JP2006064113A - Plain bearing - Google Patents

Plain bearing Download PDF

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JP2006064113A
JP2006064113A JP2004248753A JP2004248753A JP2006064113A JP 2006064113 A JP2006064113 A JP 2006064113A JP 2004248753 A JP2004248753 A JP 2004248753A JP 2004248753 A JP2004248753 A JP 2004248753A JP 2006064113 A JP2006064113 A JP 2006064113A
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circumferential direction
oil groove
plain bearing
bearing
depth
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Inventor
Masao Yamazaki
雅夫 山嵜
Masao Takahashi
正夫 高橋
Yasuhiro Hikita
康弘 疋田
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Taiho Kogyo Co Ltd
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Taiho Kogyo Co Ltd
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    • 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
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C9/02—Crankshaft bearings
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a plain bearing 1 having a leak rate of lubricating oil less than that of a conventional plain bearing. <P>SOLUTION: The plain bearing 1 consisting of a pair (upper and lower) of half bearings 2, 3 is structured in a cylinder shape. A sliding surface 2B of the upper side half bearing 2 has an oil groove 2C along its peripheral direction. The depth of the oil groove 2C is set so that a center part in peripheral direction is shallowest and positions at both end parts in the peripheral direction are deepest. When the plain bearing 1 is mounted on a cylinder block made of aluminum, even if the cylinder block is deformed by combustion load P at the actual operation of an engine, and the plain bearing 1 is also deformed in a narrow shape, leakage of the lubricating oil between the sliding surface 2B and an outer peripheral part of a crank shaft 6 can be restricted as the oil groove 2C of the upper side half bearing 2 is shallow at the center part in the peripheral direction. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明はすべり軸受に関し、より詳しくは、摺動面となる内周面に円周方向に沿った油溝を有するすべり軸受に関する。 The present invention relates to a slide bearing, and more particularly to a slide bearing having an oil groove along the circumferential direction on an inner peripheral surface serving as a sliding surface.

従来、すべり軸受として、摺動面となる内周面に円周方向に沿った油溝を備えたすべり軸受は知られている（例えば特許文献１、特許文献２）。
また、従来、摺動面における円周方向の両端部の位置にクラッシュリリーフを備え、かつ摺動面の円周方向において両端のクラッシュリリーフの位置まで同じ深さの油溝を形成したものも知られている（特許文献１）。
上述した従来のすべり軸受においては、上記油溝に潤滑油を供給し、さらにそこからすべり軸受の摺動面と回転軸の外周面との摺動部分に潤滑油を供給するようにしている。
特開平４−２１９５２１号公報 特開平７−２４３４３４号公報 Conventionally, as a plain bearing, a plain bearing provided with an oil groove along a circumferential direction on an inner peripheral surface serving as a sliding surface is known (for example, Patent Document 1 and Patent Document 2).
Also known is a conventional type having crush reliefs at both ends in the circumferential direction on the sliding surface and oil grooves having the same depth as the crush reliefs at both ends in the circumferential direction of the sliding surface. (Patent Document 1).
In the conventional sliding bearing described above, lubricating oil is supplied to the oil groove, and from there, lubricating oil is supplied to a sliding portion between the sliding surface of the sliding bearing and the outer peripheral surface of the rotary shaft.
JP-A-4-219521 JP-A-7-243434

