JP2007321860A - Low-friction sliding member - Google Patents

Low-friction sliding member Download PDF

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JP2007321860A
JP2007321860A JP2006152381A JP2006152381A JP2007321860A JP 2007321860 A JP2007321860 A JP 2007321860A JP 2006152381 A JP2006152381 A JP 2006152381A JP 2006152381 A JP2006152381 A JP 2006152381A JP 2007321860 A JP2007321860 A JP 2007321860A
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fine
sliding member
sliding
recess
fine recess
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Yosuke Hizuka
洋輔 肥塚
Toshikazu Nanbu
俊和 南部
Yoshiteru Yasuda
芳輝 保田
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

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  • Pistons, Piston Rings, And Cylinders (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide low-friction sliding members such as a piston and a cylinder for an internal combustion engine, which relatively slide under the existence of lubricating oil while less producing friction and wear between the sliding faces. <P>SOLUTION: The low friction sliding members for the internal combustion engine, which relatively slide under the existence of lubricating oil, have a number of finely recessed portions formed in the sliding faces on at least one side. The finely recessed portions consist of a number of first finely recessed portions, and second finely recessed portions formed therebetween in the sliding faces with their widths and depths smaller than those of the first finely recessed portions in the sliding direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、潤滑油の存在下で相対的に摺動する低摩擦摺動部材に関する。   The present invention relates to a low friction sliding member that slides relatively in the presence of lubricating oil.

例えば、ピストンおよびシリンダは、一般的に金属でできているため、高速で摺動することによる摺動面の摩耗や焼付きが問題となる。このような摩耗などを防止するには、摺動面相互間に粘性流体を介在させる方法があるが、摩擦などの低減は、十分でない。   For example, since pistons and cylinders are generally made of metal, there is a problem of wear and seizure of the sliding surface due to sliding at high speed. In order to prevent such wear and the like, there is a method of interposing a viscous fluid between the sliding surfaces, but reduction of friction or the like is not sufficient.

更に摩擦などを低減するために、従来から、摺動面に凹凸面などを形成する方法が行われている。例えば、下記特許文献１では、潤滑油を介して互いに摺動する摺動部材において、潤滑油の油膜厚さを保持するよう、摺動部材の摺動面間の隙間に対する潤滑油の流入量と流出量がバランスするときの摺動面間の最接近距離を、摺動面に形成する凹凸部の最大高さよりも大きくする手段が開示されている。これにより、潤滑油の油膜厚さが確保され、摩擦が低減する。   In order to further reduce friction and the like, conventionally, a method of forming an uneven surface on a sliding surface has been performed. For example, in the following Patent Document 1, in the sliding members that slide with each other through the lubricating oil, the inflow amount of the lubricating oil with respect to the gap between the sliding surfaces of the sliding member to maintain the oil film thickness of the lubricating oil Means is disclosed in which the closest distance between the sliding surfaces when the amount of outflow is balanced is made larger than the maximum height of the concavo-convex portion formed on the sliding surface. Thereby, the oil film thickness of lubricating oil is ensured and friction reduces.

しかし、上記のような従来の摺動部材においても、摩擦の低減を実現しうるものの、更なる摩擦の低減が要望されている。
特開２００２−２１３６１２号公報（要約、図１参照） However, even in the conventional sliding member as described above, although it is possible to reduce friction, further reduction of friction is desired.
Japanese Patent Laid-Open No. 2002-213612 (Summary, see FIG. 1)

本発明は、潤滑油の存在下で相対的に摺動する内燃機関用の低摩擦摺動部材における、摺動面間に生じる摩擦及び摩耗を低減し得る低摩擦摺動部材を提供することを目的とする。   The present invention provides a low friction sliding member that can reduce friction and wear generated between sliding surfaces in a low friction sliding member for an internal combustion engine that slides relatively in the presence of lubricating oil. Objective.

本発明は、潤滑油の存在下で相対的に摺動する摺動部材の少なくとも一方の摺動部材の摺動面に多数の微細凹部を形成した低摩擦摺動部材であって、前記微細凹部は、多数の第１微細凹部間に、摺動方向の幅及び深さが前記第１微細凹部より小さな値の第２微細凹部を形成したことを特徴とする低摩擦摺動部材である。   The present invention is a low friction sliding member in which a plurality of fine concave portions are formed on a sliding surface of at least one sliding member of a sliding member that slides relatively in the presence of lubricating oil, the fine concave portion Is a low-friction sliding member characterized in that a second fine recess having a smaller width and depth in the sliding direction than the first fine recess is formed between a number of first fine recesses.

本発明の低摩擦摺動部材によれば、潤滑油の存在下で相対的に摺動する摺動部材の摺動面に多数の第１微細凹部を形成し、この第１微細凹部間に第２の微細凹部を形成したので、摺動面上での保油性が向上し、摺動面間に生じる摩擦を低減することができる。また、第２の微細凹部の摺動方向の幅及び深さを第１微細凹部より小さな値とすることにより負荷容量の低下による直接接触を発生させることなく、摩擦を低減することが可能となる。なお、本明細書においては、「微細凹部」とは、ミクロンオーダーの極めて小さな凹部をいう。   According to the low friction sliding member of the present invention, a large number of first fine recesses are formed on the sliding surface of the sliding member that slides relatively in the presence of lubricating oil, and the first fine recesses are formed between the first fine recesses. Since the two minute recesses are formed, the oil retaining property on the sliding surface is improved, and the friction generated between the sliding surfaces can be reduced. Further, by making the width and depth of the second fine recess in the sliding direction smaller than those of the first fine recess, it becomes possible to reduce friction without causing direct contact due to a decrease in load capacity. . In the present specification, the “fine concave portion” means an extremely small concave portion on the order of microns.

