JPH10325410A - Connecting rod - Google Patents
Connecting rodInfo
- Publication number
- JPH10325410A JPH10325410A JP9151501A JP15150197A JPH10325410A JP H10325410 A JPH10325410 A JP H10325410A JP 9151501 A JP9151501 A JP 9151501A JP 15150197 A JP15150197 A JP 15150197A JP H10325410 A JPH10325410 A JP H10325410A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- large end
- cap
- combination
- metal
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
- F16C9/04—Connecting-rod bearings; Attachments thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/046—Brasses; Bushes; Linings divided or split, e.g. half-bearings or rolled sleeves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は内燃機関、往復動圧
縮機等の往復動機関に用いられるコネクティングロッド
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a connecting rod used for a reciprocating engine such as an internal combustion engine and a reciprocating compressor.
【０００２】[0002]
【従来の技術】図３は往復動内燃機関用コネクティング
ロッドの正面図である。図３において１は大端部、１ａ
は小端部、６は該大端部１と小端部１ａとを結合する桿
部、７は大端部１側のキャップ、９は該キャップ７を大
端部１に締着するための締付ボルトである。３はピスト
ンピン、２はクランクピンであり、かかるコネクティン
グロッドにおいては小端部１ａ側の小端部軸受５にて前
記ピストンピン３を軸支し、大端部軸受４により、クラ
ンクピン２を軸支している。2. Description of the Related Art FIG. 3 is a front view of a connecting rod for a reciprocating internal combustion engine. In FIG. 3, 1 is a large end, 1a
Is a small end, 6 is a rod connecting the large end 1 and the small end 1a, 7 is a cap on the large end 1, and 9 is a cap for fastening the cap 7 to the large end 1. Tightening bolt. Reference numeral 3 denotes a piston pin. Reference numeral 2 denotes a crank pin. In such a connecting rod, the piston pin 3 is supported by a small end bearing 5 on the small end 1a side, and the crank pin 2 is supported by a large end bearing 4. It is pivoted.
【０００３】前記小端部軸受５は円筒状のピストンピン
ブッシュ１０によってピストンピン３を軸支するように
なっている。また、前記大端部軸受４は半割り円筒状の
上メタル８ａと下メタル８ｂとの２つ割り構造であり、
大端部１とキャップ７との組合せ面１１ａ、１１ｂにて
該上・下メタル８ａ・８ｂが接合するようになってい
る。即ち、前記上メタル８ａと下メタル８ｂとは前記締
付ボルト９によりキャップ７を大端部４に締付ける際
に、その組合せ端面同士を圧接してクラッシュを与え、
夫々大端部１の嵌合周面１ｂ及びキャップ７の嵌合周面
７ａ内に夫々圧嵌されるようになっている。そしてピス
トン（図示省略）からピストンピン３を介した軸荷重
（ガス圧及び慣性力）を前記小端部軸受５で支持し、こ
れを桿部６を経て大端部１に伝え、大端部軸受４を介し
てクランクピン２に伝達するようになっている。The small end bearing 5 is configured to support the piston pin 3 by a cylindrical piston pin bush 10. The large end bearing 4 has a split structure of a half-cylindrical upper metal 8a and a lower metal 8b.
The upper and lower metals 8a and 8b are joined at the combination surfaces 11a and 11b of the large end 1 and the cap 7. That is, when the upper metal 8a and the lower metal 8b fasten the cap 7 to the large end 4 by the fastening bolt 9, the combined end faces thereof are pressed against each other to give a crash,
The fitting peripheral surface 1b of the large end 1 and the fitting peripheral surface 7a of the cap 7 are respectively press-fitted. An axial load (gas pressure and inertia force) from a piston (not shown) via a piston pin 3 is supported by the small end bearing 5, transmitted to the large end 1 via the rod 6, and The power is transmitted to the crankpin 2 via the bearing 4.
