JP2017110761A - Slide bearing - Google Patents

Slide bearing Download PDF

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JP2017110761A
JP2017110761A JP2015246781A JP2015246781A JP2017110761A JP 2017110761 A JP2017110761 A JP 2017110761A JP 2015246781 A JP2015246781 A JP 2015246781A JP 2015246781 A JP2015246781 A JP 2015246781A JP 2017110761 A JP2017110761 A JP 2017110761A
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narrow groove
bearing
slide bearing
oil film
rotational direction
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JP6724280B2 (en
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周 神谷
Shu Kamiya
周 神谷
悠一朗 梶木
Yuichiro Kajiki
悠一朗 梶木
裕紀 高田
Hiroki Takata
裕紀 高田
政治 八田
Seiji Hatta
政治 八田
大輔 関
Daisuke Seki
大輔 関
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Taiho Kogyo Co Ltd
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Taiho Kogyo Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a slide bearing which can provide friction reduction effect and can reduce the total oil outflow.SOLUTION: In a slide bearing 1, halved members 2, 2 obtained by splitting, parallel to the axial direction, a cylinder into two are disposed at the top and the bottom. At axial ends of the lower halved member 2, thin grooves 3 are formed in a circumferential direction from a rotationally upstream joint face to a prescribed bearing angle. In addition, the thin grooves 3 are formed from the rotationally upstream joint face to a position rotationally upstream of a position P1 having the minimum oil film thickness, or the thin grooves 3 are formed from the rotationally upstream joint face to a position rotationally upstream of a position P2 having the maximum oil film pressure gradient.SELECTED DRAWING: Figure 2

Description

本発明は、すべり軸受の技術に関する。   The present invention relates to a slide bearing technology.

従来、エンジンのクランクシャフトを軸支するための軸受が公知となっている。また、前記軸受の摺動面積を減らし、フリクション低減効果を得るために、前記軸受の幅を狭くする構造がある。しかし、軸受の幅を狭くすると、流出油量が増加していた。そこで、前記軸受の軸方向両端部に、全周に逃げ部分（細溝）を形成した軸受が公知となっている（例えば、特許文献１参照）。   Conventionally, a bearing for supporting an engine crankshaft is known. Further, in order to reduce the sliding area of the bearing and obtain a friction reduction effect, there is a structure in which the width of the bearing is narrowed. However, when the bearing width was narrowed, the amount of spilled oil increased. Therefore, a bearing in which relief portions (narrow grooves) are formed on the entire circumference at both ends in the axial direction of the bearing is known (for example, see Patent Document 1).

特表２００３−５３２０３６号公報Japanese translation of PCT publication No. 2003-532036

しかし、従来の全周に細溝を形成した軸受では、摺動面積減少により、負荷容量が低下し、良好な潤滑に必要な油膜厚さを確保することができず、且つ、総和の流出油量が多かった。   However, in conventional bearings with narrow grooves on the entire circumference, the load capacity decreases due to the reduction in sliding area, the oil film thickness necessary for good lubrication cannot be secured, and the total spilled oil The amount was large.

そこで、本発明は係る課題に鑑み、フリクション低減効果を得ることができ、総和の流出油量を抑えることができるすべり軸受を提供する。   Then, in view of the subject which concerns, this invention provides the sliding bearing which can acquire a friction reduction effect and can suppress the total oil spill amount.

本発明の解決しようとする課題は以上の如くであり、次にこの課題を解決するための手段を説明する。   The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

即ち、請求項１においては、円筒状に形成したすべり軸受であって、
前記すべり軸受の下部の軸方向端部に円周方向を長手方向とする細溝を設け、
前記細溝は、回転方向上流側端部を前記すべり軸受の最下点よりも回転方向上流側に設け、回転方向下流側端部を前記すべり軸受の最下点よりも回転方向下流側に設けたことを
たものである。 That is, in claim 1, a slide bearing formed in a cylindrical shape,
A narrow groove with the circumferential direction as the longitudinal direction is provided at the axial end of the lower part of the slide bearing,
The narrow groove has an upstream end in the rotational direction provided upstream in the rotational direction from the lowest point of the slide bearing, and a downstream end in the rotational direction provided downstream in the rotational direction from the lowest point of the slide bearing. It is a thing.