ところで、最近では鉄製に比べてアルミニウム製のシリンダブロックが採用されることが多くなっているが、鉄製と比べてアルミニウム製のシリンダブロックは熱や荷重による変形が大きい事は知られている。
そして、従来では、図８に示すように、すべり軸受は上下一対の半割り軸受をキャップによってシリンダブロックに取り付けるが、エンジンの実働時においてはシリンダブロックが鉄製かアルミニウム製かによってシリンダブロックおよびキャップの変形量が異なってくる。
より詳細には、ピストンから伝達される燃焼荷重がクランク軸に作用する方向において、つまり、図８の上下方向においてアルミニウム製のシリンダブロックの方が鉄製のシリンダブロックよりも変形量が大きくなり、従って、それにキャップを介して取り付けたすべり軸受の変形量も大きくなる。
そのため、アルミニウム製のシリンダブロックにすべり軸受を取り付けた場合には、すべり軸受の油溝に供給された潤滑油は、すべり軸受の摺動面とクランク軸の外周面に生じた隙間を介して洩れる量が多くなり、ひいては油溝に潤滑油を供給している油圧源の油圧が減少する虞がある。 Recently, aluminum cylinder blocks are more often used than iron ones, but it is known that aluminum cylinder blocks are more deformed by heat and load than iron ones.
Conventionally, as shown in FIG. 8, a plain bearing has a pair of upper and lower halved bearings attached to a cylinder block with a cap. In actual operation of the engine, the cylinder block and the cap depend on whether the cylinder block is made of iron or aluminum. The amount of deformation is different.
More specifically, in the direction in which the combustion load transmitted from the piston acts on the crankshaft, that is, in the vertical direction in FIG. 8, the amount of deformation of the aluminum cylinder block is larger than that of the iron cylinder block. Also, the amount of deformation of the plain bearing attached to the cap via the cap increases.
Therefore, when a slide bearing is attached to an aluminum cylinder block, the lubricating oil supplied to the oil groove of the slide bearing leaks through a clearance generated between the sliding surface of the slide bearing and the outer peripheral surface of the crankshaft. The amount increases, and as a result, the hydraulic pressure of the hydraulic source supplying the lubricating oil to the oil groove may decrease.

上述した事情に鑑み、本発明は、一対の半割り軸受を抱き合わせて円筒状に構成され、上方側となる半割り軸受の摺動面に円周方向に伸びる油溝を備え、キャップを介してシリンダブロックに取り付けられて、回転軸を回転自在に軸支するすべり軸受において、
上記油溝は、円周方向の中央側の箇所が円周方向両端側の箇所よりも深さが浅くなるように設定されているすべり軸受を提供するものである。 In view of the circumstances described above, the present invention is configured by tying a pair of half bearings into a cylindrical shape, and includes an oil groove extending in the circumferential direction on the sliding surface of the upper half bearing, via a cap. In a slide bearing that is attached to a cylinder block and rotatably supports a rotating shaft,
The oil groove provides a plain bearing that is set so that the depth on the center side in the circumferential direction is shallower than the position on both ends in the circumferential direction.

このような構成によれば、円周方向中央側の油溝は深さが浅くなっているので、シリンダブロックが熱や燃焼荷重によって変形することに伴ってすべり軸受が変形した際に、油溝の底部と回転軸の外周面との間の隙間を小さく抑制することができる。したがって、従来と比較して潤滑油の洩れ量が少ないすべり軸受を提供することができる。   According to such a configuration, since the oil groove on the center side in the circumferential direction is shallow, when the slide bearing is deformed along with the deformation of the cylinder block due to heat or combustion load, the oil groove The gap between the bottom of the rotating shaft and the outer peripheral surface of the rotating shaft can be reduced. Therefore, it is possible to provide a plain bearing with less lubricating oil leakage as compared with the prior art.

以下図示実施例について本発明を説明すると、図１において、すべり軸受１は、ともに半円形をした上方側の半割り軸受２と下方側の半割り軸受３とによって全体として円筒状に形成されている。
下方側の半割り軸受３は、下方側のキャップ４の係合凹部４Ａに装着された状態で、該キャップ４を介して図示しないアルミニウム製のシリンダブロックに連結されており、上方側の半割り軸受２は、上方側のハウジング５の係合凹部５Ａに装着されて、上記シリンダブロックに取り付けられている。このようにして、上下の半割り軸受２、３を抱き合わせた状態ですべり軸受１をアルミニウム製のシリンダブロックに取り付けるとともに、すべり軸受１によってクランク軸６を回転自在に軸支している。なお、上記キャップ４は鋳鉄製もしくはアルミニウム製であり、ハウジング５はアルミニウム製であり、両係合凹部４Ａ、５Ａは半円形に形成している。
図１における上方側には図示しないピストンを配置してあり、図示しないコンロッドを介してピストンとクランク軸６とを連結している。したがって、エンジンの実働時においてはピストンからの燃焼荷重Ｐは矢印で示すように、上方側から下方側に向けてクランク軸６に作用するようになっている。 The present invention will be described below with reference to the illustrated embodiment. In FIG. 1, a plain bearing 1 is formed in a cylindrical shape as a whole by an upper half bearing 2 and a lower half bearing 3 which are both semicircular. Yes.
The lower half bearing 3 is connected to an aluminum cylinder block (not shown) through the cap 4 in a state where the lower half bearing 3 is mounted in the engagement recess 4A of the lower cap 4. The bearing 2 is attached to the engagement recess 5A of the upper housing 5 and attached to the cylinder block. In this manner, the sliding bearing 1 is attached to the aluminum cylinder block in a state where the upper and lower half bearings 2 and 3 are joined together, and the crankshaft 6 is rotatably supported by the sliding bearing 1. The cap 4 is made of cast iron or aluminum, the housing 5 is made of aluminum, and both engaging recesses 4A and 5A are formed in a semicircular shape.
A piston (not shown) is arranged on the upper side in FIG. 1, and the piston and the crankshaft 6 are connected via a connecting rod (not shown). Therefore, during actual operation of the engine, the combustion load P from the piston acts on the crankshaft 6 from the upper side to the lower side as shown by the arrow.