【０００４】従来、かかる往復動内燃機関用コネクティ
ングロッドにおいては、図４に示すように、大端部軸受
４の上メタル８ａ及び下メタル８ｂの内周の曲率中心３
０は、上メタル８ａと下メタル８ｂとの接合面から該組
合せ面１１ａ、１１ｂに垂直な線（つまりクランクピン
２の中心線）２３上で一致しており、従って組み立て状
態では上メタル８ａと下メタル８ｂとは半径Ｒの完全な
半円筒体となっている。Conventionally, in such a connecting rod for a reciprocating internal combustion engine, as shown in FIG. 4, the center of curvature 3 of the inner circumference of the upper metal 8a and the lower metal 8b of the large end bearing 4 is increased.
0 coincides on a line 23 (that is, the center line of the crankpin 2) perpendicular to the combined surfaces 11a and 11b from the joint surface between the upper metal 8a and the lower metal 8b. The lower metal 8b is a complete semi-cylindrical body having a radius R.
【０００５】[0005]
【発明が解決しようとする課題】かかる往復動内燃機関
においては、図５に示すように、運転中、コネクティン
グロッド、ピストン、ピストンピン等の運動部分の慣性
力Ｆ1 によって大端部軸受４には周期的なキャップ７方
向のクランクピン２による反力、即ち下メタル８ｂへの
軸受荷重Ｆが作用する。かかる荷重Ｆは、大端部軸受４
を上下に引張ったような弾性変形、つまりクローズイン
Ｎをもたらす。In THE INVENTION It is an object of such a reciprocating internal combustion engine, as shown in FIG. 5, in operation, the connecting rod, piston, the inertia force F 1 of the moving part of the piston pin or the like to the large end bearing 4 A periodic reaction force from the crankpin 2 in the direction of the cap 7, that is, a bearing load F acts on the lower metal 8b. The load F is applied to the large end bearing 4
Is elastically deformed as if pulled up and down, that is, close-in N is brought about.
【０００６】即ち、図５において、コネクティングロッ
ドの上方に向いて慣性力Ｆ1 が作用すると、該慣性力Ｆ
1 の反力として大端部軸受４には下向きの軸受荷重Ｆが
作用する。この軸受荷重Ｆは軸受４の上メタル８ａ及び
下メタル８ｂを上下方向に変形させる働きをなし、この
ため、大端部１とキャップ７との組合せ面１１ａ、１１
ｂ付近の大端部軸受面は前記クローズインＮによって内
側に引き寄せられる。That is, in FIG. 5, when the inertial force F 1 acts upward of the connecting rod, the inertial force F 1
As a reaction force of 1, a downward bearing load F acts on the large end bearing 4. The bearing load F serves to deform the upper metal 8a and the lower metal 8b of the bearing 4 in the vertical direction, and therefore, the combined surfaces 11a, 11
The large end bearing surface near b is drawn inward by the close-in N.
【０００７】かかるクローズインＮによってキャップ７
側において下メタル８ｂとクランクピン２との間隙が小
さくなる。そしてかかる間隙の縮小が顕著になると上・
下メタル８ａ・８ｂとクランクピン２とが金属接触を起
こす。[0007] The cap 7 is closed by the close-in N.
On the side, the gap between the lower metal 8b and the crankpin 2 becomes smaller. And when the gap shrinks significantly,
The lower metals 8a and 8b and the crankpin 2 make metal contact.
【０００８】また、かかるクローズインＮの発生がある
と、すべり軸受である大端部軸受４において、荷重負荷
能力が低下する。特に、近年高回転・高出力化されてい
る機関では過大な慣性力が作用するため、大端部は大き
く弾性変形して軸受４の破損を誘発する。When the close-in N occurs, the load bearing capacity of the large end bearing 4 which is a slide bearing is reduced. In particular, in an engine that has recently been increased in rotational speed and output, an excessive inertial force acts thereon, so that the large end portion is largely elastically deformed, and the bearing 4 is damaged.