また、請求項２においては、前記細溝の長さは、前記細溝による最小油膜厚さの減少率が２０％以下となる長さに設定したものである。   According to a second aspect of the present invention, the length of the narrow groove is set such that a reduction rate of the minimum oil film thickness by the narrow groove is 20% or less.

また、請求項３においては、前記細溝の軸方向外側に周縁部を形成し、前記周縁部の前記細溝底面からの高さは０ｍｍよりも高く、前記すべり軸受の軸との当接面よりも低くなるように形成したものである。   According to a third aspect of the present invention, a peripheral edge is formed on the outer side in the axial direction of the narrow groove, and the height of the peripheral edge from the bottom surface of the narrow groove is higher than 0 mm, and the contact surface with the shaft of the slide bearing It is formed so as to be lower than that.

本発明の効果として、以下に示すような効果を奏する。   As effects of the present invention, the following effects can be obtained.

すなわち、油膜圧力の発生を妨げない程度の細溝を設けることで、摺動面積を減らしつつ、フリクション低減効果を得ることができ、かつ、総和の流出油量を抑えることができる。   That is, by providing a narrow groove that does not hinder the generation of oil film pressure, it is possible to obtain a friction reduction effect while reducing the sliding area, and to suppress the total amount of oil spilled.

本発明の第一の実施形態に係るすべり軸受を示す正面図。The front view which shows the slide bearing which concerns on 1st embodiment of this invention. （ａ）本発明の第一の実施形態に係るすべり軸受を構成する半割部材を示す平面図。（ｂ）同じく（ａ）のＩ−Ｉ線断面図。（ｃ）同じく（ａ）のＩＩ−ＩＩ線断面図。(A) The top view which shows the half member which comprises the slide bearing which concerns on 1st embodiment of this invention. (B) The II sectional view taken on the line of (a). (C) II-II line sectional drawing of (a). 本発明の第二の実施形態に係るすべり軸受を示す正面図。The front view which shows the slide bearing which concerns on 2nd embodiment of this invention. （ａ）本発明の第二の実施形態に係るすべり軸受の正面断面図。（ｂ）同じく（ａ）のＩ−Ｉ線断面図。(A) Front sectional drawing of the slide bearing which concerns on 2nd embodiment of this invention. (B) The II sectional view taken on the line of (a).

次に、発明の実施の形態を説明する。なお、図１はすべり軸受１の正面図であり、画面の上下を上下方向、画面の手前方向及び奥方向を軸方向（前後方向）とする。   Next, embodiments of the invention will be described. FIG. 1 is a front view of the sliding bearing 1, where the top and bottom of the screen is the vertical direction, and the front and back directions of the screen are the axial directions (front and back directions).

まず、第一の実施形態に係るすべり軸受１を構成する半割部材２について図１及び図２を用いて説明する。
すべり軸受１は円筒状の部材であり、図１に示すように、エンジンのクランクシャフト１１のすべり軸受構造に適用される。すべり軸受１は、二つの半割部材２・２で構成されている。二つの半割部材２・２は、円筒を軸方向と平行に二分割した形状であり、断面が半円状となるように形成されている。本実施形態においては、半割部材２・２は上下に配置されており、左右に合わせ面が配置されている。クランクシャフト１１をすべり軸受１で軸支する場合、所定の隙間が形成され、この隙間に対し図示せぬ油路から潤滑油が供給される。 First, the half member 2 which comprises the slide bearing 1 which concerns on 1st embodiment is demonstrated using FIG.1 and FIG.2.
The slide bearing 1 is a cylindrical member and is applied to a slide bearing structure of an engine crankshaft 11 as shown in FIG. The plain bearing 1 is composed of two halved members 2 and 2. The two halved members 2 and 2 have a shape obtained by dividing a cylinder into two in parallel to the axial direction, and are formed so that the cross section is a semicircular shape. In the present embodiment, the half members 2 and 2 are arranged up and down, and mating surfaces are arranged on the left and right. When the crankshaft 11 is pivotally supported by the slide bearing 1, a predetermined gap is formed, and lubricating oil is supplied to the gap from an oil passage (not shown).