以下、本発明に係る低摩擦摺動面材について、詳細に説明する。   Hereinafter, the low friction sliding face material according to the present invention will be described in detail.

図１は本発明の実施形態に係る低摩擦摺動部材が使用されるエンジンの要部を示す概略断面図、図２は同低摩擦摺動部材の要部を示す概略斜視図、図３は同低摩擦摺動部材の凹部を示す平面図、図４は図３の４−４線に沿う端面図である。   1 is a schematic cross-sectional view showing a main part of an engine in which a low friction sliding member according to an embodiment of the present invention is used, FIG. 2 is a schematic perspective view showing the main part of the low friction sliding member, and FIG. FIG. 4 is a plan view showing a concave portion of the low friction sliding member, and FIG. 4 is an end view taken along line 4-4 of FIG.

本実施形態に係る低摩擦摺動部材は、例えば、図１に示すようなエンジンのピストン１とシリンダ２、クランクシャフト３とメタル軸受４などのように、潤滑油の存在下で摺動する部分の摩擦を大幅に低減するために使用される。   The low-friction sliding member according to the present embodiment is a portion that slides in the presence of lubricating oil, such as an engine piston 1 and cylinder 2, a crankshaft 3 and a metal bearing 4 as shown in FIG. Used to greatly reduce friction.

潤滑油の存在下で、相互に接して摺動する一対の摺動部材においては、一方の摺動部材に形成された摺動方向に平行な方向の凸部の長さが、他方の摺動部材に形成された摺動方向に平行な方向の凹部の長さよりも大きいと、摺動の際、潤滑油を凹部に閉じ込めることができ、摺動部材相互間に一定の油膜厚さを保持でき、低摩擦を実現することができる。しかし、凹部が大きすぎたり深すぎると、負荷容量が低下し直接接触が生じやすくなる。本発明者らは、このような知見に基づき本発明を完成させたものである。つまり、本発明は、負荷容量に与える影響が小さい状態で、潤滑油の保油性を向上させるために、摺動方向または潤滑油の流れ方向に対して小さく、深さが浅い凹部を形成したもので、シリンダ２のボアやメタル軸受４の内周面のような円弧状内面を有する部品側に適用して好適なものである。   In a pair of sliding members that slide in contact with each other in the presence of lubricating oil, the length of the convex portion formed in one sliding member in a direction parallel to the sliding direction is the other sliding member. If it is longer than the length of the recess in the direction parallel to the sliding direction formed on the member, the lubricating oil can be trapped in the recess during sliding, and a constant oil film thickness can be maintained between the sliding members. Low friction can be realized. However, if the recess is too large or too deep, the load capacity decreases and direct contact tends to occur. The present inventors have completed the present invention based on such findings. That is, in the present invention, in order to improve the oil retaining property of the lubricating oil in a state where the influence on the load capacity is small, a concave portion having a small depth and a shallow depth is formed in the sliding direction or the lubricating oil flow direction. Thus, the present invention is suitable for application to a component side having an arcuate inner surface such as the bore of the cylinder 2 or the inner peripheral surface of the metal bearing 4.

さらに詳述する。本実施形態の低摩擦摺動部材は、潤滑油の存在下で、図２に示す矢印の方向に相対的に摺動する第１の摺動部材１０と第２の摺動部材１１とからなり、両摺動部材１０，１１の摺動面１０ａ，１１ａには、大きな多数の第１微細凹部１２と、これら第１微細凹部１２間に形成され、第１微細凹部１２より小さな多数の第２微細凹部１３と、が形成されている。   Further details will be described. The low-friction sliding member of the present embodiment includes a first sliding member 10 and a second sliding member 11 that slide relatively in the direction of the arrow shown in FIG. 2 in the presence of lubricating oil. The sliding surfaces 10 a, 11 a of both sliding members 10, 11 are formed with a large number of first fine recesses 12 and a plurality of second fine recesses 12 formed between these first fine recesses 12 and smaller than the first fine recesses 12. A fine recess 13 is formed.

第１微細凹部１２は、図２〜４に示すように、摺動方向と直交する方向に扁平な凹部で、幅Ｘ１及び深さｈ１の値を有し、第２微細凹部１３は、第１微細凹部１２間の摺動面１０ａ，１１ａに形成され、摺動方向において、第１微細凹部１２の幅Ｘ１及び深さｈ１より小さな値である幅Ｘ２及び深さｈ２を有している。このように第１微細凹部１２の間の平坦部に、油溜りとなる第２微細凹部１３が存在すると、保油性が向上し摩擦の低減と，耐焼付き性の向上を行うことができる。   2-4, the 1st fine recessed part 12 is a flat part flat in the direction orthogonal to a sliding direction, has the value of width X1 and depth h1, and the 2nd fine recessed part 13 is 1st. It is formed on the sliding surfaces 10a and 11a between the fine concave portions 12, and has a width X2 and a depth h2 which are smaller than the width X1 and the depth h1 of the first fine concave portion 12 in the sliding direction. Thus, when the 2nd fine recessed part 13 used as an oil reservoir exists in the flat part between the 1st fine recessed parts 12, oil retention property can improve, a friction can be reduced, and seizure resistance can be improved.