【０００９】従って本発明は、大端部軸受におけるクロ
ーズインの度合いを抑制して、軸受負荷能力が上昇せし
められ、耐焼付性の大なるコネクティングロッドを提供
することを目的とする。SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a connecting rod that suppresses the degree of close-in in a large end bearing, increases bearing load capacity, and has high seizure resistance.
【００１０】[0010]
【課題を解決するための手段】本発明はかかる課題を解
決するため、ロッド部を含む上部部材の円弧状内面と、
該上部部材にボルト等の締結部材により締着される下部
部材の円弧状内面とによりクランクピンを軸支する大端
部軸受を備えたコネクティングロッドにおいて、前記下
部部材の円弧状内面の曲率中心が、前記上部部材と下部
部材との組合せ面に垂直な線上における該組合せ面より
も上方に位置し、かつ前記上部部材の円弧状内面の曲率
中心が、前記垂直線上の前記組合せ面よりも下方に位置
するように構成されたことを特徴とするコネクティング
ロッドを提案する。According to the present invention, an arc-shaped inner surface of an upper member including a rod portion is provided.
In a connecting rod having a large end bearing that supports a crankpin with an arcuate inner surface of a lower member fastened to the upper member by a fastening member such as a bolt, the center of curvature of the arcuate inner surface of the lower member is , Located above the combination surface on a line perpendicular to the combination surface of the upper member and the lower member, and the center of curvature of the arc-shaped inner surface of the upper member is below the combination surface on the vertical line A connecting rod characterized by being configured to be positioned is proposed.
【００１１】かかる発明によれば、上部部材と下部部材
との組合せ面の近傍における軸受（上部、下部部材）と
クランクピンとの間のクリアランスが大きく形成される
こととなり、軸受荷重が作用しても、下部部材あるいは
上部部材の側部内周とクランクピンの外周との間に接触
の発生は無く、軸受部の弾性変形によって、クランクピ
ンを挟み込むクローズインの度合いを低減することが可
能となる。かかるクローズインの抑制により軸受の負荷
能力が上昇し、耐焼付性が向上する。According to this invention, the clearance between the bearing (upper and lower members) and the crankpin near the combined surface of the upper member and the lower member is increased, and even if a bearing load is applied. There is no contact between the inner periphery of the side part of the lower member or the upper member and the outer periphery of the crankpin, and the degree of the close-in which clamps the crankpin can be reduced by the elastic deformation of the bearing. By suppressing such close-in, the load capacity of the bearing is increased, and seizure resistance is improved.
【００１２】[0012]
【発明の実施の形態】以下、図面を参照して本発明の好
適な実施形態を例示的に詳しく説明する。但しこの実施
形態に記載されている構成部品の寸法、材質、形状、そ
の相対的配置等は特に特定的な記載がないかぎりは、こ
の発明の範囲をそれに限定する趣旨ではなく、単なる説
明例にすぎない。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will now be described in detail with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely illustrative examples. Only.
【００１３】図１は本発明の実施形態に係る内燃機関用
コネクティングロッドの大端部近傍の正面図、図２は作
用説明図、図３は本発明が適用される内燃機関用コネク
ティングロッドの全体正面図である。図３において１は
大端部、１ａは小端部、６は該大端部１と小端部１ａと
を結合する桿部、７は大端部側のキャップ、９は該キャ
ップ７を大端部１に締着するための締付ボルトである。
３はピストンピン、２はクランクピンであり、かかるコ
ネクティングロッドにおいては小端部１ａ側の小端部軸
受５にて前記ピストンピン３を軸支し、大端部軸受４に
より、クランクピン２を軸支している。FIG. 1 is a front view showing the vicinity of a large end of a connecting rod for an internal combustion engine according to an embodiment of the present invention, FIG. 2 is an explanatory view of the operation, and FIG. 3 is an entire connecting rod for an internal combustion engine to which the present invention is applied. It is a front view. In FIG. 3, 1 is a large end, 1a is a small end, 6 is a rod connecting the large end 1 and the small end 1a, 7 is a cap on the large end, and 9 is a large cap. A fastening bolt for fastening to the end 1.