図２（ａ）においては、上側および下側の半割部材２を示している。なお、本実施形態においては、クランクシャフト１１の回転方向を図１の矢印に示すように正面視時計回り方向とする。また、軸受角度ωは、図２（ｂ）における右端の位置を０度とし、図２（ｂ）において、反時計回り方向を正とする。すなわち、図２（ｂ）において、左端の位置の軸受角度ωが１８０度となり、下端の位置の軸受角度ωが２７０度となるように定義する。   In FIG. 2A, the upper and lower half members 2 are shown. In the present embodiment, the rotation direction of the crankshaft 11 is the clockwise direction when viewed from the front as indicated by the arrow in FIG. Also, the bearing angle ω is 0 degree at the right end position in FIG. 2B, and the counterclockwise direction in FIG. 2B is positive. That is, in FIG. 2B, the bearing angle ω at the left end position is defined as 180 degrees, and the bearing angle ω at the lower end position is defined as 270 degrees.

上側の半割部材２の内周には円周方向に溝が設けられており、中心に円形の孔が設けられている。また、上側の半割部材２の左右に合わせ面が配置されている。
下側の半割部材２の内周の当接面において、その軸方向の端部に細溝３が形成されている。
細溝３は下側の半割部材２に設けられる。本実施形態においては、細溝３は軸方向に並列して二本設けられている。詳細には、細溝３は、円周方向を長手方向として設けられる。 On the inner periphery of the upper half member 2, a groove is provided in the circumferential direction, and a circular hole is provided in the center. In addition, mating surfaces are arranged on the left and right of the upper half member 2.
A narrow groove 3 is formed at an end portion in the axial direction on the contact surface on the inner periphery of the lower half member 2.
The narrow groove 3 is provided in the lower half member 2. In the present embodiment, two narrow grooves 3 are provided in parallel in the axial direction. Specifically, the narrow groove 3 is provided with the circumferential direction as the longitudinal direction.

下側の半割部材２においては、図２（ｂ）の右側の合わせ面が回転方向上流側合わせ面、図２（ｂ）の左側の合わせ面が回転方向下流側合わせ面となる。   In the lower half member 2, the right mating surface in FIG. 2B is the upstream mating surface in the rotational direction, and the left mating surface in FIG. 2B is the downstream mating surface in the rotational direction.

細溝３は、図２（ｂ）に示すように、回転方向上流側端部３ａと、回転方向下流側端部３ｂとを備える。
細溝３の回転方向下流側端部３ａは、軸受角度ωがω１となる位置に配置されている。
ここで、軸受角度ωがω１となる位置は、すべり軸受１の最下点Ｐ１（軸受角度ωが２７０°）よりも回転方向上流側の位置である。ω１は、２７０°以上であって３１５°以下である。 As shown in FIG. 2B, the narrow groove 3 includes a rotation direction upstream end 3a and a rotation direction downstream end 3b.
The downstream end 3a in the rotation direction of the narrow groove 3 is disposed at a position where the bearing angle ω becomes ω1.
Here, the position at which the bearing angle ω is ω1 is a position upstream of the lowest point P1 of the sliding bearing 1 (the bearing angle ω is 270 °) in the rotational direction. ω1 is 270 ° or more and 315 ° or less.