しかし、保油性の向上と摩擦の低減を図るには、第１微細凹部１２や第２微細凹部１３の大きさが問題で、この大きさは、摺動方向又は油の流れの方向に対して小さく、深さも浅いものとすべきである。本実施形態では、第２微細凹部１３の摺動方向の幅Ｘ２と第１微細凹部１２の摺動方向の幅Ｘ１との比（Ｘ２／Ｘ１）を、１／１５〜２／３とし、第２微細凹部１３の深さｈ２と第１微細凹部１２の深さｈ１との比（ｈ２／ｈ１）を、１／１０〜１／２としている。   However, in order to improve oil retention and reduce friction, the size of the first fine concave portion 12 and the second fine concave portion 13 is a problem, and this size depends on the sliding direction or the oil flow direction. It should be small and shallow. In the present embodiment, the ratio (X2 / X1) of the width X2 in the sliding direction of the second fine recess 13 to the width X1 in the sliding direction of the first fine recess 12 is 1/15 to 2/3, The ratio (h2 / h1) between the depth h2 of the second fine recess 13 and the depth h1 of the first fine recess 12 is set to 1/10 to 1/2.

第２微細凹部１３が大きすぎると、面積率が大きくなりすぎるため、負荷容量が低下して直接接触が生じやすくなり、深さが深すぎる場合も同様である。したがって、負荷容量に与える影響が小さい状態で、表面の油の保油性を向上させるために、比Ｘ２／Ｘ１やｈ２／ｈ１は、上記の値とすることが好ましいことが実験により確認されている。   If the second fine recess 13 is too large, the area ratio becomes too large, so that the load capacity decreases and direct contact is likely to occur, and the same is true when the depth is too deep. Therefore, it has been confirmed by experiments that the ratios X2 / X1 and h2 / h1 are preferably set to the above values in order to improve the oil retaining property of the surface oil in a state where the influence on the load capacity is small. .

負荷容量に与える影響や表面の保油性は、このような比のみでなく、第１微細凹部１２と第２微細凹部１３の摺動部材の摺動面１０ａ，１１ａ全体に対する比率、つまり、面積率(％)、深さ、個々の大きさなども重要な要素なため、これらについても明らかにする。   The influence on the load capacity and the oil retaining property of the surface are not only such a ratio but also the ratio of the sliding members of the first fine recess 12 and the second fine recess 13 to the entire sliding surfaces 10a, 11a, that is, the area ratio. (%), Depth, and individual size are also important factors.

第１微細凹部１２の面積率(％)は、０．３％〜１０％であることが好ましい。０．３％以下では、油膜を厚くする効果が十分に得られず、また，１０％以上では負荷容量が低下し直接接触が発生しやすくなり、摩擦低減効果を十分に得ることができない。このような面積率は、例えば、表面観察写真を画像処理することにより算出することができる。   The area ratio (%) of the first fine recess 12 is preferably 0.3% to 10%. If it is 0.3% or less, the effect of thickening the oil film cannot be obtained sufficiently, and if it is 10% or more, the load capacity decreases and direct contact tends to occur, and the friction reduction effect cannot be sufficiently obtained. Such an area ratio can be calculated, for example, by subjecting a surface observation photograph to image processing.

第１微細凹部１２の深さに関しては、最大深さが０．５μm〜２０μmであることが好ましい。０．５μm以下では、動圧効果が発揮されず、油閉じ込め効果が十分でないため、フリクション低現効果が十分に発現されない。２０μmを超えると負荷容量の低下を招き、金属接触が発生しやすくなり、十分なフリクション低減が発現できない。このような凹部の深さの測定は、三次元表面構造解析顕微鏡ＮｅｗＶｉｅｗ５０３２（ザイゴ株式会社製）を用い、非接触三次元白色光位相変調干渉方式などにより測定する。   Regarding the depth of the first fine recess 12, the maximum depth is preferably 0.5 μm to 20 μm. If it is 0.5 μm or less, the dynamic pressure effect is not exhibited and the oil confinement effect is not sufficient, so that the friction reduction effect is not sufficiently exhibited. If it exceeds 20 μm, the load capacity is reduced, metal contact is likely to occur, and sufficient friction reduction cannot be realized. The depth of the concave portion is measured by a non-contact three-dimensional white light phase modulation interference method using a three-dimensional surface structure analysis microscope NewView 5032 (manufactured by Zygo Corporation).

第１微細凹部１２の大きさは、短辺の長さが５０μm〜１５０μmであり、長辺の長さを短辺の２倍以上１０倍以下であることが望ましい。微細な凹部の短辺が５０μm以下の場合、油が微細な凹部へ十分に流入せず動圧の効果が十分に得られず、１５０μm以上では負荷容量が低下し金属接触が起こりやすくなる虞がある。したがって、この範囲であれば、第１微細凹部１２は、動圧効果を十分に発揮し、油膜を厚くすることでフリクション低減効果を発現できることになる。   Regarding the size of the first fine recess 12, the length of the short side is preferably 50 μm to 150 μm, and the length of the long side is preferably not less than 2 times and not more than 10 times the short side. If the short side of the fine recess is 50 μm or less, the oil does not sufficiently flow into the fine recess and the effect of dynamic pressure cannot be obtained sufficiently, and if it is 150 μm or more, the load capacity decreases and metal contact may occur easily. is there. Therefore, if it is this range, the 1st fine recessed part 12 will fully exhibit a dynamic pressure effect, and can express the friction reduction effect by thickening an oil film.

