保持器９の材質は自由で
あり、プレス・溶接・削り出し品のいずれの保持器であ
っても良い。保持器９には、焼き付き防止の表面処理加
工をしても良い。ころ８は、保持器９に対して軸未組み
込み状態で脱落するタイプであっても、非脱落タイプで
あっても良い。In order to suppress the diameter difference ΔD to 20 μm or less, it is effective to use an outer ring 7 having high rigidity. That is, the outer ring 7 having high rigidity capable of suppressing the diameter difference ΔD to 20 μm or less is used. As the outer ring 7 having such rigidity, for example, a cutout type outer ring having a straight cylindrical shape has a certain thickness.
The thickness of the outer ring 7 is set according to the interference with the through-hole 5 of the connecting rod 1. The material of the outer ring 7 may be bearing steel or low carbon steel. In addition, the material of the cage 9 is not limited, and may be any of a pressed, welded, and machined cage. The cage 9 may be subjected to a surface treatment for preventing image sticking. The roller 8 may be of a type that falls off the retainer 9 in a state where the shaft is not assembled, or may be a non-dropping type.
【００１６】なお、上記実施形態では、大端部３および
小端部４の両方の軸受６について、ころ長さＢをコンロ
ッド幅Ａよりも長くしたが、大端部３および小端部４の
いずれか片方の軸受６についてのみ、ころ長さＢをコン
ロッド幅Ａよりも長くしても良い。また、ころ端部にお
ける転走面内径ＤB と最小径Ｄ0 の径差ΔＤを、２０μ
ｍ以下とするのも、大端部３および小端部４のいずれか
片方の軸受６についてのみであっても良い。In the above embodiment, the roller length B is longer than the connecting rod width A for the bearings 6 at both the large end 3 and the small end 4. For only one of the bearings 6, the roller length B may be longer than the connecting rod width A. Further, the rolling run side inner diameter D B and the diameter difference ΔD of the minimum diameter D 0 at the roller end portions, 20 [mu]
m may be set only for one of the bearings 6 of the large end 3 and the small end 4.
【００１７】図５は、この発明の他の実施形態を示す。
この実施形態は、第１の実施形態（図１〜図３）にかか
る軸受付きコンロッドにおいて、削り出しタイプの外輪
７を有する軸受６を用いる代わりに、シェルタイプの外
輪７Ａを有する軸受６Ａを用いたものである。シェルタ
イプの外輪７Ａは、鋼板のプレス成形品からなり、両側
に鍔７Ａａを有している。このシェルタイプの軸受６Ａ
も、コンロッド１の大端部３および小端部４の貫通穴５
に圧入により固定される。この実施形態におけるその他
の構成は、第１の実施形態と同じである。シェルタイプ
の外輪７Ａを用いた場合も、圧入の締代の管理等を適宜
に行うことにより、転走面内径の最小径と、ころ８の端
部における転走面内径との径差が２０μｍ以下となるよ
うにすることができる。FIG. 5 shows another embodiment of the present invention.
In this embodiment, in the connecting rod with bearing according to the first embodiment (FIGS. 1 to 3), a bearing 6A having a shell-type outer ring 7A is used instead of using the bearing 6 having a cut-out type outer ring 7. It was what was. The shell-type outer ring 7A is made of a steel sheet press-formed product, and has flanges 7Aa on both sides. This shell type bearing 6A
Also, through holes 5 in the large end 3 and the small end 4 of the connecting rod 1
Is fixed by press-fitting. Other configurations in this embodiment are the same as those in the first embodiment. Even when the shell type outer ring 7A is used, the diameter difference between the minimum diameter of the inner diameter of the rolling surface and the inner diameter of the rolling surface at the end of the roller 8 is 20 μm by appropriately controlling the interference of press fitting. It can be as follows.