細溝３の回転方向下流側端部３ａは、軸受角度ωがω２となる位置に配置されている。
ここで、軸受角度ωがω２となる位置は、すべり軸受１の最下点Ｐ１（軸受角度ωが２７０°）よりも回転方向下流側の位置である。ω１は、２２５°以上であって２７０°以下である。 The downstream end 3a in the rotation direction of the narrow groove 3 is disposed at a position where the bearing angle ω becomes ω2.
Here, the position at which the bearing angle ω becomes ω2 is a position on the downstream side in the rotational direction from the lowest point P1 (the bearing angle ω is 270 °) of the slide bearing 1. ω1 is 225 ° or more and 270 ° or less.

このように構成することにより、すべり軸受１の最下点Ｐ１付近に細溝３を設けることができるので、下方向に移動してきた異物等を細溝３内に取り込みやすくなるため、クランクシャフト１１の損傷を防ぐことができる。   By configuring in this way, the narrow groove 3 can be provided in the vicinity of the lowest point P1 of the slide bearing 1, and therefore it becomes easy to take in foreign matter or the like that has moved downward into the narrow groove 3, so that the crankshaft 11 Can prevent damage.

また、細溝３の長さｌは、細溝３による最小油膜厚さの減少率が２０％以下となる長さに設定したものである。最小油膜厚さの減少率とは、細溝を設けなかったすべり軸受の最小油膜厚さに対する細溝３を設けたすべり軸受１の最小油膜厚さの割合（％）を１００％から減算した値である。また、最小油膜厚さの減少率が２０％以下となる長さとは、すべり軸受１が安全な潤滑を行うのに最低限必要な油膜厚さである。最小油膜厚さの減少率が２０％以下となる長さは、回転方向上流側端部の軸受角度ω１と回転方向下流側端部の軸受角度ω２との差の絶対値が９０°以下となるような長さである。   The length 1 of the narrow groove 3 is set to a length at which the reduction rate of the minimum oil film thickness due to the narrow groove 3 is 20% or less. The reduction rate of the minimum oil film thickness is a value obtained by subtracting, from 100%, the ratio (%) of the minimum oil film thickness of the slide bearing 1 with the narrow groove 3 to the minimum oil film thickness of the slide bearing without the narrow groove. It is. The length at which the reduction rate of the minimum oil film thickness is 20% or less is the minimum oil film thickness required for the sliding bearing 1 to perform safe lubrication. The length at which the reduction rate of the minimum oil film thickness is 20% or less is such that the absolute value of the difference between the bearing angle ω1 at the upstream end in the rotation direction and the bearing angle ω2 at the downstream end in the rotation direction is 90 ° or less. It is such a length.

細溝３の幅は、図２（ｃ）に示すように、ｗとなるように形成されている。
また、細溝３の底面から当接面までの高さｄは、半割部材２の外周面から当接面までの高さＤよりも短くなるように形成されている。
また、細溝３の軸方向外側面を形成する周縁部２ａは、細溝３の底面からの高さｈが、細溝３の底面から当接面までの高さｄよりも低くなるように形成されている。すなわち、軸方向外側の周縁部２ａが周囲のクランクシャフト１１との当接面よりも一段低くなるように形成されている。 As shown in FIG. 2C, the narrow groove 3 is formed to have a width w.
The height d from the bottom surface of the narrow groove 3 to the contact surface is formed to be shorter than the height D from the outer peripheral surface of the half member 2 to the contact surface.
In addition, the peripheral edge 2a that forms the outer surface in the axial direction of the narrow groove 3 is such that the height h from the bottom surface of the narrow groove 3 is lower than the height d from the bottom surface of the narrow groove 3 to the contact surface. Is formed. That is, the outer peripheral edge 2a in the axial direction is formed to be one step lower than the contact surface with the surrounding crankshaft 11.