一方、第２微細凹部１３の面積率(％)は、０．５％〜２０％であることが好ましい。０．５％以下の場合は、第２微細凹部１３による油溜まりの効果が十分でなくフリクション低減効果が十分発現されず、２０％以上になると負荷容量の低下により，摩擦特性の悪化が生じる。   On the other hand, the area ratio (%) of the second fine recess 13 is preferably 0.5% to 20%. In the case of 0.5% or less, the effect of the oil reservoir by the second fine concave portion 13 is not sufficient, and the friction reducing effect is not sufficiently expressed, and in the case of 20% or more, the load capacity is reduced and the friction characteristics are deteriorated.

第２微細凹部１３の深さは、第１微細凹部１２よりも浅く、最大深さが第１微細凹部１２の最大深さの１／２〜１／１０であることが好ましい。第２微細凹部１３の深さが深すぎる場合、負荷容量の低下を招き、金属接触が発生しやすくなる。また、浅すぎる場合にも油を保持する能力がなくなり、金属接触が発生しやすくなる。   The depth of the second fine recess 13 is shallower than that of the first fine recess 12, and the maximum depth is preferably 1/2 to 1/10 of the maximum depth of the first fine recess 12. When the depth of the 2nd fine recessed part 13 is too deep, the fall of a load capacity will be caused and it will become easy to generate | occur | produce a metal contact. In addition, when it is too shallow, the ability to retain oil is lost, and metal contact tends to occur.

第２微細凹部１３の大きさは、摺動方向に対する幅が第１微細凹部１２の幅より小さく、摺動方向に対する幅が第１微細凹部１２の幅の１／１５〜２／３であることが好ましい。第２微細凹部１３が小さすぎる場合には、油の保持効果がなくなり、金属接触が発生しやすくなる。また、大きすぎる場合には、負荷容量が低下し、金属接触が発生しやすくなる。   The size of the second fine recess 13 is such that the width in the sliding direction is smaller than the width of the first fine recess 12 and the width in the sliding direction is 1/15 to 2/3 of the width of the first fine recess 12. Is preferred. If the second fine recess 13 is too small, the oil retaining effect is lost and metal contact is likely to occur. Moreover, when too large, load capacity will fall and it will become easy to generate | occur | produce a metal contact.

第１微細凹部１２や第２微細凹部１３の面積率(％)×深さ(μｍ)の値の合計は、３０以下であることが好ましい。これら各凹部１２と１３の面積率(％)×深さ(μｍ)の値が３０を超えると，負荷容量の低下と共に凹部に入り込む油の量が多くなるため，油膜が薄くなり，直接接触が発生しやすくなり、十分なフリクション低減が発現できないからである。   The sum of the area ratio (%) × depth (μm) values of the first fine recess 12 and the second fine recess 13 is preferably 30 or less. If the value of the area ratio (%) x depth (μm) of each of these recesses 12 and 13 exceeds 30, the amount of oil that enters the recesses increases as the load capacity decreases, so the oil film becomes thinner and direct contact is reduced. This is because they tend to occur and sufficient friction reduction cannot be realized.

第１微細凹部１２や第２微細凹部１３の形状は、図３では矩形状をしたものであるが、これのみに制限されるものではなく、長方形、楕円、不定形などあらゆる形状が採用されうる。   The shape of the first fine concave portion 12 and the second fine concave portion 13 is a rectangular shape in FIG. 3, but is not limited to this, and any shape such as a rectangle, an ellipse, and an indefinite shape can be adopted. .

特に、第２微細凹部１３の形状は、保油性を向上させる油溜まりの役割として形成するため、それぞれが独立して形成されたものであってもよいが、連続した溝状であってもよい。図５Ａ〜Ｅは第２微細凹部の種々の形状例を示す概略図である。   In particular, since the shape of the second fine recess 13 is formed as a role of an oil reservoir for improving oil retention, each may be formed independently, but may be a continuous groove shape. . 5A to 5E are schematic views illustrating various shape examples of the second fine recess.

第２微細凹部１３の形状に関しては、例えば、図５Ａに示すように、図３に示すものよりさらに多数のものを第１微細凹部１２間の摺動面１１ａに形成したものであってもよく、図５Ｂに示すように、第１微細凹部１２間の摺動面１１ａで連続的に伸延する溝状であってもよい。溝状の第２微細凹部１３の場合、図５Ｃに示すように、第１微細凹部１２と平行に形成してもよい。場合によっては、第２微細凹部１３は、図５Ｄに示すように、ドット状に形成したものであってもよい。ただし、このような形状の第２微細凹部１３であっても、前述の面積率や深さとすべきである。   Regarding the shape of the second fine recess 13, for example, as shown in FIG. 5A, a larger number than that shown in FIG. 3 may be formed on the sliding surface 11 a between the first fine recesses 12. As shown in FIG. 5B, a groove shape that continuously extends on the sliding surface 11 a between the first fine recesses 12 may be used. In the case of the groove-shaped second fine recess 13, it may be formed in parallel with the first fine recess 12 as shown in FIG. 5C. Depending on the case, the 2nd fine recessed part 13 may be formed in dot shape, as shown to FIG. 5D. However, even the second fine concave portion 13 having such a shape should have the above-described area ratio and depth.

さらに、第２微細凹部１３の形状は、図５Ｅに示すように、ランダムに筋状に形成したもの(以下、ランダム溝と称す)であっても油膜を保持する機能が発現できる。   Further, as shown in FIG. 5E, the second fine concave portion 13 can exhibit a function of retaining an oil film even when it is randomly formed in a streak shape (hereinafter referred to as a random groove).

