JPS63101511A - Bearing structure for connecting rod - Google Patents
Bearing structure for connecting rodInfo
- Publication number
- JPS63101511A JPS63101511A JP24602686A JP24602686A JPS63101511A JP S63101511 A JPS63101511 A JP S63101511A JP 24602686 A JP24602686 A JP 24602686A JP 24602686 A JP24602686 A JP 24602686A JP S63101511 A JPS63101511 A JP S63101511A
- Authority
- JP
- Japan
- Prior art keywords
- cylindrical metal
- connecting rod
- piston
- bearing structure
- inner periphery
- 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
- 239000002184 metal Substances 0.000 claims abstract description 63
- 229910052751 metal Inorganic materials 0.000 claims abstract description 63
- 230000002093 peripheral effect Effects 0.000 claims abstract description 10
- 239000010687 lubricating oil Substances 0.000 abstract description 9
- 238000000034 method Methods 0.000 abstract description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 229910001361 White metal Inorganic materials 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000010969 white metal Substances 0.000 description 1
Landscapes
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、往復動機関におけるピストンとクランク軸と
を連接する連接棒の軸受構造に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a bearing structure for a connecting rod that connects a piston and a crankshaft in a reciprocating engine.
（従来技術及びその問題点）
従来、内燃機関や圧縮機等に用いられる連接棒の大端部
の軸受構造としては、例えば実開昭６０−１２７１８号
公報に開示された技術がある。この技術は、連接棒の大
端部をロンド側の半円形部と半円形のキャップとに２分
割し、該半円形部及び半円形のキャップを２つ割りにし
た半円形状の平軸受部片を介してクランク軸のクランク
ピンに嵌合させた状態で、前記半円形部及び半円形のキ
ャップをボルトとナツトで締結したものである。(Prior Art and its Problems) Conventionally, as a bearing structure for a large end of a connecting rod used in an internal combustion engine, a compressor, etc., there is a technology disclosed in, for example, Japanese Utility Model Application Publication No. 12718/1983. This technology divides the large end of the connecting rod into two parts, a semicircular part on the iron side and a semicircular cap, and creates a semicircular flat bearing by dividing the semicircular part and the semicircular cap into two parts. The semicircular portion and the semicircular cap are fastened with bolts and nuts while being fitted onto the crank pin of the crankshaft via the piece.
しかしながら、このような従来例では１部品点数が多く
なるために１組み付は作業が煩雑となると共にコストが
増大してしまい、かつ慣性質量が大きくなるために、小
型の内燃機関において要求される高速回転には適さない
という問題点があった。However, in such a conventional example, the number of parts per unit is large, so one assembly becomes complicated and costs increase, and the inertial mass becomes large, which is required for small internal combustion engines. The problem was that it was not suitable for high-speed rotation.
部品点数を削減して軽量化を図り、慣性質量を小さくし
て高速回転型の内燃機関や圧縮機等に適するようにした
連接棒大端部の軸受構造としては、例えば実開昭５８−
１１９６１８号公報に開示された技術がある。この技術
は、クランク軸を２分割し、２分割したクランク軸の一
方から延びたクランクピンに連接棒の円形状大端部（一
体型の大端部）をニードルベアリングを介して嵌合し、
かつ２分割したクランク軸の他方に形成されたクランク
ピン孔を前記円形状大端部の外方からクランクピンに嵌
合して組み付けたものである。An example of a bearing structure for the large end of a connecting rod that reduces the number of parts, reduces weight, and reduces inertial mass to make it suitable for high-speed rotating internal combustion engines, compressors, etc.
There is a technique disclosed in Japanese Patent No. 119618. This technology involves dividing the crankshaft into two parts, and fitting the circular large end (integrated large end) of the connecting rod to the crank pin extending from one of the two halves via a needle bearing.
In addition, a crank pin hole formed in the other of the two divided crankshafts is fitted into the crank pin from the outside of the circular large end portion.
しかしながら、このような従来例では、前記連接棒の小
端部が連結されたピストンの往復動による大きな荷重が
前記ニードルベアリングに面圧として集中するため１面
圧を下げるために前記クランクピンの径を大きくしてニ
ードルベアリングの本数を増やすとか、該ニードルベア
リングの幅を広げて該ニードルベアリングの有効長を伸
ばす必要があるが、このようにした場合にはやはり軽量
化が困難であるという問題点がある。However, in such a conventional example, a large load due to the reciprocating motion of the piston to which the small end of the connecting rod is connected is concentrated as surface pressure on the needle bearing. It is necessary to increase the number of needle bearings by increasing the number of needle bearings, or to increase the effective length of the needle bearings by widening the width of the needle bearings, but in this case, the problem is that it is still difficult to reduce the weight. There is.