図２ないし図３に示すように、半円状をした上方側の半割り軸受２は、円周方向の両端部に突合せ面となる端面２Ａを備えるとともに内周面はクランク軸６と摺動する摺動面２Ｂとしている。
また、上記摺動面２Ｂにおける軸方向の中央位置には、円周方向の全域にわたって油溝２Ｃを形成している。さらに、半割り軸受２には、上記油溝２Ｃまで到達するように半径方向の所定位置に２箇所の貫通孔２Ｄを穿設している。
一方、図１に示すように、下方側の半割り軸受３は、円周方向の両端部の位置に突合せ面となる端面３Ａを備えるとともに、内周面をクランク軸６と摺動する摺動面３Ｂとしている。この下方側の半割り軸受３の摺動面３Ｂには、油溝や貫通孔は形成していない。
上述したようにアルミニウム製のシリンダブロックに上記すべり軸受１を連結すると、該シリンダブロックと上方側のハウジング５にわたって設けた給油通路を介して上記２箇所の貫通孔２Ｄから油溝２Ｃ内に潤滑油を供給され、さらに油溝２Ｃ内の潤滑油は、摺動面２Ｂとクランク軸６の外周面との間の隙間１１に供給されるようになっている。そして、エンジンの実働時にクランク軸６が回転される際には、両半割り軸受２、３の摺動面２Ｂ、３Ｂとクランク軸６との摺動部分に潤滑油が供給されるようになっている。
上述した構成は、基本的に従来公知のすべり軸受と変わるところはない。 As shown in FIGS. 2 to 3, the semi-circular upper half bearing 2 includes end surfaces 2 </ b> A that serve as butt surfaces at both ends in the circumferential direction, and the inner peripheral surface slides with the crankshaft 6. The sliding surface 2B is used.
In addition, an oil groove 2C is formed at the center position in the axial direction on the sliding surface 2B over the entire circumferential direction. Further, the half bearing 2 is formed with two through holes 2D at predetermined positions in the radial direction so as to reach the oil groove 2C.
On the other hand, as shown in FIG. 1, the lower half bearing 3 is provided with end surfaces 3 </ b> A serving as butt surfaces at the positions of both end portions in the circumferential direction, and sliding on the inner peripheral surface with the crankshaft 6. The surface is 3B. No oil groove or through hole is formed in the sliding surface 3B of the lower half bearing 3.
As described above, when the slide bearing 1 is connected to the cylinder block made of aluminum, the lubricating oil enters the oil groove 2C from the two through holes 2D through the oil supply passage provided over the cylinder block and the upper housing 5. Further, the lubricating oil in the oil groove 2 </ b> C is supplied to the gap 11 between the sliding surface 2 </ b> B and the outer peripheral surface of the crankshaft 6. When the crankshaft 6 is rotated during actual operation of the engine, lubricating oil is supplied to the sliding portions between the sliding surfaces 2B and 3B of the half bearings 2 and 3 and the crankshaft 6. ing.
The configuration described above is basically the same as a conventionally known plain bearing.