第２微細凹部１３をランダム溝１５とした場合には、第１微細凹部１２間の表面粗さＲｚが、０．０３μｍ≦Ｒｚ≦０．２５μmであることが好ましい。   When the second fine recess 13 is a random groove 15, the surface roughness Rz between the first fine recesses 12 is preferably 0.03 μm ≦ Rz ≦ 0.25 μm.

表面粗さＲｚが０．０３μｍ以下の場合には、表面が平滑なため油の保持効果が不十分になり、表面粗さＲｚが０．２５μm以上の場合には、粗さが大きすぎ、粗さの凸部の増加に起因する直接接触が発生し、十分に摩擦が低減されないことになる。なお、表面粗さＲｚは、例えば、触針式表面形状測定装置ＦｏｒｍＴａｌｙｓｕｒｆ−１２０Ｌ（Ｔａｙｌｏｒ−Ｈｏｂｓｏｎ社製）により測定される。   When the surface roughness Rz is 0.03 μm or less, the oil is not sufficiently retained because the surface is smooth, and when the surface roughness Rz is 0.25 μm or more, the roughness is too large, The direct contact resulting from the increase in the height of the protrusion occurs, and the friction is not sufficiently reduced. The surface roughness Rz is measured by, for example, a stylus type surface shape measuring device FormTalysurf-120L (manufactured by Taylor-Hobson).

また、ランダム溝１５は、表面粗さのゆがみ（Ｒｓｋ；ＪＩＳ Ｂ ０６０１記載)の値が負であることが好ましい。表面粗さのゆがみのＲｓｋ値を負とすれば、粗さ成分の表面から窪んだ部分の分布が増え、保油性に優れたものとなり、好ましい。   Further, the random groove 15 preferably has a negative surface roughness distortion (Rsk; described in JIS B 0601). If the Rsk value of the distortion of the surface roughness is negative, the distribution of the recessed portion from the surface of the roughness component is increased, and the oil retaining property is excellent, which is preferable.

（実施例１）
図６は試験片を往復動させる試験機の要部を示す概略斜視図、図７Ａはピン試験片の平面図、図７Ｂはピン試験片の側面図、図８Ａは平板試験片の大きさを示す平面図、図８Ｂは平板試験片の側面図である。 Example 1
6 is a schematic perspective view showing a main part of a test machine for reciprocating the test piece, FIG. 7A is a plan view of the pin test piece, FIG. 7B is a side view of the pin test piece, and FIG. 8A shows the size of the flat plate test piece. FIG. 8B is a side view of a flat plate test piece.

実験は、図６に示すように、平坦な面に様々な凹形状を形成した平板試験片２０上で、ピン試験片２１に垂直荷重Ｗを掛けた状態で、両矢印方向に往復摺動させることにより行った。平板試験片２０の大きさは、厚さ７ｍｍ、長さ６０ｍｍ、幅４０ｍｍであるが、摺動面は、表面に第１微細凹部１２と第２微細凹部１３を形成した。ピン試験片２１の大きさは、厚さ８ｍｍ、長さ４０ｍｍ、高さ１１．５ｍｍで、先端面は、曲率半径Ｒを有しているが、ＣＶＤ法を用いて、硬質炭素薄膜であるＤＬＣ（ダイヤモンドライクカーボン）をコーティングした。   In the experiment, as shown in FIG. 6, on a flat plate test piece 20 having various concave shapes formed on a flat surface, the pin test piece 21 is slid back and forth in the direction of a double arrow with a vertical load W applied. Was done. The flat test piece 20 has a thickness of 7 mm, a length of 60 mm, and a width of 40 mm. On the sliding surface, the first fine concave portion 12 and the second fine concave portion 13 were formed on the surface. The pin test piece 21 has a thickness of 8 mm, a length of 40 mm, and a height of 11.5 mm. The tip surface has a radius of curvature R, but is a DLC that is a hard carbon thin film using a CVD method. (Diamond like carbon) was coated.

ピン試験片２１に対する垂直荷重Ｗは、２５ｋｇｆ、速度は、６００ｒｐｍ、潤滑油は、５Ｗ３０の油（油温度８０℃）を０．８ｃｃ／ｍｉｎで滴下し、摩擦係数を測定し、後述の比較例１の場合の摩擦係数を「１」とし、これと比較した。   The vertical load W with respect to the pin test piece 21 is 25 kgf, the speed is 600 rpm, and the lubricating oil is 5W30 oil (oil temperature 80 ° C.) dropped at 0.8 cc / min, and the friction coefficient is measured. The friction coefficient in the case of 1 was set to “1” and compared with this.

ここに、比較例１は、研磨加工により平滑な鏡面にした後に、その表面に第１微細凹部１２のみを形成したもので、平坦部の表面粗さは、Ｒｚ＝０．３μｍ、第１微細凹部１２は、矩形状で、大きさが８０μｍ×３２０μｍ、深さが３μｍ、面積率１％とした。   Here, in Comparative Example 1, after making a smooth mirror surface by polishing, only the first fine concave portion 12 is formed on the surface, and the surface roughness of the flat portion is Rz = 0.3 μm, the first fine surface. The recess 12 was rectangular and had a size of 80 μm × 320 μm, a depth of 3 μm, and an area ratio of 1%.

比較例２は、平坦部に第１微細凹部１２を形成せず、平坦部の表面粗さをＲｚ＝３μｍのクロスハッチ目で加工したものである。   In Comparative Example 2, the first fine concave portion 12 is not formed in the flat portion, and the surface roughness of the flat portion is processed with a cross hatch of Rz = 3 μm.