Reference numeral 3 denotes a piston pin. Reference numeral 2 denotes a crank pin. In such a connecting rod, the piston pin 3 is supported by a small end bearing 5 on the small end 1a side, and the crank pin 2 is supported by a large end bearing 4. It is pivoted.
【００１４】前記小端部軸受５は円筒状のブッシュ１０
によってピストンピン３を軸支するようになっている。
また前記大端部軸受４は半割り円筒状の上メタル８ａと
下メタル８ｂとの２つ割り構造であり、大端部１とキャ
ップ７との組合せ面１１ａ、１１ｂにて上・下メタル８
ａ・８ｂが接合するようになっている。The small end bearing 5 has a cylindrical bush 10.
Thereby, the piston pin 3 is pivotally supported.
The large end bearing 4 has a half-cylindrical upper metal 8a and a lower metal 8b divided into two parts, and the upper and lower metal 8 are combined at the combined surfaces 11a and 11b of the large end 1 and the cap 7.
a and 8b are joined.
【００１５】以上の構成は従来技術と同様である。本発
明においては、大端部軸受４の上メタル８ａ及び下メタ
ル８ｂを改良している。即ち図１において、下メタル８
ｂ（内周半径Ｒ1 ）及び、キャップ７に設けられた該下
メタル８ｂの嵌合周面７ａの曲率中心２１は、大端部１
とキャップ７との組合せ面１１ａ、１１ｂ即ち上メタル
８ａと下メタル８ｂとの接合面から該組合せ面１１ａ、
１１ｂに垂直な線（つまりクランクピン２の中心線）２
３上において、該組合せ面１１ａ、１１ｂよりも上方
（組合せ面１１ａ、１１ｂと反対方向）に所定量Ｂ1 偏
位（オフセット）せしめられている。The above configuration is the same as in the prior art. In the present invention, the upper metal 8a and the lower metal 8b of the large end bearing 4 are improved. That is, in FIG.
b (the inner radius R 1 ) and the center of curvature 21 of the fitting peripheral surface 7 a of the lower metal 8 b provided on the cap 7 are
Surfaces 11a and 11b of the upper metal 8a and the lower metal 8b from the combination surfaces 11a and 11b of the
Line perpendicular to 11b (that is, the center line of crankpin 2) 2
On 3, it is brought predetermined amount B 1 displaced (offset) upwards (mating surface 11a, 11b in the opposite direction) than the combination surface 11a, 11b.
【００１６】また、前記上メタル８ａ（内周半径Ｒ
2 ）、及び大端部１に設けられた該上メタル８ａの嵌合
周面１ｂの曲率中心２２は、前記組合せ面１１ａ、１１
ｂに垂直な線２３上において、該組合せ面１１ａ、１１
ｂ面よりも下方に所定量Ｂ2 偏位（オフセット）せしめ
られている。そして、このコネクティングロッドは、図
１に示すように、前記のようにして形成された前記組合
せ面１１ａ、１１ｂの方向の幅が前記垂直線２３の方向
の幅よりも大きいつまり、上下方向に狭く、水平方向に
広い、円弧状の上メタル８ａと下メタル８ｂとが前記組
合せ面１１ａ、１１ｂにて圧接されて前記大端部１及び
キャップ７に夫々組付けられることとなる。The upper metal 8a (inner radius R
2 ) and the center of curvature 22 of the fitting peripheral surface 1b of the upper metal 8a provided on the large end 1 is the same as that of the combination surfaces 11a, 11a.
b on a line 23 perpendicular to b.
A predetermined amount B 2 is offset (offset) below the surface b. As shown in FIG. 1, the connecting rod has a width in the direction of the combination surfaces 11a and 11b formed as described above that is larger than the width in the direction of the vertical line 23, that is, the connecting rod is narrower in the vertical direction. An arc-shaped upper metal 8a and lower metal 8b, which are wide in the horizontal direction, are pressed against each other at the combination surfaces 11a and 11b and are assembled to the large end 1 and the cap 7, respectively.