この問題点を解決するために、第６図に示すように、連
接棒Ａの円形状大端部八〇と前記２分割したクランク軸
の一方から延びたクランクピンＢとの間に、前記ニード
ルベアリングの代りに円筒状メタルＣを介装することが
考えられるが、このように構成した場合には、ピストン
の往復運動による大きな荷重が円筒状メタルＣに作用し
、該メタルＣが図の上下方向に引っ張られて図の一点鎖
線で示すように楕円形状に変形してしまうので、円筒状
メタルＣの、前記ピストンの往復動方向に直交する内周
部Ｃ工、Ｃ２がクランクピンＢの外周とコスしてしまい
、このコスレル部分で潤滑油不足により焼き付きを生じ
てしまうという問題点があった。In order to solve this problem, as shown in FIG. It is conceivable to insert a cylindrical metal C instead of a bearing, but in this case, a large load due to the reciprocating motion of the piston will act on the cylindrical metal C, and the metal C will move upward and downward in the figure. As the inner peripheral part C2 of the cylindrical metal C, which is perpendicular to the reciprocating direction of the piston, becomes the outer periphery of the crank pin B. This caused the problem of seizure due to lack of lubricant in this Cosrel part.
（発明の目的）
本発明は、このような従来の問題点に着目して成された
もので１部品点数及び組み付は工数を削減してコストを
低減することができると共に、軽量化及び慣性質量の低
減化を図ることができ、かつ焼き付きの生じない連接棒
の軸受構造を提供することを目的としている。(Purpose of the Invention) The present invention has been made by focusing on these conventional problems.The number of parts and assembly can be reduced by reducing the number of man-hours and costs, as well as reducing weight and inertia. It is an object of the present invention to provide a bearing structure for a connecting rod that can reduce mass and prevent seizing.
（発明の構成） かかる目的を達成するための本発明の要旨は。(Structure of the invention) The gist of the present invention to achieve this object is as follows.
一端がピストンピンに、他端がクランクピンに夫々軸支
されてピストンとクランク軸とを連接する往復動機関の
連接棒を、少なくとも前記天端の一方に一体型の円筒状
メタルを嵌装して軸支する連接棒の軸受構造において、
前記円筒状メタルの、前記ピストンの往復運動方向と直
交する内周部の内径を、他の内周部に比して大きくした
ことを特徴とする連接棒の軸受構造に存する。A connecting rod of a reciprocating engine connects the piston and the crankshaft with one end supported by a piston pin and the other end supported by a crank pin, and an integrated cylindrical metal fitting is fitted into at least one of the top ends. In the bearing structure of the connecting rod that is supported by
The bearing structure of the connecting rod is characterized in that the inner diameter of the inner peripheral part of the cylindrical metal perpendicular to the reciprocating direction of the piston is larger than the other inner peripheral parts.
（作用）
そして、上記連接棒の軸受構造では、ピストンの往復運
動による大きな荷重が前記円筒状メタルに作用すること
により、該円筒状メタルがピストンの往復運動方向に引
っ張られて変形しても、前記円筒状メタルの、前記ピス
トンの往復運動方向と直交する内周部の内径が、他の内
周部に比して大きくなっているために、前記円筒状メタ
ルの内周とクランクピンの外周との間にコスレル部分が
出来ず、該両者間に潤滑油が十分に供給され、焼き付き
は生じない。(Function) In the bearing structure of the connecting rod, even if a large load due to the reciprocating movement of the piston acts on the cylindrical metal, and the cylindrical metal is pulled and deformed in the direction of the reciprocating movement of the piston, Since the inner diameter of the inner periphery of the cylindrical metal perpendicular to the reciprocating direction of the piston is larger than the other inner periphery, the inner periphery of the cylindrical metal and the outer periphery of the crank pin are larger. A Cosrel part is not formed between the two, and lubricating oil is sufficiently supplied between the two, and seizure does not occur.