実施例１は、平坦部の表面粗さをＲｚ＝０．３μｍとし、第１微細凹部１２は、矩形状で、大きさが８０μｍ×３２０μｍ、深さが３μｍ、面積率１％とし、さらに第２の微細凹部１３は、クロスハッチ状の溝で、摺動方向の長さＸ２が２０μｍ、深さが１μｍ、面積率１０％とした。   In Example 1, the surface roughness of the flat portion is Rz = 0.3 μm, the first fine recess 12 is rectangular, has a size of 80 μm × 320 μm, a depth of 3 μm, an area ratio of 1%, The second fine recess 13 is a cross-hatched groove having a length X2 in the sliding direction of 20 μm, a depth of 1 μm, and an area ratio of 10%.

図９，１０，１１は、比較例１，２と実施例１の断面曲線を示すグラフであり、縦軸には表面粗さ、横軸に位置を示している。図９と図１１には要部を拡大して示す図を併記しているが、この要部拡大図は、縦軸の表面粗さを１μｍ単位で示し、横軸の位置を２００μｍ単位で示している。この図９〜１１より明らかなように、比較例１の表面は極めて平滑な面であり、比較例２の表面は粗く、実施例１の表面は極めて平滑な面と粗い部分が併存している。   9, 10, and 11 are graphs showing the cross-sectional curves of Comparative Examples 1 and 2 and Example 1, in which the vertical axis indicates the surface roughness and the horizontal axis indicates the position. FIGS. 9 and 11 also show enlarged views of the main part. This enlarged view of the main part shows the surface roughness of the vertical axis in units of 1 μm and the position of the horizontal axis in units of 200 μm. ing. As is apparent from FIGS. 9 to 11, the surface of Comparative Example 1 is a very smooth surface, the surface of Comparative Example 2 is rough, and the surface of Example 1 has both a very smooth surface and a rough portion. .

実施例としては、実施例１の他に実施例２〜７があるが、これら実施例２〜７は、実施例１と第２の微細凹部１３が、下記のように相違している。つまり、実施例２〜７は、実施例１と同様、平坦部の表面粗さをＲｚ＝０．３μｍに加工し、第１微細凹部１２が、矩形状で、大きさが８０μｍ×３２０μｍ、深さが３μｍ、面積率１％のものを形成し、さらに第２の微細凹部１３をクロスハッチ状の溝としているが、実施例２〜７においては、第２の微細凹部１３が、表１にも示しているが、下記の点で相違している。   Examples include Examples 2 to 7 in addition to Example 1. In Examples 2 to 7, Example 1 and second fine recess 13 are different as described below. That is, in Examples 2 to 7, as in Example 1, the surface roughness of the flat portion was processed to Rz = 0.3 μm, the first fine recess 12 was rectangular, the size was 80 μm × 320 μm, and the depth Is formed with a thickness of 3 μm and an area ratio of 1%, and the second fine concave portion 13 is a cross-hatched groove. In Examples 2 to 7, the second fine concave portion 13 is shown in Table 1. This also shows differences in the following points.

実施例２では、第２の微細凹部１３が、摺動方向の長さＸ２が２０μｍ、深さが１μｍ、面積率２５％である。   In Example 2, the second fine recess 13 has a sliding direction length X2 of 20 μm, a depth of 1 μm, and an area ratio of 25%.

実施例３では、第２の微細凹部１３が、摺動方向の長さＸ２が２０μｍ、深さが１μｍ、面積率０．５％である。   In Example 3, the second fine recess 13 has a length X2 in the sliding direction of 20 μm, a depth of 1 μm, and an area ratio of 0.5%.

実施例４では、第２の微細凹部１３が、摺動方向の長さＸ２が２０μｍ、深さが０．２μｍ、面積率１０％である。   In Example 4, the second fine recess 13 has a sliding direction length X2 of 20 μm, a depth of 0.2 μm, and an area ratio of 10%.

実施例５では、第２の微細凹部１３が、摺動方向の長さＸ２が２０μｍ、深さが２μｍ、面積率２０％である。   In Example 5, the second fine recess 13 has a sliding direction length X2 of 20 μm, a depth of 2 μm, and an area ratio of 20%.

実施例６では、第２の微細凹部１３が、摺動方向の長さＸ２が６０μｍ、深さが１μｍ、面積率１０％である。   In Example 6, the second fine recess 13 has a sliding direction length X2 of 60 μm, a depth of 1 μm, and an area ratio of 10%.

実施例７では、第２の微細凹部１３が、摺動方向の長さＸ２が１０μｍ、深さが１μｍ、面積率１０％である。   In Example 7, the second fine recess 13 has a sliding direction length X2 of 10 μm, a depth of 1 μm, and an area ratio of 10%.

実施例８，９は、第１微細凹部１２の平坦部の表面粗さをＲｚ＝０．３μｍに加工し、第１微細凹部１２として、矩形状のもので、大きさが８０μｍ×３２０μｍ、深さが３μｍ、とした点は、前記実施例と同様であるが、第１微細凹部１２の面積率を５％とし、さらに第２の微細凹部１３をクロスハッチ状の溝として形成している。ただし、実施例８は、第２の微細凹部１３の面積率を２０％とし、実施例９は、第２の微細凹部１３の面積率を１０％としている。   In Examples 8 and 9, the surface roughness of the flat portion of the first fine recess 12 is processed to Rz = 0.3 μm, and the first fine recess 12 has a rectangular shape with a size of 80 μm × 320 μm and a depth of 8 μm. However, the area ratio of the first fine recesses 12 is set to 5%, and the second fine recesses 13 are formed as cross-hatched grooves. However, in Example 8, the area ratio of the second fine concave portion 13 is set to 20%, and in Example 9, the area ratio of the second fine concave portion 13 is set to 10%.