しかして、本実施例においては、上方側の半割り軸受２における油溝２Ｃの深さを改良することで隙間１１を介して洩れる潤滑油量を減少させるようにしたものである。
上述したように、本実施例においては、アルミニウム製のシリンダブロックに上記すべり軸受１を装着するようにしている。そして、上記すべり軸受１を装着したシリンダブロックを搭載したエンジンを実働させた際には、図１にＰで示したように燃焼荷重がクランク軸６に対して上方から下方に向けて作用する。そのため、すべり軸受１は上記燃焼荷重Ｐの作用方向である上下方向に沿って縦長に引き伸ばされるように変形する（図８参照）。
本願発明者が行った実験の結果によれば、この場合の半割り軸受２の円周方向各部における内径の変化量は図４に示すとおりである。つまり、半割り軸受２の円周方向の一端である０°の位置と他端である１８０°の位置では燃焼荷重の作用方向における半割り軸受２の内径の変化量は最小である。一方、半割り軸受２の円周方向の中央部である９０°の位置では、半割り軸受２の内径の変化量は最大となる。そして、半割り軸受２の一端（０°）および他端（１８０°）の位置から中央（９０°）の位置に近づくほど内径の変化量が徐々に大きくなっている。 Therefore, in this embodiment, the amount of lubricating oil leaking through the gap 11 is reduced by improving the depth of the oil groove 2C in the upper half bearing 2.
As described above, in this embodiment, the slide bearing 1 is mounted on an aluminum cylinder block. When the engine equipped with the cylinder block equipped with the slide bearing 1 is actually operated, the combustion load acts on the crankshaft 6 from the upper side to the lower side as indicated by P in FIG. Therefore, the plain bearing 1 is deformed so as to be elongated in the vertical direction along the vertical direction, which is the direction of action of the combustion load P (see FIG. 8).
According to the result of the experiment conducted by the inventor of the present application, the amount of change in the inner diameter at each portion in the circumferential direction of the half bearing 2 in this case is as shown in FIG. That is, the amount of change in the inner diameter of the half bearing 2 in the direction of action of the combustion load is minimal at the 0 ° position, which is one end in the circumferential direction of the half bearing 2, and the 180 ° position, which is the other end. On the other hand, at the 90 ° position, which is the central portion in the circumferential direction of the half bearing 2, the amount of change in the inner diameter of the half bearing 2 is maximized. The amount of change in the inner diameter is gradually increased from the position of one end (0 °) and the other end (180 °) of the half bearing 2 toward the center (90 °).

そこで、本願の発明者は、半割り軸受２の内径の変化量の分布状態に合わせて半割り軸受２の油溝２Ｃの各部の深さを設定したものである。すなわち、図２、図３および図５に示すように、半割り軸受２の油溝２Ｃは、半割り軸受２の円周方向の一端である０°の位置と他端である１８０°の位置において深さを最も深く設定している。他方、半割り軸受２の円周方向の中央部である９０°の位置では、油溝２Ｃの深さを最も浅く設定している。そして、油溝２Ｃは、半割り軸受２の一端（０°）および他端（１８０°）の位置から中央（９０°）の位置に近づくほど徐々に深さが浅くなるようにしている。
つまり、図４に示した半割り軸受２における円周方向各部の内径の変化量が大きい位置では、油溝２Ｃの深さを浅くするとともに、図４に示した半割り軸受２における円周方向各部の内径の変化量が小さい位置では油溝２Ｃの深さを深くしている。 Therefore, the inventor of the present application sets the depth of each part of the oil groove 2C of the half bearing 2 in accordance with the distribution state of the change amount of the inner diameter of the half bearing 2. That is, as shown in FIGS. 2, 3 and 5, the oil groove 2 </ b> C of the half bearing 2 is positioned at 0 ° which is one end in the circumferential direction of the half bearing 2 and at 180 ° which is the other end. The depth is set most deeply. On the other hand, the depth of the oil groove 2C is set to be the shallowest at a 90 ° position, which is the central portion of the half bearing 2 in the circumferential direction. The oil groove 2C gradually decreases in depth as it approaches the center (90 °) position from the position of one end (0 °) and the other end (180 °) of the half bearing 2.
That is, at the position where the amount of change in the inner diameter of each part in the circumferential direction in the half bearing 2 shown in FIG. 4 is large, the depth of the oil groove 2C is made shallow and the circumferential direction in the half bearing 2 shown in FIG. The oil groove 2C is deepened at a position where the change amount of the inner diameter of each part is small.