周縁部２ａが周囲のクランクシャフト１１との当接面よりも一段低くなるように形成されていることにより、クランクシャフト１１が傾いて軸方向片側端部にのみ接触する状態（片当りする状態）となったときに、周縁部２ａとクランクシャフト１１との接触機会を減らすことができるため、周縁部２ａの損傷を防止することができる。   The peripheral edge 2a is formed so as to be one step lower than the contact surface with the surrounding crankshaft 11, so that the crankshaft 11 is tilted and is in contact with only one end in the axial direction (a state where it comes into contact with one side) When it becomes, since the contact opportunity with the peripheral part 2a and the crankshaft 11 can be reduced, damage to the peripheral part 2a can be prevented.

また、周縁部２ａが周囲の当接面よりも一段低くなるように形成されていることにより、すべり軸受１の軸方向端部における隙間が広がり、吸い戻し油量が増えてトータルの流出油量が低減される。   Further, since the peripheral edge portion 2a is formed so as to be one step lower than the surrounding contact surface, the gap at the axial end portion of the slide bearing 1 is widened, and the amount of sucked-back oil is increased and the total amount of oil spilled Is reduced.

以上のように、円筒状に形成したすべり軸受１であって、すべり軸受１の下部の軸方向端部に円周方向を長手方向とする細溝３・３を設け、細溝３・３は、回転方向上流側端部３ａをすべり軸受１の最下点Ｐ１よりも回転方向上流側に設け、回転方向下流側端部３ｂをすべり軸受１の最下点Ｐ１よりも回転方向下流側に設けたものである。
このように構成することにより、油膜圧力の発生を妨げない程度の細溝３を設けることで、摺動面積を減らしつつ、フリクション低減効果を得ることができ、かつ、総和の流出油量を抑えることができる。また、すべり軸受１の最下点Ｐ１付近に細溝３を設けることができるので、下方向に移動してきた異物等を細溝３内に取り込みやすくなるため、クランクシャフト１１の損傷を防ぐことができる。 As described above, in the slide bearing 1 formed in a cylindrical shape, the narrow grooves 3 and 3 having the circumferential direction as the longitudinal direction are provided at the axial end portion of the lower portion of the slide bearing 1. The upstream end 3a in the rotational direction is provided on the upstream side in the rotational direction from the lowest point P1 of the slide bearing 1, and the downstream end 3b in the rotational direction is provided on the downstream side in the rotational direction from the lowest point P1 of the slide bearing 1. It is a thing.
With this configuration, by providing the narrow groove 3 that does not hinder the generation of the oil film pressure, it is possible to obtain a friction reduction effect while reducing the sliding area, and to suppress the total amount of oil spilled. be able to. Further, since the narrow groove 3 can be provided in the vicinity of the lowest point P1 of the slide bearing 1, foreign matters that have moved downward can be easily taken into the narrow groove 3, so that damage to the crankshaft 11 can be prevented. it can.

また、細溝３の長さｌは、細溝３による最小油膜厚さの減少率が２０％以下となる長さに設定したものである。
このように構成することにより、負荷容量の低下を抑えつつ、フリクション低減効果を得ることができ、かつ、総和の流出油量を抑えることができる。 The length 1 of the narrow groove 3 is set to a length at which the reduction rate of the minimum oil film thickness due to the narrow groove 3 is 20% or less.
With this configuration, it is possible to obtain a friction reduction effect while suppressing a decrease in load capacity, and it is possible to suppress the total amount of oil spilled.

また、細溝３の軸方向外側に周縁部２ａを形成し、周縁部２ａの細溝３底面からの高さｈは０ｍｍよりも高く、すべり軸受１のクランクシャフト１１との当接面よりも低くなるように形成したものである。
このように構成することにより、クランクシャフト１１が傾いて軸方向片側端部にのみ接触する状態（片当りする状態）となったときに、周縁部２ａとクランクシャフト１１との接触機会を減らすことができるため、周縁部２ａの損傷を防止することができる。 Further, the peripheral edge 2a is formed on the outer side in the axial direction of the narrow groove 3, and the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is higher than 0 mm, which is higher than the contact surface with the crankshaft 11 of the slide bearing 1. It is formed so as to be lowered.
By configuring in this way, when the crankshaft 11 is tilted and comes into contact with only one end portion in the axial direction (a state where it comes into contact with each other), the chance of contact between the peripheral edge 2a and the crankshaft 11 is reduced. Therefore, damage to the peripheral edge 2a can be prevented.

