JP2019031981A - Slide bearing - Google Patents

Slide bearing Download PDF

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Publication number
JP2019031981A
JP2019031981A JP2015246780A JP2015246780A JP2019031981A JP 2019031981 A JP2019031981 A JP 2019031981A JP 2015246780 A JP2015246780 A JP 2015246780A JP 2015246780 A JP2015246780 A JP 2015246780A JP 2019031981 A JP2019031981 A JP 2019031981A
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Prior art keywords
narrow groove
peripheral edge
slide bearing
height
bearing
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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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Priority to JP2015246780A priority Critical patent/JP2019031981A/en
Priority to PCT/JP2016/087534 priority patent/WO2017104795A1/en
Publication of JP2019031981A publication Critical patent/JP2019031981A/en
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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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

To provide a slide bearing capable of obtaining a friction reduction effect and capable of reducing a total oil outflow amount.SOLUTION: A slide bearing 1 is configured such that halved members 2, 2 are arranged vertically, wherein the halved member are formed by dividing a cylinder in parallel with an axis direction. At an axial end part of the lower halved member 2, a fine groove 3 is provided in a circumferential direction. A peripheral edge part 2a is formed on an axial outside of the fine groove 3. A height h of the peripheral edge part 2a from a bottom of the fine groove 3 is not less than 0.05 mm, and is lower than a contact surface of the slide bearing 1 with a crank shaft 11.SELECTED DRAWING: Figure 2

Description

本発明は、すべり軸受の技術に関し、円筒を軸方向と平行に二分割した半割部材を上下に配置したすべり軸受の技術に関する。   The present invention relates to a slide bearing technique, and more particularly to a slide bearing technique in which a half member in which a cylinder is divided into two in parallel with an axial direction is vertically arranged.

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であって、円筒形状を二分割した二つの部材を合わせる半割れ構造のすべり軸受が公知となっているが、冷間時に油の粘度が高いためフリクションが大きいという課題がある。そこで、前記軸受の軸方向両端部に逃げ部分（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 and having a half-crack structure in which two members divided into two cylindrical shapes are combined is known, but the viscosity of oil is high when cold. Therefore, there is a problem that friction is large. Thus, a bearing in which relief portions (narrow grooves) are formed at both axial end portions of the bearing is known (see, for example, Patent Document 1).

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

しかし、従来の細溝を形成した軸受では、油の引込み量増加と軸方向両端部からの油の漏れ量抑制を両立することができず、更なるフリクション低減効果が期待できなかった。   However, in a conventional bearing having a narrow groove, it is impossible to achieve both an increase in the amount of oil drawn and a suppression of the amount of oil leakage from both ends in the axial direction, and a further effect of reducing friction cannot be expected.

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、トータル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 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、円筒を軸方向と平行に二分割した半割部材を上下に配置したすべり軸受であって、前記下側の半割部材の軸方向端部に円周方向に細溝を設け、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を０．０５ｍｍ以上であって、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。   That is, according to the first aspect of the present invention, there is provided a plain bearing in which a half member obtained by dividing a cylinder into two in parallel to the axial direction is arranged vertically, and is narrowed in a circumferential direction at an axial end portion of the lower half member. A groove is provided, 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 0.05 mm or more, from the contact surface with the shaft of the slide bearing Also, it is formed so as to be low.

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、トータルの流出油量を抑えることができる。また、周縁部をすべり軸受の軸との当接面よりも低くすることで吸い戻し油量を増加させつつ、周縁部の高さが低すぎてサイドフロー（軸受から外部への流出油量）が増加するのを防止することでトータルの流出油量が低減される。したがって、軸受内面より漏れた油の再循環を促進し、冷間時油膜を早期昇温させ、フリクションを低減することができる。   That is, by providing a narrow groove that does not hinder the generation of oil film pressure, the friction reduction effect can be obtained while reducing the sliding area, and the total amount of oil spilled can be suppressed. In addition, by reducing the peripheral part lower than the contact surface with the shaft of the slide bearing, the suction oil amount is increased, and the peripheral part height is too low to cause side flow (the amount of oil flowing out from the bearing). By preventing the oil from increasing, the total amount of oil spilled is reduced. Therefore, it is possible to promote recirculation of oil leaked from the inner surface of the bearing, to quickly raise the temperature of the oil film during cold, and to reduce friction.

本発明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 embodiment of this invention. （ａ）本発明の第一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−Ａ線断面図（ｃ）同じくＢ−Ｂ線断面図。(A) Top view which shows the half member which comprises the slide bearing which concerns on 1st embodiment of this invention (b) Similarly AA sectional view (c) Similarly BB sectional drawing. 周縁部の細溝底面からの高さと、比較例に対するトータルの流出油量の割合との関係を示すグラフ図。The graph which shows the relationship between the height from the narrow groove bottom face of a peripheral part, and the ratio of the total amount of spilled oil with respect to a comparative example.