これら実施例および比較例における、第１微細凹部１２と第２の微細凹部１３の大きさ、深さ、面積率、深さと面積率の積をまとめるとともに実験結果を示すと、表１のようになる。   In these examples and comparative examples, the size, depth, area ratio, product of depth and area ratio of the first fine recess 12 and the second fine recess 13 are summarized, and the experimental results are shown in Table 1. Become.

表１から明らかなように、研磨加工により鏡面にした表面に、比較的大きな第１微細凹部１２を形成した比較例１や、細かなクロスハッチ目のみを有する比較例２よりも、本発明を適用した実施例の方が、大部分のものにおいて摩擦抵抗が減少していることがわかる。本発明を適用した実施例は、平滑な面に、比較的大きな第１微細凹部１２と、クロスハッチ状の溝などからなる第２の微細凹部１３とを形成したものであるが、第１微細凹部１２自体の油溜りとしての機能に、第１微細凹部１２の間の平坦部に形成した小さな第２微細凹部１３による油溜りとしての機能が加わり、微細凹部全体としての保油性が大幅に向上し、摩擦低減効果が発揮されたものである。特に、第２微細凹部１３が多数あるいは連続的に存在することにより、これが第１微細凹部１２の保油性を、摺動面全体的にわたり補うことになり、摩擦抵抗の低減に大きく寄与することになっている。   As is apparent from Table 1, the present invention is more effective than Comparative Example 1 in which a relatively large first fine recess 12 is formed on a mirror-finished surface and Comparative Example 2 having only fine cross-hatch eyes. It can be seen that in the applied embodiment, the frictional resistance is reduced in most cases. In the embodiment to which the present invention is applied, a relatively large first fine concave portion 12 and a second fine concave portion 13 made of a cross-hatched groove or the like are formed on a smooth surface. The function of the recess 12 itself as an oil reservoir is added to the function of an oil reservoir by the small second micro recess 13 formed in the flat portion between the first micro recesses 12, thereby greatly improving the oil retaining property of the entire micro recess. In addition, the friction reducing effect is exhibited. In particular, the presence or absence of a large number or a plurality of second fine recesses 13 supplements the oil retaining property of the first fine recesses 12 over the entire sliding surface, and contributes greatly to the reduction of frictional resistance. It has become.

このような本発明の低摩擦摺動部材を、潤滑油の存在下で摺動する内燃機関用の摺動部材、例えば、シリンダ、メタル軸受などの、円弧状内面を形成するものに適用すると、第１微細凹部１２や第２微細凹部１３が、保油性を向上させる油溜まりの役割を発揮し、これら凹部に入り込む油の量が多くなり、負荷容量の低下や油膜が薄くなる事態を防止し、金属同士の直接接触が発生せず、摩擦抵抗が低減する好ましい内燃機関になる。   When the low friction sliding member of the present invention is applied to a sliding member for an internal combustion engine that slides in the presence of lubricating oil, for example, a cylinder, a metal bearing, or the like that forms an arc-shaped inner surface, The 1st fine recessed part 12 and the 2nd fine recessed part 13 exhibit the role of the oil sump which improves oil retention, and the amount of the oil which penetrates into these recessed parts increases, and the situation where the load capacity falls and the oil film becomes thin is prevented. In addition, it is a preferable internal combustion engine in which direct contact between metals does not occur and frictional resistance is reduced.

本発明は、上述した実施の形態に限定されるものではなく、特許請求の範囲の範囲内で種々改変することができる。例えば、上述した実施形態では、平坦な低摩擦摺動部材に第１微細凹部１２や第２微細凹部１３を形成したものであるが、これのみでなく、他の種々の形状を有するもの、例えば、ある程度湾曲したものあるいは円弧状の面を有するもの、又は球面のものなどにも適用することもできる。   The present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the claims. For example, in the above-described embodiment, the first micro concave portion 12 and the second micro concave portion 13 are formed on a flat low friction sliding member. However, not only this but also other various shapes, for example, Also, the present invention can be applied to one that is curved to some extent, one that has an arcuate surface, or one that is spherical.

本発明は、潤滑油の存在下で摺動する摺動部材の摺動摩擦を低減した内燃機関用部品、特に、ピストンやシリンダあるいは軸受部材に利用することができる。   INDUSTRIAL APPLICABILITY The present invention can be used for an internal combustion engine component that reduces sliding friction of a sliding member that slides in the presence of lubricating oil, particularly a piston, cylinder, or bearing member.

本発明の実施形態に係る低摩擦摺動部材が使用されるエンジンの要部を示す概略断面図である。It is a schematic sectional drawing which shows the principal part of the engine in which the low friction sliding member which concerns on embodiment of this invention is used. 同低摩擦摺動部材の要部を示す概略斜視図である。It is a schematic perspective view which shows the principal part of the same low friction sliding member. 同低摩擦摺動部材の凹部を示す平面図である。It is a top view which shows the recessed part of the same low friction sliding member. 図３の４−４線に沿う端面図である。FIG. 4 is an end view taken along line 4-4 of FIG. 3. 第２微細凹部の種々の形状例を示す概略図である。It is the schematic which shows the example of various shapes of a 2nd fine recessed part. 往復動試験機の要部を示す概略斜視図である。It is a schematic perspective view which shows the principal part of a reciprocating test machine. Ａはピン試験片の平面図、Ｂはピン試験片の側面図である。A is a plan view of a pin test piece, and B is a side view of the pin test piece. Ａは平板試験片の大きさを示す平面図、Ｂは平板試験片の側面図である。A is a plan view showing the size of a flat test piece, and B is a side view of the flat test piece. 比較例１の断面曲線を示すグラフである。6 is a graph showing a cross-sectional curve of Comparative Example 1. 比較例２の断面曲線を示すグラフである。10 is a graph showing a cross-sectional curve of Comparative Example 2. 実施例１の断面曲線を示すグラフである。3 is a graph showing a cross-sectional curve of Example 1.