以上のように、上方側となる半割り軸受２の油溝２Ｃは、円周方向の両端部の深さが最も深くなり、円周方向における中央部の深さが最も浅くなるように設定されている。
そのため、エンジンの実働時において、図１に示すように上方側からクランク軸６に燃焼荷重Ｐが作用し、それに伴って、鋳鉄製もしくはアルミニウム製のキャップ４、アルミニウム製のハウジング５および両半割り軸受２、３が、燃焼荷重Ｐの作用方向（上下方向）に変形したとしても、油溝２Ｃの円周方向中央部の深さは最も浅くなっているので、円周方向中央部の油溝２Ｃの底部とクランク軸６の外周面との間隙は、円周方向全域を同じ深さの油溝とした場合と比較して小さくなる。
したがって、油溝２Ｃから隙間１１を介して洩れる潤滑油の洩れ量を減少させることができ、ひいては油溝２Ｃへ潤滑油を供給している潤滑油の供給源の油圧が低下することを防止することができる。 As described above, the oil groove 2C of the half bearing 2 on the upper side is set so that the depth at both ends in the circumferential direction is the deepest and the depth at the center in the circumferential direction is the shallowest. ing.
Therefore, during actual operation of the engine, as shown in FIG. 1, a combustion load P acts on the crankshaft 6 from above, and accordingly, a cast iron or aluminum cap 4, an aluminum housing 5, and both halves. Even if the bearings 2 and 3 are deformed in the acting direction (vertical direction) of the combustion load P, the depth of the central portion in the circumferential direction of the oil groove 2C is the shallowest. The gap between the bottom of 2C and the outer peripheral surface of the crankshaft 6 is smaller than that in the case where oil grooves having the same depth are formed in the entire circumferential direction.
Accordingly, the leakage amount of the lubricating oil leaking from the oil groove 2C through the gap 11 can be reduced, and as a result, the oil pressure of the lubricating oil supply source supplying the lubricating oil to the oil groove 2C is prevented from decreasing. be able to.

次に、図６ないし図７は、本発明の第２実施例を示したものであり、この第２実施例においては、円周方向の両端部にクラッシュリリーフ２Ｅ、２Ｅを設けた上方側の半割り軸受２に上記第１実施例と同様の油溝２Ｃを形成したものである。
その他の構成は、前述した第１の実施例と同じである。このような構成の第２実施例であっても上述した第１実施例と同様の作用・効果を得ることができる。 Next, FIGS. 6 to 7 show a second embodiment of the present invention. In the second embodiment, the upper side provided with crush reliefs 2E and 2E at both ends in the circumferential direction is shown. The half bearing 2 is formed with an oil groove 2C similar to that of the first embodiment.
Other configurations are the same as those of the first embodiment described above. Even in the second embodiment having such a configuration, the same operations and effects as those of the first embodiment described above can be obtained.

本発明の第１実施例を示す正面図。The front view which shows 1st Example of this invention. 図１に示した半割り軸受２の内周面側から見た場合の平面図。The top view at the time of seeing from the inner peripheral surface side of the half bearing 2 shown in FIG. 図２のＩＩＩ―ＩＩＩ線に沿う断面図。Sectional drawing which follows the III-III line | wire of FIG. 図１に示した第１実施例についてエンジンの実働時における半割り軸受２の円周方向各部の内径変化量を示す図。The figure which shows the internal diameter variation | change_quantity of each part of the circumferential direction of the half bearing 2 at the time of engine working about 1st Example shown in FIG. 図１に示した半割り軸受における油溝の円周方向各部の位置と深さとの関係を示す図。The figure which shows the relationship between the position and depth of each part of the circumferential direction of an oil groove in the half bearing shown in FIG. 本発明の第２実施例を示す平面図。The top view which shows 2nd Example of this invention. 図６のＶＩＩ―ＶＩＩ線に沿う断面図。Sectional drawing which follows the VII-VII line of FIG. 鉄製とアルミニウム製のシリンダブロックに燃焼荷重が作用した際のキャップの変形量を示す図。The figure which shows the deformation amount of a cap when a combustion load acts on the cylinder blocks made of iron and aluminum. 鉄製とアルミニウム製のシリンダブロックに燃焼荷重が作用した際におけるキャップの内径の変化量と温度との関係を示した図。The figure which showed the relationship between the variation | change_quantity of the internal diameter of a cap at the time of a combustion load acting on the cylinder block made from iron, and aluminum, and temperature.