（実施例）
以下１図面に基づいて本発明の各実施例を説明する。な
お、各実施例の説明において同様の部位には同一の符号
を付して重複した説明を省略する。(Example) Each example of the present invention will be described below based on one drawing. In addition, in the description of each embodiment, the same parts are given the same reference numerals and redundant description will be omitted.
第１図から第３図は本発明の第１実施例を示している。1 to 3 show a first embodiment of the invention.
第１図及び第３図に示すように、連接棒１は、内燃機関
や圧縮機等の往復動機関に用いられるピストン１０とク
ランク軸２とを連結し、該クランり軸２と共にシリンダ
１０ｂ内でのピストン１０の往復運動を回転運動に変換
するもので、ピストン１０のピストンピン１０ａに連結
される小端部１１と、工学形断面のロンド部１２と、内
周１３ａが真円に加工された円筒形状の大端部１３とが
一体的に形成されて成っている。As shown in FIGS. 1 and 3, the connecting rod 1 connects a piston 10 used in a reciprocating engine such as an internal combustion engine or a compressor to a crankshaft 2, and together with the crankshaft 2, the connecting rod 1 is connected to a cylinder 10b. The piston 10 converts the reciprocating motion of the piston 10 into a rotational motion, and the small end 11 connected to the piston pin 10a of the piston 10, the rond part 12 with an engineering cross section, and the inner circumference 13a are machined into a perfect circle. A large end portion 13 having a cylindrical shape is integrally formed.
第１図に示すように、前記大端部１３の内周１３ａには
ホワイトメタルや、ケルメツト合金等で製造された円筒
状メタル３が圧入されている。第２図に示すように、円
筒状メタル３の外周３ａは真円に加工され、その内周３
ｂは、前記ピストン１０の往復運動方向（図の上下方向
）に短径を持つと共に前記往復運動方向と直交する方向
（図の横方向）に長径を持つ楕円形状に加工されている
。したがって１円筒状メタル３の肉厚は、上下部分３ｃ
。As shown in FIG. 1, a cylindrical metal 3 made of white metal, Kelmet alloy, or the like is press-fitted into the inner periphery 13a of the large end 13. As shown in FIG. As shown in FIG. 2, the outer periphery 3a of the cylindrical metal 3 is machined into a perfect circle, and the inner periphery 3
b is processed into an elliptical shape having a short axis in the reciprocating direction of the piston 10 (vertical direction in the figure) and a long axis in a direction perpendicular to the reciprocating direction (horizontal direction in the figure). Therefore, the thickness of the cylindrical metal 3 is the upper and lower parts 3c.
.
３ｄから左右部分３ｅ、３ｆに向かって夫々徐々に薄く
なっている。すなわち、前記円筒状メタル３の、ピスト
ン１０の往復運動方向と直交する内周部（左右部分３ｅ
、３ｆ）の内径は、他の内周部に比して大きくなってい
る。It gradually becomes thinner from 3d toward the left and right portions 3e and 3f. That is, the inner circumferential portion (left and right portions 3e
, 3f) are larger than the other inner circumferences.
第３図に示すように、前記クランク軸２は２分割された
半割り部２１．２２から成っている。半割り部２１には
、前記円筒状メタル３の内周３ｂが嵌合可能なりランク
ピン２１ａが突設されていると共に、潤滑油の供給通路
２１ｂ、２１ｃが形成されている。一方、半割り部２２
には、クランクピン２１ａに嵌合可能なりランクピン孔
２２ａが穿設されている。As shown in FIG. 3, the crankshaft 2 consists of two halves 21 and 22. The half portion 21 is provided with a protruding rank pin 21a into which the inner periphery 3b of the cylindrical metal 3 can be fitted, and also has lubricating oil supply passages 21b and 21c formed therein. On the other hand, the half part 22
A rank pin hole 22a is formed in the crank pin hole 22a so that the crank pin 21a can be fitted into the crank pin hole 22a.
次に、連接棒１とクランク軸２との組み付は手順を説明
する。Next, the procedure for assembling the connecting rod 1 and the crankshaft 2 will be explained.
まず、連接棒１の大端部１３の内周１３ａに円筒状メタ
ル３の外周３ａを第１図に示すように圧入して嵌合し、
該円筒状メタル３の内周３ｂをクランクピン２１ａに第
３図に示すように嵌合する。First, the outer periphery 3a of the cylindrical metal 3 is press-fitted into the inner periphery 13a of the large end 13 of the connecting rod 1 as shown in FIG.