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、図面の上下を上下方向、図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, and the vertical direction in the drawing is the vertical direction, and the front direction and the back direction in the drawing are axial directions (front-rear direction).

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。   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.

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、クランクシャフト１１の回転方向下流側端部３ａ（軸受角度ωがω０）から軸受角度ωが正となる方向（反時計回り方向）に向けて円周方向に設けられる。なお、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。 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 in the circumferential direction from the downstream end 3a (the bearing angle ω is ω0) in the rotation direction of the crankshaft 11 toward the direction in which the bearing angle ω is positive (counterclockwise direction). It is done. 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の回転方向下流側端部３ａは、クランクシャフト１１の回転方向下流側合わせ面に近接しており、回転方向下流側端部３ａと回転方向下流側合わせ面とは連通することなく設けられている。
細溝３の回転方向下流側端部３ｂは、軸受角度ωがω１となる位置に設けられている。
細溝３の長さｌは、回転方向下流側端部３ａから回転方向上流側端部３ｂまでの長さに形成したものである。
細溝３の軸方向の幅は、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の底面からすべり軸受の軸との当接面までの高さ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。ここで、半割部材２の外周面から当接面までの高さＤとは、半割部材２の肉厚であり、本実施形態においては、Ｄは１〜１０ｍｍである。 The rotation direction downstream end 3a of the narrow groove 3 is close to the rotation direction downstream mating surface of the crankshaft 11, and the rotation direction downstream end 3a and the rotation direction downstream mating surface are not communicated with each other. It has been.
The downstream end 3b in the rotation direction of the narrow groove 3 is provided at a position where the bearing angle ω is ω1.
The length 1 of the narrow groove 3 is a length from the downstream end 3a in the rotational direction to the upstream end 3b in the rotational direction.
The width of the narrow groove 3 in the axial direction is formed to be w as shown in FIG.
Further, the height d from the bottom surface of the narrow groove 3 to the contact surface with the shaft of the slide bearing is formed to be shorter than the height D from the outer peripheral surface of the half member 2 to the contact surface. . Here, the height D from the outer peripheral surface of the half member 2 to the contact surface is the thickness of the half member 2, and in the present embodiment, D is 1 to 10 mm.

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の底面からすべり軸受の軸との当接面までの高さｄよりも低くなるように形成した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。
また、細溝３の底面からの高さｈは０．０５ｍｍ以上となるように形成している。 Further, the peripheral edge portion 2a forming the axially outer surface of the narrow groove 3 has a height h from the bottom surface of the narrow groove 3 that is a height d from the bottom surface of the narrow groove 3 to the contact surface with the shaft of the slide bearing. It is formed to be lower than that formed to be lower. 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.
Further, the height h from the bottom surface of the narrow groove 3 is formed to be 0.05 mm or more.

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。また、周縁部２ａの一段低くなった部分の長さは、細溝３の長さｌよりも短くなるように形成されている。   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. Further, the length of the lower part of the peripheral edge 2 a is formed to be shorter than the length 1 of the narrow groove 3.

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.

図３は、周縁部の細溝底面からの高さと、比較例に対するトータルの流出油量の割合との関係を示すグラフである。最も左の点は比較例である細溝を設けない場合のすべり軸受のトータルの流出油量であり、本実施形態に係る細溝３及び周縁部２ａを設けたすべり軸受１のトータルの流出油量の比較例に対する割合を示したものである。   FIG. 3 is a graph showing the relationship between the height of the peripheral edge from the bottom surface of the narrow groove and the ratio of the total amount of oil spilled with respect to the comparative example. The leftmost point is the total spilled oil amount of the sliding bearing when no narrow groove is provided as a comparative example, and the total spilled oil of the sliding bearing 1 provided with the narrow groove 3 and the peripheral edge 2a according to this embodiment. The ratio with respect to the comparative example of quantity is shown.

図３の右方向に向かうにしたがって、周縁部２ａの細溝３の底面からの高さｈが大きくなる。ここで、周縁部２ａの細溝３の底面からの高さｈを０とした場合には、比較例に対するトータルの流出油量の割合が１００％を超える。言い換えれば、周縁部２ａの細溝３の底面からの高さｈを０とした場合には、細溝を設けない場合に比べて、トータルの流出油量が多くなってしまうものである。   The height h from the bottom surface of the narrow groove 3 of the peripheral edge portion 2a increases toward the right in FIG. Here, when the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is set to 0, the ratio of the total amount of oil spilled to the comparative example exceeds 100%. In other words, when the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is set to 0, the total amount of oil spilled is larger than when no narrow groove is provided.