次に、第二の実施形態に係るすべり軸受２１について図１及び図２を用いて説明する。
すべり軸受２１は円筒状の部材である。すべり軸受２１は、板状の金属を円筒状に形成することで設けられる。 Next, the plain bearing 21 according to the second embodiment will be described with reference to FIGS. 1 and 2.
The slide bearing 21 is a cylindrical member. The slide bearing 21 is provided by forming a plate-like metal into a cylindrical shape.

図４（ａ）においては、すべり軸受２１の断面図を示している。なお、本実施形態においては、クランクシャフト１１の回転方向を図１の矢印に示すように正面視時計回り方向とする。また、軸受角度ωは、図４（ａ）における右端の位置を０度とし、図４（ａ）において、反時計回り方向を正とする。すなわち、図４（ａ）において、左端の位置の軸受角度ωが１８０度となり、下端の位置の軸受角度ωが２７０度となるように定義する。   FIG. 4A shows a cross-sectional view of the slide bearing 21. In the present embodiment, the rotation direction of the crankshaft 11 is the clockwise direction when viewed from the front as indicated by the arrow in FIG. The bearing angle ω is 0 degree at the right end position in FIG. 4A, and the counterclockwise direction in FIG. 4A is positive. That is, in FIG. 4A, the bearing angle ω at the left end position is defined as 180 degrees, and the bearing angle ω at the lower end position is defined as 270 degrees.

すべり軸受２１の内周の当接面において、その軸方向の端部に細溝３が形成されている。
細溝３はすべり軸受２１の下部に設けられる。本実施形態においては、細溝３は軸方向に並列して二本設けられている。詳細には、細溝３は、円周方向を長手方向として設けられる。 A narrow groove 3 is formed at the axial end of the contact surface on the inner periphery of the slide bearing 21.
The narrow groove 3 is provided in the lower part of the slide bearing 21. In the present embodiment, two narrow grooves 3 are provided in parallel in the axial direction. Specifically, the narrow groove 3 is provided with the circumferential direction as the longitudinal direction.

細溝３は、図４（ａ）に示すように、回転方向上流側端部３ａと、回転方向下流側端部３ｂとを備える。
細溝３の回転方向下流側端部３ａは、軸受角度ωがω１となる位置に配置されている。
ここで、軸受角度ωがω１となる位置は、すべり軸受２１の最下点Ｐ１（軸受角度ωが２７０°）よりも回転方向上流側の位置である。ω１は、２７０°以上であって３１５°以下である。 As shown in FIG. 4A, the narrow groove 3 includes a rotation direction upstream end 3a and a rotation direction downstream end 3b.
The downstream end 3a in the rotation direction of the narrow groove 3 is disposed at a position where the bearing angle ω becomes ω1.
Here, the position at which the bearing angle ω becomes ω1 is a position upstream of the lowest point P1 (the bearing angle ω is 270 °) of the sliding bearing 21 in the rotational direction. ω1 is 270 ° or more and 315 ° or less.

細溝３の回転方向下流側端部３ａは、軸受角度ωがω２となる位置に配置されている。
ここで、軸受角度ωがω２となる位置は、すべり軸受２１の最下点Ｐ１（軸受角度ωが２７０°）よりも回転方向下流側の位置である。ω１は、２２５°以上であって２７０°以下である。 The downstream end 3a in the rotation direction of the narrow groove 3 is disposed at a position where the bearing angle ω becomes ω2.
Here, the position at which the bearing angle ω is ω2 is a position on the downstream side in the rotational direction from the lowest point P1 of the plain bearing 21 (the bearing angle ω is 270 °). ω1 is 225 ° or more and 270 ° or less.