【００１７】また、かかる上メタル８ａと大端部１の嵌
合周面１ｂ、及び下メタル８ｂとキャプ７の嵌合周面７
ａの加工及び組付けについては、従来のものと同様な真
円形状の大端部軸受４の組合せ面１１ａ、１１ｂから大
端部１側及びキャップ７側を平行に同量だけ削り取って
から上メタル８ａ及び下メタル８ｂを組合せて締付ボル
ト９で締着する。これによって、前記のように、組合せ
面１１ａ、１１ｂの方向に広いメタル８ａ、８ｂとな
る。The upper metal 8a and the fitting peripheral surface 1b of the large end 1 and the lower metal 8b and the fitting peripheral surface 7 of the cap 7
Regarding the processing and assembling of a, the large end 1 side and the cap 7 side are cut in parallel by the same amount from the combination surfaces 11a and 11b of the round end large bearing 4 similar to the conventional one, and then The metal 8a and the lower metal 8b are combined and tightened with the tightening bolt 9. As a result, as described above, the metals 8a and 8b are wide in the direction of the combination surfaces 11a and 11b.
【００１８】かかる構成からなるコネクティングロッド
を組み込んだ内燃機関の運転時において、該コネクティ
ングロッド、ピストン、ピストンピン等の運動部分の慣
性力Ｆ1 （図５参照）によって、大端部軸受４には、図
２に示すように、周期的なキャップ７方向のクランクピ
ン２による反力、即ち下メタル８ｂへの軸受荷重Ｆが作
用する。かかる荷重Ｆにより、大端部軸受４においては
これを上下に引張ったような弾性変形、つまりクローズ
インＮが生起する。During operation of the internal combustion engine incorporating the connecting rod having such a configuration, the inertia force F 1 (see FIG. 5) of the moving part of the connecting rod, piston, piston pin, etc. causes the large end bearing 4 to As shown in FIG. 2, a periodic reaction force from the crankpin 2 in the direction of the cap 7, that is, a bearing load F acts on the lower metal 8 b. Due to the load F, elastic deformation, that is, close-in N, occurs as if the large end bearing 4 is pulled up and down.
【００１９】しかしながら、本発明の実施形態では、上
記２つの円弧状の組合せとしたことによって、図２
（Ａ）に示されるように上・下メタル８ａ・８ｂの組合
せ面１１ａ、１１ｂに近くなるに従って水平方向のクリ
アランス、つまり前記組合せ面１１ａ、１１ｂ上、ある
いはこれに平行な方向のクリアランスＣが大きくなるの
で、上記軸受荷重Ｆが比較的剛性の低いキャップ７の方
向に作用しても、上メタル８ａあるいは下メタル８ｂと
クランクピン２とが接触することは無く、軸受部の弾性
変形によって上記クローズインＮの度合いを、図２
（Ｂ）に示す従来技術に較べて小さくすることができ、
前記組合せ面１１ａ、１１ｂの下部において充分な油膜
厚さを確保することができる。However, in the embodiment of the present invention, the above-mentioned two arc-shaped combinations are used, so that FIG.
As shown in (A), the clearance in the horizontal direction, that is, the clearance C in the direction above or parallel to the combination surfaces 11a and 11b increases as the position approaches the combination surfaces 11a and 11b of the upper and lower metals 8a and 8b. Therefore, even if the bearing load F acts in the direction of the cap 7 having a relatively low rigidity, the upper metal 8a or the lower metal 8b does not come into contact with the crankpin 2, and the closed portion is formed by the elastic deformation of the bearing portion. Figure 2 shows the degree of in-N.
(B) can be smaller than the prior art,
A sufficient oil film thickness can be secured below the combination surfaces 11a and 11b.