符号の説明Explanation of symbols

１０，１１…摺動部材、
１０ａ，１１ａ…摺動面、
１２…第１微細凹部、
１３…第２微細凹部。 10, 11 ... sliding member,
10a, 11a ... sliding surface,
12 ... 1st minute recessed part,
13 ... 2nd fine recessed part.

Claims (11)

潤滑油の存在下で相対的に摺動する摺動部材の少なくとも一方の摺動部材の摺動面に多数の微細凹部を形成した低摩擦摺動部材であって、前記微細凹部は、多数の第１微細凹部間に、摺動方向の幅及び深さが前記第１微細凹部より小さな値の第２微細凹部を形成したことを特徴とする低摩擦摺動部材。   A low-friction sliding member in which a large number of fine recesses are formed on the sliding surface of at least one of the sliding members that slide relatively in the presence of lubricating oil. A low-friction sliding member characterized in that a second fine recess having a smaller width and depth in the sliding direction than the first fine recess is formed between the first fine recesses. 前記第２微細凹部は、相互に独立に形成したことを特徴とする請求項１記載の低摩擦摺動部材。   The low-friction sliding member according to claim 1, wherein the second fine recesses are formed independently of each other. 前記第２微細凹部は、前記第１微細凹部間の摺動面を連続的に伸延する溝状に形成したことを特徴とする請求項１に記載の低摩擦摺動部材。   2. The low friction sliding member according to claim 1, wherein the second fine recess is formed in a groove shape that continuously extends a sliding surface between the first fine recesses. 前記第１微細凹部は、前記摺動方向と直交する方向に扁平形状の凹部である請求項１〜３のいずれかに記載の低摩擦摺動部材。   The low friction sliding member according to any one of claims 1 to 3, wherein the first fine recess is a recess having a flat shape in a direction orthogonal to the sliding direction. 前記第２微細凹部の前記摺動方向の幅（X２）と前記第１微細凹部の前記摺動方向の幅（Ｘ１）との比（X２／Ｘ１）が、１／１５〜２／３であり、前記第２微細凹部の深さ（ｈ２）と前記第１微細凹部の深さ（ｈ１）との比（ｈ２／ｈ１）が、１／１０〜１／２である請求項１〜４のいずれかに記載の低摩擦摺動部材。   The ratio (X2 / X1) of the width (X2) in the sliding direction of the second fine recess to the width (X1) in the sliding direction of the first fine recess is 1/15 to 2/3. The ratio (h2 / h1) between the depth (h2) of the second fine recess and the depth (h1) of the first fine recess is 1/10 to 1/2. A low friction sliding member according to claim 1. 前記第１微細凹部及び第２微細凹部が前記摺動面で占有する面積率(％)×深さ(μｍ)の値が３０以下であることを特徴とする請求項１〜５のいずれかに記載の低摩擦摺動部材。   The value of the area ratio (%) × depth (μm) occupied by the sliding surface by the first fine concave portion and the second fine concave portion is 30 or less. The low friction sliding member as described. 前記第２微細凹部は、前記摺動面で占有する面積率が０．５〜２０％であることを特徴とする請求項１〜６のいずれかに記載の低摩擦摺動部材。   The low-friction sliding member according to any one of claims 1 to 6, wherein the second fine recess has an area ratio of 0.5 to 20% occupied by the sliding surface. 前記第２微細凹部は、前記第１微細凹部間の表面粗さ（Ｒｚ）が、
０．０３μｍ≦Ｒｚ≦０．２５μm
であり、表面粗さのゆがみ（Ｒｓｋ；ＪＩＳ Ｂ ０６０１記載)の値が負であるランダム溝としたことを特徴とする請求項１に記載の低摩擦摺動部材。 The second fine recess has a surface roughness (Rz) between the first fine recesses,
0.03 μm ≦ Rz ≦ 0.25 μm
The low friction sliding member according to claim 1, wherein the groove is a random groove having a negative surface roughness distortion (Rsk; described in JIS B 0601). 前記第１微細凹部は、前記摺動面で占有する面積率(％)が０．３％〜１０％である請求項１〜８のいずれかに記載の低摩擦摺動部材。   The low-friction sliding member according to any one of claims 1 to 8, wherein the first fine recess has an area ratio (%) occupied by the sliding surface of 0.3% to 10%. 前記第１微細凹部は、最大深さが０．５μm〜２０μmである請求項１〜９のいずれかに記載の低摩擦摺動部材。   The low friction sliding member according to claim 1, wherein the first fine recess has a maximum depth of 0.5 μm to 20 μm. 前記第１微細凹部は、短辺の長さが５０μm〜１５０μmであり、長辺の長さを短辺の２倍以上１０倍以下としたことを特徴とする請求項１〜１０のいずれかに記載の低摩擦摺動部材。   11. The first fine recess according to claim 1, wherein a length of a short side is 50 μm to 150 μm, and a length of the long side is set to be 2 to 10 times the short side. The low friction sliding member as described.
JP2006152381A 2006-05-31 2006-05-31 Low-friction sliding member Pending JP2007321860A (en)

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