The inner periphery 3b of the cylindrical metal 3 is fitted onto the crank pin 21a as shown in FIG.
次に、半割り部２２のクランクピン孔２２ａを第３図に
示すように大端部１３の外方からクランクピン２１ａに
嵌合し、この状態で半割り部２２と半割り部２１のクラ
ンクピン２１ａとを締結して組み付けが完了する。Next, as shown in FIG. 3, the crank pin hole 22a of the half-split part 22 is fitted into the crank pin 21a from the outside of the large end part 13, and in this state, the crank pin hole 22a of the half-split part 22 and the half-split part 21 are The assembly is completed by fastening the pin 21a.
上記構成を有する連接棒の軸受構造では、ピストン１０
の往復運動による大きな荷重が連接棒１を介して前記円
筒状メタル３に作用することにより、該円筒状メタル３
がピストン１０の往復運動方向に強い力で引っ張られて
変形すると、該往復運動方向に短径を持つと共に該往復
運動方向と直交する方向に長径を持つ楕円形状の内周３
ｂは、円形状になる。したがって、円形状に変形した円
筒状メタル３の内周３ｂとクランクピン２１ａの外周と
の間にはコスレル部分が出来ず、該内周３ｂとクランク
ピン２１ａの外周との間には潤滑油の供給通路２１ｂ、
２１ｃからの潤滑油が十分に供給され、焼き付きは生じ
ない。In the connecting rod bearing structure having the above configuration, the piston 10
A large load due to the reciprocating motion of
When the piston 10 is pulled by a strong force in the reciprocating direction of the piston 10 and deformed, the inner periphery 3 of an elliptical shape having a short axis in the reciprocating direction and a long axis in a direction perpendicular to the reciprocating direction
b has a circular shape. Therefore, a Cosrel part is not formed between the inner circumference 3b of the cylindrical metal 3 that has been deformed into a circular shape and the outer circumference of the crank pin 21a, and no lubricating oil is formed between the inner circumference 3b and the outer circumference of the crank pin 21a. supply passage 21b,
The lubricating oil from 21c is sufficiently supplied and no seizure occurs.
なお、上記実施例では、連接棒１の大端部１３に前記円
筒状メタル３を嵌装した場合について説明したが、本発
明はこれに限定されるものではなく、小端部１１に円筒
状メタル３を嵌装しても良いことは言うまでもない。In the above embodiment, the case where the cylindrical metal 3 is fitted to the large end 13 of the connecting rod 1 has been described, but the present invention is not limited to this, and the small end 11 is fitted with a cylindrical metal 3. It goes without saying that Metal 3 may be fitted.
次に、第４図に基づいて本発明の第２実施例を説明する
。Next, a second embodiment of the present invention will be described based on FIG.
この第２実施例に係る連接棒の軸受構造は、前記円筒状
メタル３の内周３ｂを楕円形状に加工する代りに１円筒
状メタル３の内外周３ａ、３ｂを真円に加工し、且つ該
内周３ｂの、前記往復運動方向と直交する方向の部位（
左右）に油溜り用の切欠部３ｇ＊３ｇを設けたもので、
他の構成は上記第１実施例と同様である。該切欠部３ｇ
＊３ｇを設けたことにより、前記円筒状メタル３の、ピ
ストン１０の往復運動方向と直交する内周部の内径は、
他の内周部に比して大きくなっている。The bearing structure of the connecting rod according to the second embodiment is such that instead of processing the inner circumference 3b of the cylindrical metal 3 into an elliptical shape, the inner and outer circumferences 3a and 3b of the cylindrical metal 3 are processed into a perfect circle, and A portion of the inner periphery 3b in a direction perpendicular to the reciprocating direction (
It has a cutout of 3g*3g for oil sump on both sides (left and right).
The other configurations are the same as those of the first embodiment. The notch 3g
*By providing 3g, the inner diameter of the inner peripheral portion of the cylindrical metal 3 perpendicular to the reciprocating direction of the piston 10 is
It is larger than the other inner peripheral parts.