【００２０】また、上記のように本発明のクローズイン
Ｎの度合が小さくなり、大端部軸受４における油膜厚さ
の薄くなる箇所が比較的軟剛性のキャップ７の嵌合周面
７ａの底部寄りに移るため、相殺される水平方向油膜圧
力成分が減少し、軸受荷重Ｆを負荷する上向きの油膜圧
力成分が増加することとなり、これによって軸受の負荷
能力が上昇する。As described above, the degree of the close-in N of the present invention is reduced, and the portion of the large end bearing 4 where the oil film thickness is reduced is the bottom of the fitting peripheral surface 7a of the relatively soft rigid cap 7. As a result, the offset horizontal oil film pressure component decreases, and the upward oil film pressure component that applies the bearing load F increases, thereby increasing the load capacity of the bearing.
【００２１】尚、前記のように上メタル８ａ及び下メタ
ル８ｂの軸受面（内面）の曲率半径Ｒ2 、Ｒ1 の増加に
よって軸受面の油膜圧力レベルが上昇することが考えら
れるが、軸受荷重Ｆを受けるキャップ７側の剛性が小さ
く、半径方向の変形量が軸受クリアランスの２〜３倍に
達して、軸受面がクランクピン２にフィットする形で変
形するため、実際の油膜圧力の上昇は殆ど無い。As described above, it is conceivable that the oil film pressure level on the bearing surface is increased by increasing the curvature radii R 2 and R 1 of the bearing surfaces (inner surfaces) of the upper metal 8a and the lower metal 8b. Since the rigidity on the side of the cap 7 receiving F is small, the amount of deformation in the radial direction reaches two to three times the bearing clearance, and the bearing surface is deformed so as to fit the crankpin 2, the actual oil film pressure increases. Almost no.
【００２２】[0022]
【発明の効果】以上記載のごとく、本発明によれば、上
部部材と下部部材との組合せ面の近傍における該上・下
部部材とクランクピンとの間隙を大きく形成することが
できるので、軸受荷重の作用によって、下部部材あるい
は上部部材の側部内周とクランクピンの外周との間に接
触が発生することは無く、軸受部の弾性変形によって、
クランクピンを挟み込むクローズインの度合いを低減す
ることが可能となる。従って、係るクローズインの抑制
により、軸受の負荷能力が上昇し、耐焼付性の向上がな
された軸受部を有するコネクティングロッドを得ること
ができる。As described above, according to the present invention, a large gap between the upper and lower members and the crankpin near the combined surface of the upper and lower members can be formed, so that the bearing load can be reduced. By the action, there is no contact between the inner circumference of the side part of the lower member or the upper member and the outer circumference of the crankpin, and the elastic deformation of the bearing part causes
This makes it possible to reduce the degree of close-in that sandwiches the crankpin. Therefore, by suppressing such close-in, it is possible to obtain a connecting rod having a bearing portion in which the load capacity of the bearing is increased and seizure resistance is improved.
【図１】本発明の実施形態に係る内燃機関用コネクティ
ングロッドの大端部近傍の正面図である。FIG. 1 is a front view near a large end of a connecting rod for an internal combustion engine according to an embodiment of the present invention.
【図２】上記コネクティングロッドにおける作用説明図
である。FIG. 2 is an explanatory diagram of an operation of the connecting rod.
【図３】本発明が適用されるコネクティングロッドの正
面図である。FIG. 3 is a front view of a connecting rod to which the present invention is applied.
【図４】従来のコネクティングロッドを示す図１に対応
する図である。FIG. 4 is a view corresponding to FIG. 1 showing a conventional connecting rod.
【図５】従来のコネクティングロッドの作用説明図であ
る。FIG. 5 is an operation explanatory view of a conventional connecting rod.
