JPH0634152U - Piston structure of internal combustion engine - Google Patents
Piston structure of internal combustion engineInfo
- Publication number
- JPH0634152U JPH0634152U JP6874492U JP6874492U JPH0634152U JP H0634152 U JPH0634152 U JP H0634152U JP 6874492 U JP6874492 U JP 6874492U JP 6874492 U JP6874492 U JP 6874492U JP H0634152 U JPH0634152 U JP H0634152U
- Authority
- JP
- Japan
- Prior art keywords
- inclined surface
- piston
- cylinder
- outer peripheral
- thrust side
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
(57)【要約】
【目的】 潤滑性能を向上させてシリンダ壁に対するピ
ストンの摺動摩擦抵抗を低減し、機関の出力向上と燃費
の低下を図る。
【構成】 スカート部２０の上端部外周縁に約０．１°
〜３°の傾斜角度θをもつ傾斜面２２を形成すると共
に、前記反スラスト側の傾斜面２２ａ角度θ１をスラス
ト側の傾斜面２２ｂ角度θ２よりも大きく設定してい
る。そして、傾斜面２２の下部外周縁２４でシリンダ１
０の一側面１０ａに付着している潤滑油を掻き集めなが
ら適度な油膜厚さに均すようにした。
(57) [Abstract] [Purpose] To improve the lubrication performance and reduce the sliding frictional resistance of the piston against the cylinder wall to improve the engine output and reduce fuel consumption. [Structure] The outer peripheral edge of the upper end of the skirt portion 20 is approximately 0.1 °.
The inclined surface 22 having an inclination angle θ of ˜3 ° is formed, and the angle θ1 of the inclined surface 22a on the anti-thrust side is set to be larger than the angle θ2 of the inclined surface 22b on the thrust side. Then, at the lower outer peripheral edge 24 of the inclined surface 22, the cylinder 1
The lubricating oil adhering to the one side surface 10a of No. 0 was scraped so as to have an appropriate oil film thickness.
Description
【０００１】[0001]
本考案は、内燃機関のピストン構造の改良に関する。 The present invention relates to improvement of a piston structure of an internal combustion engine.
【０００２】[0002]
周知のように、例えば自動車用内燃機関のピストンにあっては、膨張行程時の 燃焼ガス圧によって高熱に晒されて熱膨張変化すると共に、爆発力によりコンロ ッドを押圧する反力に起因して、シリンダの壁面に押さえ付けられる側力つまり スラスト力が作用する。このため、ピストンとシリンダ壁面との間に、ピストン スラップによる打音や摺動抵抗による摩耗が発生し易くなっている。 As is well known, for example, a piston of an internal combustion engine for an automobile is exposed to high heat due to the combustion gas pressure during the expansion stroke and undergoes thermal expansion change, and at the same time, it is caused by the reaction force that presses the stove by the explosive force. As a result, a side force that is pressed against the wall surface of the cylinder, that is, a thrust force acts. For this reason, between the piston and the cylinder wall surface, it is easy for the tapping sound of the piston slap and the abrasion due to the sliding resistance to occur.
【０００３】 そこで、例えば図４に示すようにピストン１の最も熱膨張変化量の大きい冠部 ２の外周面からリング溝ランド部３及びスカート部４の上端部４ａ外周面をバレ ル形状に形成して、熱膨張変化量の均一化等を図り、局部的な摺動摩擦抵抗によ る摩耗等の発生を防止する技術も提供されている（実開昭６１−３９４８号公報 等参照）。Therefore, for example, as shown in FIG. 4, the outer peripheral surface of the crown portion 2 of the piston 1 having the largest amount of change in thermal expansion from the outer peripheral surface of the ring groove land portion 3 and the upper end portion 4a of the skirt portion 4 is formed into a ball shape. In addition, there is also provided a technique for making the amount of change in thermal expansion uniform and preventing the occurrence of wear or the like due to local sliding frictional resistance (see Japanese Utility Model Laid-Open No. 61-3948).