上記第２実施例に係る連接棒大端部の軸受構造では、ピ
ストン１０の往復運動による大きな荷重が連接棒１を介
して前記円筒状メタル３に作用することにより、該円筒
状メタル３がピストン１０の往復運動方向に強い力で引
っ張られると、該円筒状メタル３は上下方向に長い楕円
形状に変形するが、その内周３ｂの、前記往復運動方向
と直交する方向の部位に油溜り用の切欠部３ｇｙ３ｇが
あるので、変形した円筒状メタル３の内周３ｂと前記ク
ランクピン２１ａの外周との間にはコスレル部分が出来
ず、該内周３ｂとクランクピン２１ａの外周との間には
潤滑油の供給通路２１ｂ、２１ｃからの潤滑油が十分に
供給され、焼き付きは生じなＵλ。In the bearing structure of the large end of the connecting rod according to the second embodiment, a large load due to the reciprocating motion of the piston 10 acts on the cylindrical metal 3 through the connecting rod 1, so that the cylindrical metal 3 When the cylindrical metal 3 is pulled with a strong force in the direction of the reciprocating motion of 10, the cylindrical metal 3 deforms into an elongated ellipse shape in the vertical direction. Because of the notches 3gy3g, no Cosrel portion is formed between the inner periphery 3b of the deformed cylindrical metal 3 and the outer periphery of the crank pin 21a, and no Cosrel portion is formed between the inner periphery 3b and the outer periphery of the crank pin 21a. The lubricating oil is sufficiently supplied from the lubricating oil supply passages 21b and 21c, and no seizure occurs.
次に、第５図に基づいて上記第１一実施例で用いている
内周が楕円形状である円筒状メタル３（第２図を参照）
を加工する方法について説明する。Next, based on FIG. 5, the cylindrical metal 3 (see FIG. 2) whose inner periphery is elliptical used in the above-mentioned 11th embodiment
We will explain how to process.
まず、第５図（Ａ）に示すように円筒状メタル３０の外
周３０ａ及び内周３０ｂを真円に加工する。次に、第５
図（Ｂ）に示すように、円筒状メタル３０を、楕円形の
取付は孔４ａを持つ治具部材４の該取付は孔４ａに圧入
固定し、該取付は孔４ａに圧入されて外周３０ａ及び内
周３０ｂ共に楕円形状に弾性変形した円筒状メタル３０
の内周３０ｂを図の破線で示すように真円に加工する。First, as shown in FIG. 5(A), the outer periphery 30a and the inner periphery 30b of the cylindrical metal 30 are processed into perfect circles. Next, the fifth
As shown in Figure (B), when mounting a cylindrical metal 30, the jig member 4 having a hole 4a is press-fitted into the hole 4a, and when the jig member 4 is mounted in an oval shape, the jig member 4 is press-fitted into the hole 4a and the outer periphery 30a is fixed. and the inner circumference 30b are both elastically deformed into elliptical shapes.
The inner periphery 30b is machined into a perfect circle as shown by the broken line in the figure.
この加工後に１円筒状メタル３０を取付は孔４ａから取
外すと、第５図（Ｃ）に示すように、外周３ａが真円で
、内周３ｂが楕円形状の前記円筒状メタル３ができあが
る。After this processing, when the cylindrical metal 30 is removed from the mounting hole 4a, the cylindrical metal 3 is completed, with the outer periphery 3a being a perfect circle and the inner periphery 3b being elliptical, as shown in FIG. 5(C).
（発明の効果）
本発明に係る連接棒の軸受構造によれば、連接棒の少な
くとも一端とクランク軸のクランクピンとの間に円筒状
メタルを介装して軸受部を構成したので１部品点数及び
組み付は工数を削減してコストを低減することができる
と共に、クランクピンの軽量化及び慣性質量の低減化を
図ることができ、かつ前記円筒状メタルの、前記ピスト
ンの往復運動方向と直交する内周部の内径を、他の内周
部に比して大きくしたので、ピストンの往復運動による
大きな荷重が前記円筒状メタルに作用することにより、
該円筒状メタルがピストンの往復運動方向に引っ張られ
て変形しても、前記円筒状メタルの内周とクランクピン
の外周との間にコスレル部分が出来ず、該両者間に潤滑
油が十分に供給され、焼き付きは生じない。(Effects of the Invention) According to the bearing structure of the connecting rod according to the present invention, since the bearing part is constructed by interposing a cylindrical metal between at least one end of the connecting rod and the crank pin of the crankshaft, the number of parts is reduced by one part. Assembling can reduce man-hours and costs, as well as reduce the weight and inertial mass of the crank pin, and the cylindrical metal is perpendicular to the reciprocating direction of the piston. Since the inner diameter of the inner circumferential part is made larger than the other inner circumferential parts, a large load due to the reciprocating movement of the piston acts on the cylindrical metal.