このように構成することにより、すべり軸受２１の最下点Ｐ１付近に細溝３を設けることができるので、下方向に移動してきた異物等を細溝３内に取り込みやすくなるため、クランクシャフト１１の損傷を防ぐことができる。   By configuring in this way, the narrow groove 3 can be provided in the vicinity of the lowest point P1 of the slide bearing 21, so that it becomes easy to take in foreign matter or the like that has moved downward into the narrow groove 3, so that the crankshaft 11 Can prevent damage.

また、細溝３の長さｌは、細溝３による最小油膜厚さの減少率が２０％以下となる長さに設定したものである。最小油膜厚さの減少率とは、細溝を設けなかったすべり軸受の最小油膜厚さに対する細溝３を設けたすべり軸受２１の最小油膜厚さの割合（％）を１００％から減算した値である。また、最小油膜厚さの減少率が２０％以下となる長さとは、すべり軸受２１が安全な潤滑を行うのに最低限必要な油膜厚さである。最小油膜厚さの減少率が２０％以下となる長さは、回転方向上流側端部の軸受角度ω１と回転方向下流側端部の軸受角度ω２との差の絶対値が９０°以下となるような長さである。   The length 1 of the narrow groove 3 is set to a length at which the reduction rate of the minimum oil film thickness due to the narrow groove 3 is 20% or less. The reduction rate of the minimum oil film thickness is a value obtained by subtracting, from 100%, the ratio (%) of the minimum oil film thickness of the slide bearing 21 provided with the fine groove 3 to the minimum oil film thickness of the slide bearing provided with no fine groove. It is. The length at which the reduction rate of the minimum oil film thickness is 20% or less is the minimum oil film thickness required for the sliding bearing 21 to perform safe lubrication. The length at which the reduction rate of the minimum oil film thickness is 20% or less is such that the absolute value of the difference between the bearing angle ω1 at the upstream end in the rotation direction and the bearing angle ω2 at the downstream end in the rotation direction is 90 ° or less. It is such a length.

細溝３の幅は、図４（ｂ）に示すように、ｗとなるように形成されている。
また、細溝３の底面から当接面までの高さｄは、すべり軸受２１の外周面から当接面までの高さＤよりも短くなるように形成されている。
また、細溝３の軸方向外側面を形成する周縁部２１ａは、細溝３の底面からの高さｈが、細溝３の底面から当接面までの高さｄよりも低くなるように形成されている。すなわち、軸方向外側の周縁部２１ａが周囲のクランクシャフト１１との当接面よりも一段低くなるように形成されている。 As shown in FIG. 4B, the narrow groove 3 has a width w.
The height d from the bottom surface of the narrow groove 3 to the contact surface is formed to be shorter than the height D from the outer peripheral surface of the slide bearing 21 to the contact surface.
Further, the peripheral edge portion 21a that forms the axially outer side surface of the narrow groove 3 has a height h from the bottom surface of the narrow groove 3 that is lower than a height d from the bottom surface of the narrow groove 3 to the contact surface. Is formed. In other words, the outer peripheral edge 21a on the outer side in the axial direction is formed to be one step lower than the contact surface with the surrounding crankshaft 11.

周縁部２１ａが周囲のクランクシャフト１１との当接面よりも一段低くなるように形成されていることにより、クランクシャフト１１が傾いて軸方向片側端部にのみ接触する状態（片当りする状態）となったときに、周縁部２１ａとクランクシャフト１１との接触機会を減らすことができるため、周縁部２１ａの損傷を防止することができる。   The peripheral edge portion 21a is formed so as to be one step lower than the contact surface with the surrounding crankshaft 11, so that the crankshaft 11 is tilted and is in contact with only one end portion in the axial direction (a state where it strikes one side) When it becomes, since the contact opportunity with the peripheral part 21a and the crankshaft 11 can be reduced, damage to the peripheral part 21a can be prevented.