【０００４】[0004]
然し乍ら、前記従来のピストン構造にあっては、スカート部４の上端部４ａ外 周面４ｂ全体を円弧面としたため、例えば排気行程時などにピストン１が傾動し て冠部２側がシリンダ壁５と当接するスカート部４の反スラスト側外周面４ｂの うち、シリンダ壁５に当接する接触部位４ｃよりも上方の非接触部位４ｄでは、 シリンダ壁５に付着した潤滑油を掻き集めたり適当な油膜厚さに均すことが不可 能である。したがって、外周面４ｂの接触部位４ｃとシリンダ壁５間の潤滑性能 が低下し、摺動摩擦抵抗が大きくなる惧れがある。 However, in the conventional piston structure described above, since the entire outer peripheral surface 4b of the upper end portion 4a of the skirt portion 4 is a circular arc surface, the piston 1 tilts, for example, during the exhaust stroke so that the crown portion 2 side becomes the cylinder wall 5. Of the non-thrust side outer peripheral surface 4b of the abutting skirt portion 4 at the non-contact portion 4d above the contact portion 4c abutting on the cylinder wall 5, the lubricating oil adhering to the cylinder wall 5 is scraped off or an appropriate oil film thickness is obtained. It is impossible to level it. Therefore, the lubrication performance between the contact portion 4c of the outer peripheral surface 4b and the cylinder wall 5 may be deteriorated, and the sliding friction resistance may be increased.
【０００５】[0005]
本考案は、前記従来の実情に鑑みて案出されたもので、冠部の下端部に有する ピストンリング溝と、該最下端側のピストンリング溝の下部に有するスカート部 とを備えた内燃機関のピストン構造において、前記最下端側のピストンリング溝 を構成するスカート部の上端部外周縁に傾斜面を形成すると共に、反スラスト側 の前記傾斜面角度を、スラスト側の傾斜面角度よりも大きく設定したことを特徴 としている。 The present invention has been devised in view of the above-mentioned conventional circumstances, and an internal combustion engine including a piston ring groove provided at a lower end portion of a crown portion and a skirt portion provided at a lower portion of the piston ring groove at the lowermost end side. In the above piston structure, an inclined surface is formed on the outer peripheral edge of the upper end portion of the skirt that constitutes the piston ring groove on the lowermost end side, and the inclined surface angle on the anti-thrust side is larger than the inclined surface angle on the thrust side. The feature is that it is set.
【０００６】[0006]
前記構成の本考案によれば、例えば排気行程時などにおいて、スカート部上端 部に形成された傾斜面の下端外周縁によって、シリンダ壁に付着した潤滑油全体 を掻き集めながら適当な油膜厚さに均すことが可能になる。このため、該傾斜面 下部のシリンダ壁との接触部位とシリンダ壁間の潤滑性能が良好となる。 According to the present invention having the above-described structure, for example, during an exhaust stroke, the lower end outer peripheral edge of the inclined surface formed at the upper end of the skirt part scrapes the entire lubricating oil adhering to the cylinder wall to obtain an appropriate oil film thickness. Can be done. For this reason, the lubrication performance between the cylinder wall and the contact portion with the cylinder wall under the inclined surface is improved.
【０００７】 しかも、スカート部の接触部位に対して反スラスト側の傾斜面角度をスラスト 側傾斜面角度よりも大きく設定したことにより、ピストンの傾動時つまり冠部が シリンダ壁側に傾動した際に、前記反スラスト側傾斜面のシリンダ壁に対する接 触面積が小さくなる。このため、前記油膜の形成及び均一化と相俟って摺動摩擦 抵抗が低減する。Moreover, by setting the inclined surface angle on the anti-thrust side larger than the thrust side inclined surface angle with respect to the contact portion of the skirt portion, when the piston is tilted, that is, when the crown portion is tilted to the cylinder wall side. The contact area of the anti-thrust side inclined surface with the cylinder wall is reduced. Therefore, the sliding friction resistance is reduced in combination with the formation and uniformization of the oil film.
【０００８】[0008]
以下、本考案の実施例を図面に基づいて詳述する。尚、説明の都合上、シリン ダとピストンとの間の隙間は誇張して描いてある。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. For convenience of explanation, the gap between the cylinder and the piston is exaggerated.