【００１８】図６，図７は、この発明のさらに他の実施
形態におけるコンロッド１Ｂを示す。このコンロッド１
Ｂは、ロッド部２に凹所１１および穴１２を設けたもの
である。また、このコンロッド１Ｂは、１枚の平板状の
鋼板から打ち抜き形成されたものとしてあり、コンロッ
ド１Ｂの外周面および両側の貫通穴５が、打ち抜き加工
面とされる。凹所１１および穴１２も、打ち抜き加工時
に同時にプレス加工される。打ち抜き加工は、例えばフ
ァインブランキングプレスにより行われる。このコンロ
ッド１Ｂは、第１の実施形態おいて、そのコンロッド１
に代えて用いられる。この実施形態におけるその他の構
成は、第１の実施形態と同じである。第１の実施形態に
おけるころ長さＢとコンロッド軸受方向幅Ａの関係、お
よび転走面内径の最小径Ｄ0 と、ころ端部における転走
面内径ＤB との径差ΔＤが、２０μｍ以下となる関係
も、この実施形態において保持される。この実施形態で
は、ロッド部２に凹所１１および穴１２を設けたため、
より一層の軽量化が図れる。また、コンロッド１Ｂをフ
ァインブランキングプレスにより打ち抜き加工したた
め、その打ち抜き加工面に研削加工等の後加工が不要
で、生産性に優れる。FIGS. 6 and 7 show a connecting rod 1B according to still another embodiment of the present invention. This connecting rod 1
B shows a rod portion 2 in which a recess 11 and a hole 12 are provided. The connecting rod 1B is formed by punching out a single flat steel plate, and the outer peripheral surface of the connecting rod 1B and the through holes 5 on both sides are punched surfaces. The recess 11 and the hole 12 are also pressed simultaneously with the punching. The punching is performed by, for example, a fine blanking press. This connecting rod 1B is the same as the connecting rod 1B in the first embodiment.
Used in place of Other configurations in this embodiment are the same as those in the first embodiment. First relationship between the length B and the connecting rod bearing width A roller in the embodiment, and a minimum diameter D 0 of the rolling surface inner diameter, the diameter difference ΔD between the rolling run face inner diameter D B at the roller end portions, 20 [mu] m or less Is also maintained in this embodiment. In this embodiment, since the concave portion 11 and the hole 12 are provided in the rod portion 2,
Further weight reduction can be achieved. Further, since the connecting rod 1B is punched by the fine blanking press, post-processing such as grinding is not required on the punched surface, and the productivity is excellent.
【００１９】[0019]
【発明の効果】この発明は、外輪およびころを有する軸
受を、コンロッドの大端部および小端部の貫通穴に嵌合
させた軸受付きコンロッドにおいて、ころの長さを、コ
ンロッドの貫通穴貫通方向の幅よりも長くしたため、軽
量化と長寿命化の両方を実現することができる。上記外
輪の転走面内径が開口側ほど大きくなり、上記転走面内
径の最小径と、上記ころの端部における転走面内径との
径差を２０μｍ以下とした場合は、軸受外輪の圧入によ
って転走面内径が開口側ほど大きくなるように変形して
も、ころ端部まで転走面で支持することができ、長寿命
化が確保できる。上記ロッド部に凹所または穴を有する
場合は、より一層の軽量化が図れる。According to the present invention, in a connecting rod with a bearing in which a bearing having an outer ring and a roller is fitted in through holes at a large end and a small end of a connecting rod, the length of the roller is reduced by the through hole of the connecting rod. Since the width is longer than the width in the direction, both weight reduction and long life can be realized. When the inner diameter of the rolling surface of the outer ring becomes larger toward the opening, and the difference between the minimum diameter of the inner diameter of the rolling surface and the inner diameter of the rolling surface at the end of the roller is set to 20 μm or less, press-fitting of the outer ring of the bearing is performed. Therefore, even if the inner diameter of the rolling surface is deformed so as to become larger toward the opening, the roller end can be supported by the rolling surface, and a longer life can be secured. When the rod portion has a recess or a hole, the weight can be further reduced.
【図面の簡単な説明】[Brief description of the drawings]
【図１】（Ａ），（Ｂ）はそれぞれこの発明の第１の実
施形態における軸受付きコンロッドの断面図および正面
図である。FIGS. 1A and 1B are a sectional view and a front view, respectively, of a connecting rod with a bearing according to a first embodiment of the present invention.
【図２】同軸受付きコンロッドの部分拡大断面図であ
る。FIG. 2 is a partially enlarged sectional view of the connecting rod with a bearing.
【図３】図２の一部をさらに拡大して示す断面図であ
る。FIG. 3 is a sectional view showing a part of FIG. 2 in a further enlarged manner.