また、周縁部２１ａが周囲の当接面よりも一段低くなるように形成されていることにより、すべり軸受２１の軸方向端部における隙間が広がり、吸い戻し油量が増えてトータルの流出油量が低減される。   Further, since the peripheral edge portion 21a is formed so as to be one step lower than the surrounding contact surface, the gap at the axial end portion of the slide bearing 21 is widened, and the amount of sucked-back oil increases and the total amount of oil spilled. Is reduced.

１ すべり軸受
２ 半割部材
２ａ 周縁部
３ 細溝
１１ クランクシャフト DESCRIPTION OF SYMBOLS 1 Slide bearing 2 Half member 2a Peripheral part 3 Narrow groove 11 Crankshaft

Claims (3)

円筒状に形成したすべり軸受であって、
前記すべり軸受の下部の軸方向端部に円周方向を長手方向とする細溝を設け、
前記細溝は、回転方向上流側端部を前記すべり軸受の最下点よりも回転方向上流側に設け、回転方向下流側端部を前記すべり軸受の最下点よりも回転方向下流側に設けた、
ことを特徴とするすべり軸受。 A plain bearing formed in a cylindrical shape,
A narrow groove with the circumferential direction as the longitudinal direction is provided at the axial end of the lower part of the slide bearing,
The narrow groove has an upstream end in the rotational direction provided upstream in the rotational direction from the lowest point of the slide bearing, and a downstream end in the rotational direction provided downstream in the rotational direction from the lowest point of the slide bearing. The
A plain bearing characterized by that. 前記細溝の長さは、前記細溝による最小油膜厚さの減少率が２０％以下となる長さに設定した、
ことを特徴とする請求項１に記載のすべり軸受。 The length of the narrow groove was set to a length at which the reduction rate of the minimum oil film thickness due to the narrow groove was 20% or less,
The plain bearing according to claim 1, wherein: 前記細溝の軸方向外側に周縁部を形成し、前記周縁部の前記細溝底面からの高さは０ｍｍよりも高く、前記すべり軸受の軸との当接面よりも低くなるように形成した、
ことを特徴とする請求項１から２のいずれか一項に記載のすべり軸受。 A peripheral edge is formed on the axially outer side of the narrow groove, and the height of the peripheral edge from the bottom surface of the narrow groove is higher than 0 mm and lower than the contact surface with the shaft of the slide bearing. ,
The plain bearing according to any one of claims 1 to 2, wherein the sliding bearing is provided.
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JP2007285456A (en) * 2006-04-18 2007-11-01 Toyota Motor Corp Bearing structure
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JP2013242028A (en) * 2012-05-23 2013-12-05 Daido Metal Co Ltd Half bearing and sliding bearing
JP2014163432A (en) * 2013-02-22 2014-09-08 Taiho Kogyo Co Ltd Slide bearing
JP2014224601A (en) * 2013-04-26 2014-12-04 大豊工業株式会社 Slide bearing
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61573Y2 (en) * 1979-11-06 1986-01-10
JP2003532036A (en) * 2000-05-03 2003-10-28 デーナ、コーポレイション bearing
JP2002188624A (en) * 2000-12-25 2002-07-05 Daido Metal Co Ltd Split bearing
JP2005249024A (en) * 2004-03-03 2005-09-15 Daido Metal Co Ltd Slide bearing
JP2005256966A (en) * 2004-03-12 2005-09-22 Daido Metal Co Ltd Sliding bearing
JP2007285456A (en) * 2006-04-18 2007-11-01 Toyota Motor Corp Bearing structure
JP2007292015A (en) * 2006-04-27 2007-11-08 Toyota Motor Corp Lubrication structure
JP2013242028A (en) * 2012-05-23 2013-12-05 Daido Metal Co Ltd Half bearing and sliding bearing
JP2014163432A (en) * 2013-02-22 2014-09-08 Taiho Kogyo Co Ltd Slide bearing
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