【０００９】 図３は本考案に係る内燃機関のピストン構造の一実施例を示している。即ち、 シリンダブロック内に形成されたシリンダ１０内を往復運動するピストン１１は 、燃焼室１２内での爆発力を受ける冠部１３と、該冠部１３の下部外周に形成さ れてトップリング１４，セカンドリング１５，オイルリング１６を夫々嵌着保持 するピストンリング溝１７，１８，１９と各ピストンリング溝１７，１８，１９ の下端部に有するスカート部２０と、コンロッドの小端部が連結されるピストン ピン２１とを備えている。FIG. 3 shows an embodiment of a piston structure of an internal combustion engine according to the present invention. That is, the piston 11 that reciprocates in the cylinder 10 formed in the cylinder block includes a crown portion 13 that receives an explosive force in the combustion chamber 12, and a top ring 14 that is formed on the outer periphery of the lower portion of the crown portion 13. The piston ring grooves 17, 18 and 19 in which the second ring 15 and the oil ring 16 are fitted and held respectively, the skirt portion 20 at the lower end of each piston ring groove 17, 18 and 19, and the small end portion of the connecting rod are connected. And a piston pin 21.
【００１０】 前記スカート部２０は、横断面略円形状を呈し、前記最下端部のオイルリング 溝１９の一部を構成する上端部２０ａの外周縁全体に平坦状の傾斜面２２が形成 されている。この傾斜面２２は、その傾斜角度θが傾斜面２２下部のシリンダ１ ０の壁面と接触する直線状の接触部位２３を基準として０.１°〜３°設定され ていると共に、高さＬ１が３mmからスカート部２０の高さＬの略１／４mmに設定 されている。また、この傾斜面２２の下部外周縁２４は、円弧状に形成されて接 触部位２３と滑らかな曲線で連続的に結ばれている。The skirt portion 20 has a substantially circular cross section, and a flat inclined surface 22 is formed on the entire outer peripheral edge of an upper end portion 20 a which constitutes a part of the oil ring groove 19 at the lowermost end portion. There is. The inclination angle θ of the inclined surface 22 is set to 0.1 ° to 3 ° with reference to the linear contact portion 23 that comes into contact with the wall surface of the cylinder 10 below the inclined surface 22, and the height L1 is set. It is set from 3 mm to about 1/4 mm of the height L of the skirt portion 20. The lower peripheral edge 24 of the inclined surface 22 is formed in an arc shape and is continuously connected to the contact portion 23 with a smooth curve.
【００１１】 更に、前記傾斜面２２は、図１及び図２に示すように機関の排気行程時などに おいてピストン１１が上昇運動する際に、該ピストン１１が傾動して冠部１３が シリンダ１０の一側壁１０ａに当たる所謂反スラスト側の傾斜面２２ａの傾斜角 度θ１が、反対側のスラスト側の傾斜面２２ｂの傾斜角度θ２よりも大きく設定 されている。つまり、例えばスラスト側傾斜面２２ｂの傾斜角度θ２が１°であ るとすれば反スラスト側傾斜面２２ａの傾斜角度θ１は３°に設定されている。Further, as shown in FIGS. 1 and 2, when the piston 11 moves upward during an exhaust stroke of the engine, the inclined surface 22 tilts so that the crown portion 13 becomes a cylinder. The inclination angle θ1 of the so-called anti-thrust side inclined surface 22a that hits the one side wall 10a of 10 is set to be larger than the inclination angle θ2 of the opposite thrust side inclined surface 22b. That is, for example, if the inclination angle θ2 of the thrust side inclined surface 22b is 1 °, the inclination angle θ1 of the anti-thrust side inclined surface 22a is set to 3 °.
【００１２】 したがって、この実施例によれば、排気行程や圧縮行程時などにピストン１１ がシリンダ一側面１０ａ側へ傾動しながら上昇運動すると、傾斜面２２ａの下部 外周縁２４がシリンダ一側面１０ａを摺接しながら、該一側面１０ａに付着して いる潤滑油を掻き集めつつ一定の適当な油膜厚さに均す。このため、スカート部 ２０の接触部位２３とシリンダ一側面１０ａとの間の潤滑性能が良好になる。こ の結果、ピストン１１のシリンダ１０に対する摺動摩擦抵抗が低減する。Therefore, according to this embodiment, when the piston 11 moves upward while tilting toward the cylinder one side surface 10a during the exhaust stroke or the compression stroke, the lower outer peripheral edge 24 of the inclined surface 22a moves toward the cylinder one side surface 10a. While slidably contacting, the lubricating oil adhering to the one side surface 10a is scraped and evened to a certain suitable oil film thickness. Therefore, the lubrication performance between the contact portion 23 of the skirt portion 20 and the cylinder one side surface 10a is improved. As a result, the sliding frictional resistance of the piston 11 with respect to the cylinder 10 is reduced.