【図４】軸受付きコンロッドの外輪の変形状態を示す説
明図である。FIG. 4 is an explanatory view showing a deformed state of an outer ring of a connecting rod with a bearing.
【図５】この発明の他の実施形態にかかる軸受付きコン
ロッドの断面図である。FIG. 5 is a sectional view of a connecting rod with a bearing according to another embodiment of the present invention.
【図６】この発明のさらに他の実施形態におけるコンロ
ッドの正面図である。FIG. 6 is a front view of a connecting rod according to still another embodiment of the present invention.
【図７】同コンロッドの断面図である。FIG. 7 is a sectional view of the connecting rod.
【図８】従来例の断面図である。FIG. 8 is a sectional view of a conventional example.
１，１Ｂ…コンロッド ２…ロッド部 ３…大端部 ４…小端部 ５…貫通穴 ６，６Ａ…軸受 ７，７Ａ…外輪 ８…ころ １１…凹所 １２…穴 Ａ…コンロッド幅 Ｂ…ころの長さ 1, 1B ... connecting rod 2 ... rod part 3 ... large end part 4 ... small end part 5 ... through hole 6, 6A ... bearing 7, 7A ... outer ring 8 ... roller 11 ... recess 12 ... hole A ... connecting rod width B ... roller Length of
Claims (3)
し、これら大端部および小端部に貫通穴が設けられたコ
ンロッドと、外輪およびこの外輪の転走面に沿って転走
する複数のころを有し、上記各貫通穴に嵌合した軸受と
を備えた軸受付きコンロッドにおいて、 上記ころの長さが、上記コンロッドの貫通穴貫通方向の
幅よりも長いことを特徴とする軸受付きコンロッド。1. A connecting rod having a large end portion and a small end portion at both ends of a rod portion, and having a through hole at each of the large end portion and the small end portion, an outer ring and a rolling surface of the outer ring. A connecting rod with a bearing having a plurality of rollers that roll in the through hole, and a bearing fitted into each of the through holes, wherein the length of the roller is longer than the width of the connecting rod in the through hole through direction. A connecting rod with a bearing.
くなり、上記転走面内径の最小径と、上記ころの端部に
おける転走面内径との径差が、２０μｍ以下である請求
項１に記載の軸受付きコンロッド。2. The inner diameter of the rolling surface of the outer ring increases toward the opening, and the difference between the minimum diameter of the inner diameter of the rolling surface and the inner diameter of the rolling surface at the end of the roller is 20 μm or less. Item 2. A connecting rod with a bearing according to item 1.
求項１または請求項２に記載の軸受付きコンロッド。3. The connecting rod with bearing according to claim 1, wherein the rod portion has a recess or a hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001148886A JP3946463B2 (en) | 2001-05-18 | 2001-05-18 | Connecting rod with bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001148886A JP3946463B2 (en) | 2001-05-18 | 2001-05-18 | Connecting rod with bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002339944A true JP2002339944A (en) | 2002-11-27 |
| JP3946463B2 JP3946463B2 (en) | 2007-07-18 |
Family
ID=18994129
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001148886A Expired - Lifetime JP3946463B2 (en) | 2001-05-18 | 2001-05-18 | Connecting rod with bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3946463B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007198481A (en) * | 2006-01-26 | 2007-08-09 | Katsuhiro Yamamoto | Disk brake/pad, back metal of pad, and manufacturing method for the back metal of pad |
| JP2014240694A (en) * | 2013-06-12 | 2014-12-25 | 本田技研工業株式会社 | One-way clutch and vehicular power transmission |
| JP2017078419A (en) * | 2015-10-09 | 2017-04-27 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Large turbocharged two-stroke internal combustion engine |
-
2001
- 2001-05-18 JP JP2001148886A patent/JP3946463B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007198481A (en) * | 2006-01-26 | 2007-08-09 | Katsuhiro Yamamoto | Disk brake/pad, back metal of pad, and manufacturing method for the back metal of pad |
| JP2014240694A (en) * | 2013-06-12 | 2014-12-25 | 本田技研工業株式会社 | One-way clutch and vehicular power transmission |
| JP2017078419A (en) * | 2015-10-09 | 2017-04-27 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Large turbocharged two-stroke internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3946463B2 (en) | 2007-07-18 |
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