Even if the cylindrical metal is pulled and deformed in the direction of the reciprocating movement of the piston, a Cosrel portion is not formed between the inner periphery of the cylindrical metal and the outer periphery of the crank pin, and there is sufficient lubricating oil between the two. is supplied, and no burn-in occurs.
さらに、連接棒の軸受構造に用いる内周が楕円形状の円
筒状メタルを、外周及び内周が共に真円に加工された円
筒状メタルを治具部材の楕円形の取付は孔に圧入固定し
、該取付は孔に圧入されて内周及び外周共に楕円形状に
変形した円筒状メタルの内周を真円に加工することによ
り形成する構成であるので、前記治具部材の取付は孔の
みを楕円形状に高精度に加工しておけば、前記円筒状メ
タルの加工は真円加工だけでよいので、前記円筒状メタ
ルを極めて簡単に且つ高精度に加工することができる。Furthermore, a cylindrical metal with an elliptical inner periphery used for the bearing structure of the connecting rod, and a cylindrical metal whose outer and inner peripheries are both perfectly circular, are press-fitted into the holes to install the elliptical jig members. , Since the mounting is performed by processing the inner periphery of a cylindrical metal that is press-fitted into a hole and deformed into an elliptical shape on both the inner and outer peripheries into a perfect circle, the mounting of the jig member requires only the hole. If the cylindrical metal is machined into an elliptical shape with high precision, the cylindrical metal only needs to be machined into a perfect circle, so the cylindrical metal can be machined extremely easily and with high precision.
第１図から第３図は本発明の第１実施例を示しており、
第１図は連接棒の大端部に円筒状メタルを圧入した状態
を示す連接棒の平面図、第２図は円筒状メタルの拡大平
面図、第３図は軸受部の断面図、第４図は本発明の第２
実施例に係る連接棒の平面図、第５図は内周が楕円形状
である円筒状メタルの加工方法を示す説明図で、第５図
（Ａ）は内外周が真円形である円筒状メタルを示す平面
図、第５図（Ｂ）は同メタルを治具部材に取り付けた状
態を示す断面図、第５図（Ｃ）は完成した円筒状メタル
を示す平面図である。
１・・・連接棒、２・・・クランク軸、３・・・円筒状
メタル、３ｂ・・・円筒状メタルの内周、３ｇ・・・円
筒状メタルの切欠部、４・・・治具部材、４ａ・・・楕
円形状の取付は孔、１１・・・小端部（一端）、１３・
・・大端部（他端）、２１ａ・・・クランクピン。1 to 3 show a first embodiment of the present invention,
Figure 1 is a plan view of the connecting rod showing the cylindrical metal press-fitted into the large end of the connecting rod, Figure 2 is an enlarged plan view of the cylindrical metal, Figure 3 is a sectional view of the bearing, and Figure 4 is a cross-sectional view of the bearing. The figure shows the second aspect of the present invention.
A plan view of the connecting rod according to the embodiment, FIG. 5 is an explanatory view showing a method of processing a cylindrical metal whose inner circumference is an ellipse, and FIG. 5 (A) is a plan view of a cylindrical metal whose inner and outer circumferences are perfectly circular. FIG. 5(B) is a sectional view showing the metal attached to a jig member, and FIG. 5(C) is a plan view showing the completed cylindrical metal. 1... Connecting rod, 2... Crankshaft, 3... Cylindrical metal, 3b... Inner periphery of cylindrical metal, 3g... Notch in cylindrical metal, 4... Jig Member, 4a... Oval shaped mounting hole, 11... Small end (one end), 13...
... Big end (other end), 21a... Crank pin.