【符号の説明】 １ 大端部 １ａ 小端部 １ｂ 嵌合周面 ２ クランクピン ３ ピストンピン ４ 大端部軸受 ５ 小端部軸受 ６ 桿部 ７ キャップ ７ａ 嵌合周面 ８ａ 上メタル ８ｂ 下メタル ９ 締付ボルト １０ ピストンピンブッシュ １１ａ、１１ｂ 組合せ面 ２３ 垂直線[Description of Signs] 1 Large end 1a Small end 1b Fitting peripheral surface 2 Crank pin 3 Piston pin 4 Large end bearing 5 Small end bearing 6 Rod 7 Cap 7a Fitting peripheral surface 8a Upper metal 8b Lower metal 9 Tightening bolt 10 Piston pin bush 11a, 11b Combined surface 23 Vertical line
Claims (1)
と、該上部部材にボルト等の締結部材により締着される
下部部材の円弧状内面とによりクランクピンを軸支する
大端部軸受を備えたコネクティングロッドにおいて、 前記下部部材の円弧状内面の曲率中心が、前記上部部材
と下部部材との組合せ面に垂直な線上における該組合せ
面よりも上方に位置し、かつ前記上部部材の円弧状内面
の曲率中心が、前記垂直線上の前記組合せ面よりも下方
に位置するように構成されたことを特徴とするコネクテ
ィングロッド。A large-end bearing for supporting a crankpin by an arc-shaped inner surface of an upper member including a rod portion and an arc-shaped inner surface of a lower member fastened to the upper member by a fastening member such as a bolt. In the connecting rod provided, the center of curvature of the arc-shaped inner surface of the lower member is located above the combination surface on a line perpendicular to the combination surface of the upper member and the lower member, and the arc shape of the upper member is A connecting rod, wherein a center of curvature of an inner surface is located below the combined surface on the vertical line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9151501A JPH10325410A (en) | 1997-05-26 | 1997-05-26 | Connecting rod |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9151501A JPH10325410A (en) | 1997-05-26 | 1997-05-26 | Connecting rod |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10325410A true JPH10325410A (en) | 1998-12-08 |
Family
ID=15519899
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9151501A Pending JPH10325410A (en) | 1997-05-26 | 1997-05-26 | Connecting rod |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10325410A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010203368A (en) * | 2009-03-04 | 2010-09-16 | Nissan Motor Co Ltd | Double link type variable compression ratio internal combustion engine |
| JP2011058567A (en) * | 2009-09-10 | 2011-03-24 | Daido Metal Co Ltd | Connecting rod bearing for internal combustion engine |
| DE102013203128A1 (en) | 2012-02-27 | 2013-08-29 | Daido Metal Company Ltd. | Plain bearing and bearing device |
| US20220205487A1 (en) * | 2020-12-26 | 2022-06-30 | Enaiyat Ghani Ovy | Novel lemon shaped guide to minimize excessive rubbing in rotating machines |
-
1997
- 1997-05-26 JP JP9151501A patent/JPH10325410A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010203368A (en) * | 2009-03-04 | 2010-09-16 | Nissan Motor Co Ltd | Double link type variable compression ratio internal combustion engine |
| JP2011058567A (en) * | 2009-09-10 | 2011-03-24 | Daido Metal Co Ltd | Connecting rod bearing for internal combustion engine |
| DE102010036284A1 (en) | 2009-09-10 | 2011-04-28 | Daido Metal Company Ltd., Nagoya | Bearing for a connecting rod of an internal combustion engine |
| US8408799B2 (en) | 2009-09-10 | 2013-04-02 | Daido Metal Company Ltd. | Bearing for connecting rod of internal combustion engine |
| DE102013203128A1 (en) | 2012-02-27 | 2013-08-29 | Daido Metal Company Ltd. | Plain bearing and bearing device |
| US8714825B2 (en) | 2012-02-27 | 2014-05-06 | Daido Metal Company Ltd. | Plain bearing and bearing device |
| US20220205487A1 (en) * | 2020-12-26 | 2022-06-30 | Enaiyat Ghani Ovy | Novel lemon shaped guide to minimize excessive rubbing in rotating machines |
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