【００１３】 しかも、反スラスト側傾斜面２２ａの傾斜角度θ１がスラスト側傾斜面２２ｂ の傾斜角度θ２よりも大きく設定されているため、ピストン１１の前記傾動時に おいて、反スラスト側傾斜面２２ａの下部外周縁２４のシリンダ一側面１０ａに 対する接触面積がスラスト側下部外周縁よりも小さくなる。このため、前記潤滑 油の掻集及び油膜厚さの均一化と相俟って接触部位２３とシリンダ一側面１０ａ との摺動摩擦抵抗が一層低減する。この結果、機関の出力の向上と燃費の低下が 図れる。Moreover, since the inclination angle θ1 of the anti-thrust side inclined surface 22a is set to be larger than the inclination angle θ2 of the thrust side inclined surface 22b, when the piston 11 tilts, the anti-thrust side inclined surface 22a is inclined. The contact area of the lower outer peripheral edge 24 with the one side surface 10a of the cylinder is smaller than that of the lower outer peripheral edge on the thrust side. Therefore, the sliding frictional resistance between the contact portion 23 and the one side surface 10a of the cylinder is further reduced in combination with the scraping of the lubricating oil and the uniformization of the oil film thickness. As a result, the output of the engine can be improved and the fuel consumption can be reduced.
【００１４】 また、傾斜面２２と接触部位２３が滑らかな曲線で連続的に結ばれているため 、外周縁２４で掻き集められた潤滑油を接触部位２３方向へ円滑に送り出すこと ができ、潤滑作用がさらに良好になる。Further, since the inclined surface 22 and the contact portion 23 are continuously connected by a smooth curve, the lubricating oil scraped up by the outer peripheral edge 24 can be smoothly delivered toward the contact portion 23, and the lubricating action Will be even better.
【００１５】 尚、前記傾斜面２２の傾斜角度や高さＬ１は、考案者の実験の結果、前述のよ うにな潤滑油の掻集作用や油膜厚さの均し作用が最も適正かつ確実に行われたこ とによって選択されたものである。As a result of experiments conducted by the inventor, the inclination angle and the height L1 of the inclined surface 22 are the most appropriate and assured, as described above, for the collecting action of the lubricating oil and the leveling action of the oil film thickness. It was selected by what was done.
【００１６】 また、前記傾斜面２２は、平坦状の他に緩やかな曲面状に形成することも可能 である。Further, the inclined surface 22 can be formed in a gentle curved surface shape in addition to the flat shape.
【００１７】[0017]
以上の説明で明らかなように、本考案に係る内燃機関のピストン構造によれば 、ピストンの上昇運動時に、スカート部の上端部に形成された傾斜面の下部外周 縁によって、シリンダ壁に付着している潤滑油を掻集しかつ適当な油膜厚さに均 すことができるため、スカート部とシリンダ壁との間の潤滑性能が向上し、摺動 摩擦抵抗が十分に低減される。 As is clear from the above description, according to the piston structure of the internal combustion engine according to the present invention, when the piston moves upward, it is attached to the cylinder wall by the lower peripheral edge of the inclined surface formed at the upper end of the skirt. Since the lubricating oil that is present can be collected and leveled to an appropriate oil film thickness, the lubricating performance between the skirt portion and the cylinder wall is improved, and sliding friction resistance is sufficiently reduced.
【００１８】 しかも、反スラスト側の傾斜面角度をスラスト側の傾斜面角度よりも大きく設 定したため、シリンダ壁に対する接触面積が小さくなる。したがって、前記潤滑 油の掻集作用や油膜厚さの均一作用と相俟ってピストンの摺動摩擦抵抗が一層低 減する。この結果、機関の出力の向上と、燃費の低減が図れる。Moreover, since the inclined surface angle on the anti-thrust side is set to be larger than the inclined surface angle on the thrust side, the contact area with the cylinder wall becomes small. Therefore, the sliding frictional resistance of the piston is further reduced in combination with the scraping action of the lubricating oil and the uniform action of the oil film thickness. As a result, the output of the engine can be improved and the fuel consumption can be reduced.
【図１】本考案の一実施例を示す図３のＡ部拡大図。FIG. 1 is an enlarged view of part A of FIG. 3 showing an embodiment of the present invention.
【図２】図３のＢ部拡大図。FIG. 2 is an enlarged view of part B in FIG.
【図３】本実施例のピストン構造を示す正面図。FIG. 3 is a front view showing the piston structure of the present embodiment.