符号の説明Explanation of symbols

１…すべり軸受 ２…半割り軸受（上方側）
２Ｂ…摺動面 ２Ｃ…油溝
３…半割り軸受（下方側） ４…キャップ
５…ハウジング ６…クランク軸（回転軸） 1 ... Slide bearing 2 ... Half bearing (upper side)
2B ... Sliding surface 2C ... Oil groove 3 ... Half bearing (lower side) 4 ... Cap 5 ... Housing 6 ... Crank shaft (rotating shaft)

Claims (5)

一対の半割り軸受を抱き合わせて円筒状に構成され、上方側となる半割り軸受の摺動面に円周方向に伸びる油溝を備え、キャップを介してシリンダブロックに取り付けられて、回転軸を回転自在に軸支するすべり軸受において、
上記油溝は、円周方向の中央側の箇所が円周方向両端側の箇所よりも深さが浅くなるように設定されていることを特徴とするすべり軸受。 A pair of halved bearings are joined together to form a cylindrical shape, and an oil groove extending in the circumferential direction is provided on the sliding surface of the halved bearing on the upper side. For slide bearings that are rotatably supported,
The slide groove is characterized in that the oil groove is set so that the depth at the center side in the circumferential direction is shallower than the positions at both ends in the circumferential direction. 上記油溝は、円周方向両端側の深さが最大となるとともに円周方向中央部の深さが最小となり、かつ円周方向両端側から中央部へ徐々に深さが浅くなるように設定されていることを特徴とする請求項１に記載のすべり軸受。   The oil groove is set so that the depth at both ends in the circumferential direction is maximized, the depth at the center in the circumferential direction is minimized, and the depth gradually decreases from both ends in the circumferential direction to the center. The plain bearing according to claim 1, wherein the plain bearing is provided. 上記半割り軸受における摺動面の円周方向の両端側に、摺動面を切欠いてクラッシュリリーフを形成してあり、上記油溝の円周方向の両端部は、上記クラッシュリリーフと重合させて設けてあることを特徴とする請求項１又は請求項２に記載のすべり軸受。   A crush relief is formed by cutting out the sliding surface on both ends in the circumferential direction of the sliding surface in the half bearing, and both ends in the circumferential direction of the oil groove are overlapped with the crush relief. The plain bearing according to claim 1, wherein the plain bearing is provided. 上記回転軸に燃焼荷重が作用することに伴って上方側の半割り軸受が変形する際の円周方向各部の変形量に合わせて上記油溝の深さが設定されていることを特徴とする請求項１から請求項３のいずれか１つに記載のすべり軸受。   The depth of the oil groove is set according to the amount of deformation of each part in the circumferential direction when the upper half bearing is deformed as a combustion load acts on the rotating shaft. The plain bearing according to any one of claims 1 to 3. 上記シリンダブロックはアルミニウムからなることを特徴とする請求項１〜請求項４のいずれか１つに記載のすべり軸受。   The plain bearing according to any one of claims 1 to 4, wherein the cylinder block is made of aluminum.
JP2004248753A 2004-08-27 2004-08-27 Plain bearing Pending JP2006064113A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103119311A (en) * 2010-09-03 2013-05-22 曼柴油机和涡轮机欧洲股份公司 Bearing arrangement for a crankshaft of an internal combustion engine
CN104879472A (en) * 2015-06-03 2015-09-02 上海申鹿均质机有限公司 Homogenizer transmission case structure

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0571538A (en) * 1991-09-12 1993-03-23 Ndc Co Ltd Split bearing
JPH1182512A (en) * 1997-09-08 1999-03-26 Daido Metal Co Ltd Slit type sliding bearing and its manufacture
JP2001241442A (en) * 2000-02-25 2001-09-07 Suzuki Motor Corp Journal bearing
JP2002188624A (en) * 2000-12-25 2002-07-05 Daido Metal Co Ltd Split bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0571538A (en) * 1991-09-12 1993-03-23 Ndc Co Ltd Split bearing
JPH1182512A (en) * 1997-09-08 1999-03-26 Daido Metal Co Ltd Slit type sliding bearing and its manufacture
JP2001241442A (en) * 2000-02-25 2001-09-07 Suzuki Motor Corp Journal bearing
JP2002188624A (en) * 2000-12-25 2002-07-05 Daido Metal Co Ltd Split bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103119311A (en) * 2010-09-03 2013-05-22 曼柴油机和涡轮机欧洲股份公司 Bearing arrangement for a crankshaft of an internal combustion engine
CN104879472A (en) * 2015-06-03 2015-09-02 上海申鹿均质机有限公司 Homogenizer transmission case structure

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