これに対して、周縁部２ａの細溝３の底面からの高さｈを０．０５ｍｍとした場合には、比較例に対するトータルの流出油量の割合が１００％よりも小さくなる。
また、周縁部２ａの細溝３の底面からの高さｈを０．０５ｍｍよりも大きくした場合には、周縁部２ａの細溝３の底面からの高さｈを０．０５ｍｍとした場合と比較すると大きくなるが、比較例に対するトータルの流出油量の割合は１００％よりも小さくなる。 On the other hand, when the height h from the bottom surface of the narrow groove 3 of the peripheral edge 2a is 0.05 mm, the ratio of the total amount of oil spilled to the comparative example is less than 100%.
Further, when the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is larger than 0.05 mm, the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is 0.05 mm. Although it becomes large when compared, the ratio of the total amount of oil spilled to the comparative example becomes smaller than 100%.

また、周縁部２ａの細溝３の底面からの高さｈはすべり軸受１のクランクシャフト１１との当接面よりも小さくするように構成している。周縁部２ａの細溝３の底面からの高さｈが当接面よりも高くなると、摺動抵抗が増加してしまうため、摺動性能が低下する。そこで、周縁部２ａの細溝３の底面からの高さｈはすべり軸受１のクランクシャフト１１との当接面よりも小さくするように構成している。   Further, the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is configured to be smaller than the contact surface with the crankshaft 11 of the slide bearing 1. When the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is higher than the contact surface, the sliding resistance increases, and the sliding performance is degraded. Therefore, the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 is configured to be smaller than the contact surface of the slide bearing 1 with the crankshaft 11.

このように、周縁部２ａの細溝３の底面からの高さｈを０．０５ｍｍ以上であってすべり軸受１のクランクシャフト１１との当接面よりも小さくなるように構成することで、例えば冷間始動時において軸受内面より漏れた油の再循環を促進し、冷間時油膜を早期昇温させ、フリクション低減効果を得ることができ、トータルの流出油量を抑えることができる。   In this way, by configuring the height h of the peripheral edge 2a from the bottom surface of the narrow groove 3 to be 0.05 mm or more and smaller than the contact surface with the crankshaft 11 of the slide bearing 1, for example, It is possible to promote recirculation of oil leaked from the inner surface of the bearing at the time of cold start, to quickly raise the temperature of the oil film during cold, to obtain a friction reduction effect, and to suppress the total amount of oil spilled.

以上のように、すべり軸受１は、円筒を軸方向と平行に二分割した半割部材２・２を上下に配置したすべり軸受１であって、下側の半割部材２の軸方向端部に円周方向に細溝３を設け、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を０．０５ｍｍ以上であって、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、例えば冷間始動時においてフリクション低減効果を得ることができ、トータルの流出油量を抑えることができる。 As described above, the sliding bearing 1 is the sliding bearing 1 in which the half members 2 and 2 obtained by dividing the cylinder into two in parallel with the axial direction are arranged vertically, and the axial end portion of the lower half member 2 A narrow groove 3 is provided in the circumferential direction, a peripheral edge 2a is formed on the outer side in the axial direction of the narrow groove 3, and a height h of the peripheral edge 2a from the bottom surface of the fine groove 3 is 0.05 mm or more. It is formed so as to be lower than the contact surface with one crankshaft 11.
With this configuration, for example, a friction reduction effect can be obtained during cold start, and the total amount of oil spilled can be suppressed.

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（軸） DESCRIPTION OF SYMBOLS 1 Slide bearing 2 Half member 2a Peripheral part 3 Narrow groove 11 Crankshaft (shaft)

Claims (1)

円筒を軸方向と平行に二分割した半割部材を上下に配置したすべり軸受であって、前記下側の半割部材の軸方向端部に円周方向に細溝を設け、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を０．０５ｍｍ以上であって、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すべり軸受。   A slide bearing in which a halved member obtained by dividing a cylinder into two in parallel to the axial direction is arranged vertically, and a narrow groove is provided in a circumferential direction at an axial end of the lower halved member, A peripheral edge is formed on the outer side in the axial direction, and the height of the peripheral edge from the bottom surface of the narrow groove is 0.05 mm or more and is lower than the contact surface with the shaft of the plain bearing. A plain bearing characterized by
JP2015246780A 2015-12-17 2015-12-17 Slide bearing Pending JP2019031981A (en)

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JP2015246780A JP2019031981A (en) 2015-12-17 2015-12-17 Slide bearing
PCT/JP2016/087534 WO2017104795A1 (en) 2015-12-17 2016-12-16 Slide bearing

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Publication number Priority date Publication date Assignee Title
JP2019211001A (en) * 2018-06-04 2019-12-12 大豊工業株式会社 Slide bearing

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014224601A (en) * 2013-04-26 2014-12-04 大豊工業株式会社 Slide bearing
JP2015137709A (en) * 2014-01-22 2015-07-30 大豊工業株式会社 slide bearing
JP2015197215A (en) * 2014-04-03 2015-11-09 大豊工業株式会社 slide bearing

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014224601A (en) * 2013-04-26 2014-12-04 大豊工業株式会社 Slide bearing
JP2015137709A (en) * 2014-01-22 2015-07-30 大豊工業株式会社 slide bearing
JP2015197215A (en) * 2014-04-03 2015-11-09 大豊工業株式会社 slide bearing

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