【図４】従来のピストン構造を示す正面図。FIG. 4 is a front view showing a conventional piston structure.
１０…シリンダ １０ａ…一側面 １１…ピストン １３…冠部 １７，１８，１９…ピストンリング溝 ２０…スカート部 ２０ａ…上端部 ２２…傾斜面 ２２ａ…反スラスト側傾斜面 ２２ｂ…スラスト側傾斜面 DESCRIPTION OF SYMBOLS 10 ... Cylinder 10a ... One side surface 11 ... Piston 13 ... Crown part 17, 18, 19 ... Piston ring groove 20 ... Skirt part 20a ... Upper end part 22 ... Inclined surface 22a ... Anti thrust side inclined surface 22b ... Thrust side inclined surface
Claims (1)
と、該最下端側のピストンリング溝の下部に有するスカ
ート部とを備えた内燃機関のピストン構造において、前
記最下端側のピストンリング溝を構成するスカート部の
上端部外周縁に傾斜面を形成すると共に、反スラスト側
の前記傾斜面角度を、スラスト側の傾斜面角度よりも大
きく設定したことを特徴とする内燃機関のピストン構
造。1. A piston structure for an internal combustion engine, comprising: a piston ring groove at a lower end of a crown portion; and a skirt portion at a lower part of the piston ring groove at a lowermost end side, wherein the piston ring groove at the lowermost end side is formed. The piston structure of the internal combustion engine, wherein an inclined surface is formed on an outer peripheral edge of an upper end portion of the skirt portion, and the inclined surface angle on the anti-thrust side is set to be larger than the inclined surface angle on the thrust side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6874492U JPH0634152U (en) | 1992-10-02 | 1992-10-02 | Piston structure of internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6874492U JPH0634152U (en) | 1992-10-02 | 1992-10-02 | Piston structure of internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0634152U true JPH0634152U (en) | 1994-05-06 |
Family
ID=13382599
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6874492U Pending JPH0634152U (en) | 1992-10-02 | 1992-10-02 | Piston structure of internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0634152U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2018145861A (en) * | 2017-03-06 | 2018-09-20 | 日野自動車株式会社 | Piston structure |
| JP2019190445A (en) * | 2018-04-27 | 2019-10-31 | 三菱自動車工業株式会社 | Lubrication structure of piston |
-
1992
- 1992-10-02 JP JP6874492U patent/JPH0634152U/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2018145861A (en) * | 2017-03-06 | 2018-09-20 | 日野自動車株式会社 | Piston structure |
| JP2019190445A (en) * | 2018-04-27 | 2019-10-31 | 三菱自動車工業株式会社 | Lubrication structure of piston |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6357341B1 (en) | Piston of internal combustion engine | |
| JP5063634B2 (en) | Piston of internal combustion engine | |
| US20070272078A1 (en) | Piston Device for Internal Combustion Engine | |
| US5695199A (en) | Piston sealing assembly | |
| JPH05240348A (en) | Piston ring assembly | |
| US10927787B2 (en) | Piston for internal combustion engine | |
| JPH0634152U (en) | Piston structure of internal combustion engine | |
| KR20210025484A (en) | Piston and cylinder of an internal combustion engine and internal combustion engine | |
| JP3239493B2 (en) | Piston for internal combustion engine | |
| JPS6029656Y2 (en) | internal combustion engine piston | |
| JP2001508519A (en) | Internal combustion engine piston | |
| JP2564947Y2 (en) | Barrel face type piston ring | |
| RU2301364C2 (en) | Oil control device of cylinder-piston group | |
| AU2020100333A4 (en) | Tumbler Piston | |
| JP2018112275A (en) | Mounting structure of piston ring | |
| RU184035U1 (en) | PISTON OF THE DIESEL ENGINE OF INTERNAL COMBUSTION | |
| JPH0324857Y2 (en) | ||
| JP3778247B2 (en) | Engine cylinder structure | |
| JPH0680057U (en) | Pressure ring for internal combustion engine | |
| JPH0667838U (en) | Piston structure of internal combustion engine | |
| JPH0353005Y2 (en) | ||
| JPS6123636Y2 (en) | ||
| JP2598518Y2 (en) | Internal combustion engine piston | |
| JPH0673353U (en) | Cylinder liner mounting structure for internal combustion engine | |
| JPH06229315A (en) | Piston device of internal combustion engine |