Claims (1)
軸支されてピストンとクランク軸とを連接する往復動機
関の連接棒を、前記両端の少なくとも一方に一体型の円
筒状メタルを嵌装して軸支する連接棒の軸受構造におい
て、前記円筒状メタルの、前記ピストンの往復運動方向
と直交する内周部の内径を、他の内周部に比して大きく
したことを特徴とする連接棒の軸受構造。 ２、前記円筒状メタルの内周の、前記往復運動方向と直
交する方向の部位に切欠部を設けたことを特徴とする特
許請求の範囲第１項に記載の連接棒の軸受構造。 ３、前記円筒状メタルの内周を、前記ピストンの往復運
動方向に短径を持つと共に該往復運動方向と直交する方
向に長径を持つ楕円形状に形成したことを特徴とする特
許請求の範囲第１項に記載の連接棒の軸受構造。 ４、内周が楕円形状の円筒状メタルを、外周及び内周が
共に真円に加工された円筒状メタルを楕円形状の取付け
孔を備えた治具部材の該取付け孔に圧入固定し、該取付
け孔に圧入されて内周及び外周共に楕円形状に変形した
円筒状メタルの内周を真円に加工することにより形成し
たことを特徴とする特許請求の範囲第３項に記載の連接
棒の軸受構造。[Claims] 1. A connecting rod of a reciprocating engine that connects the piston and the crankshaft, with one end supported by a piston pin and the other end supported by a crank pin, is provided with an integral type at least one of said ends. In a bearing structure of a connecting rod in which a cylindrical metal is fitted and pivotally supported, the inner diameter of an inner peripheral part of the cylindrical metal perpendicular to the reciprocating direction of the piston is larger than other inner peripheral parts. A connecting rod bearing structure characterized by: 2. The bearing structure for a connecting rod according to claim 1, wherein a notch is provided at a portion of the inner periphery of the cylindrical metal in a direction perpendicular to the reciprocating direction. 3. The inner periphery of the cylindrical metal is formed into an elliptical shape having a short axis in the reciprocating direction of the piston and a long axis in a direction perpendicular to the reciprocating direction. Bearing structure of the connecting rod according to item 1. 4. Press-fit and fix a cylindrical metal whose inner periphery is elliptical, whose outer and inner peripheries are both perfectly circular, into the mounting hole of a jig member equipped with an elliptical mounting hole, and The connecting rod according to claim 3, wherein the connecting rod is formed by processing the inner periphery of a cylindrical metal press-fitted into a mounting hole and deformed into an elliptical shape on both the inner and outer peripheries into a perfect circle. Bearing structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24602686A JPS63101511A (en) | 1986-10-16 | 1986-10-16 | Bearing structure for connecting rod |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24602686A JPS63101511A (en) | 1986-10-16 | 1986-10-16 | Bearing structure for connecting rod |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63101511A true JPS63101511A (en) | 1988-05-06 |
Family
ID=17142344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24602686A Pending JPS63101511A (en) | 1986-10-16 | 1986-10-16 | Bearing structure for connecting rod |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63101511A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10305461A1 (en) * | 2003-02-04 | 2004-08-12 | Federal-Mogul Wiesbaden Gmbh & Co. Kg | Connecting rod with optimized bearing, especially for internal combustion engine, has bearing forming bore that widens along its longitudinal axis towards both open ends |
| DE102004024576A1 (en) * | 2004-05-18 | 2005-12-15 | Daimlerchrysler Ag | Connecting rod for an I.C. engine comprises connecting rod eyes having a cross-section which deviates from a circular or cylindrical shape |
| JP2009275752A (en) * | 2008-05-13 | 2009-11-26 | Toyota Motor Corp | Crankshaft lubricating structure |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5510152A (en) * | 1978-07-07 | 1980-01-24 | Taiho Kogyo Co Ltd | Plain bearing |
| JPS5828009A (en) * | 1981-08-10 | 1983-02-18 | Yamaha Motor Co Ltd | Engine |
-
1986
- 1986-10-16 JP JP24602686A patent/JPS63101511A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5510152A (en) * | 1978-07-07 | 1980-01-24 | Taiho Kogyo Co Ltd | Plain bearing |
| JPS5828009A (en) * | 1981-08-10 | 1983-02-18 | Yamaha Motor Co Ltd | Engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10305461A1 (en) * | 2003-02-04 | 2004-08-12 | Federal-Mogul Wiesbaden Gmbh & Co. Kg | Connecting rod with optimized bearing, especially for internal combustion engine, has bearing forming bore that widens along its longitudinal axis towards both open ends |
| DE102004024576A1 (en) * | 2004-05-18 | 2005-12-15 | Daimlerchrysler Ag | Connecting rod for an I.C. engine comprises connecting rod eyes having a cross-section which deviates from a circular or cylindrical shape |
| JP2009275752A (en) * | 2008-05-13 | 2009-11-26 | Toyota Motor Corp | Crankshaft lubricating structure |
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