JPH07139631A - Pressure ring - Google Patents
Pressure ringInfo
- Publication number
- JPH07139631A JPH07139631A JP29071593A JP29071593A JPH07139631A JP H07139631 A JPH07139631 A JP H07139631A JP 29071593 A JP29071593 A JP 29071593A JP 29071593 A JP29071593 A JP 29071593A JP H07139631 A JPH07139631 A JP H07139631A
- Authority
- JP
- Japan
- Prior art keywords
- pressure ring
- ring
- wear
- notch
- mating
- 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
Classifications
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
- F16J9/26—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction characterised by the use of particular materials
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
- F16J9/12—Details
- F16J9/14—Joint-closures
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Physical Vapour Deposition (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は圧力リングに関し、特
に、特殊合い口構造を有する圧力リングにおける合い口
部の耐折損性を向上させた圧力リングに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure ring, and more particularly, to a pressure ring having a special ring structure with improved breakage resistance of the mating portion.
【０００２】[0002]
【従来の技術】一般に往復動内燃機関のピストンには、
ピストンリングとして圧力リングとオイルリングとが装
着される。この圧力リングは、高圧の燃焼ガスが燃焼室
側からクランク室側へ流出する現象（ブローバイ）の防
止機能およびシリンダ内壁の余分な潤滑油が燃焼室に流
入することを防止している。一方、オイルリングは、シ
リンダ内壁の余分な潤滑油がクランク室側から燃焼室側
へ侵入して消費される現象（オイルアップ）の抑制機能
を有する。そして、従来の標準的なピストンリングの組
合せとしては、トップリングおよびセカンドリングから
なる２本の圧力リングと１本のオイルリングとの計３本
のピストンリングの組合せが知られている。2. Description of the Related Art Generally, a piston of a reciprocating internal combustion engine has
A pressure ring and an oil ring are attached as piston rings. The pressure ring has a function of preventing a phenomenon (blow-by) in which high-pressure combustion gas flows from the combustion chamber side to the crank chamber side, and prevents excess lubricating oil on the inner wall of the cylinder from flowing into the combustion chamber. On the other hand, the oil ring has a function of suppressing a phenomenon (oil-up) in which excess lubricating oil on the inner wall of the cylinder invades from the crank chamber side to the combustion chamber side and is consumed. As a conventional standard combination of piston rings, a combination of two pressure rings consisting of a top ring and a second ring and one oil ring, a total of three piston rings, is known.
【０００３】一方、内燃機関の低燃費化の要請からピス
トンリングの構成についても種々の検討がなされ、特に
１本の圧力リングと１本のオイルリングとを組合せた２
本構成のピストンリングは、摩擦損失を低減し、内燃機
関の一層の効率化を可能にする技術として注目されてい
る。On the other hand, various studies have been made on the structure of the piston ring in order to reduce the fuel consumption of the internal combustion engine. In particular, a combination of one pressure ring and one oil ring is used.
The piston ring having this configuration has attracted attention as a technology that reduces friction loss and enables further efficiency of the internal combustion engine.
【０００４】しかしながら、この２本構成のピストンリ
ングはシール性の維持に留意しなければならない。従っ
て、ここに使用される圧力リングは、気密特性に優れて
いることが要求される。かかる気密特性の向上を図った
圧力リングとして、たとえば図１に示す特殊合い口構造
（いわゆるダブルラップジョイント構造）の圧力リング
が提案されている（実公平１−２２９１６号公報参
照）。However, care must be taken to maintain the sealability of the piston ring having the two-piece construction. Therefore, the pressure ring used here is required to have excellent airtight properties. As a pressure ring for improving the airtightness, for example, a pressure ring having a special gap structure (so-called double lap joint structure) shown in FIG. 1 has been proposed (see Japanese Utility Model Publication No. 1-221616).
【０００５】図１に示すように、この特殊合い口構造の
圧力リング１は、一方の合い口端部２に切欠凸部２ａを
設けるとともに、他方の合い口端部３に前記切欠凸部２
ａと係合する形状の切欠凹部３ａを設けている．そし
て、圧力リング１は、合い口端部２および３で広げられ
ピストン外周面のリング溝に装着され、切欠凸部２ａと
切欠凹部３ａが互いに係合して圧力リング１の合い口端
部２および３をオイルシールする構造になっている。As shown in FIG. 1, the pressure ring 1 of this special abutment structure is provided with a notch convex portion 2a at one abutment end portion 2 and at the other abutment end portion 3 at the aforesaid notch convex portion 2a.
A notched recess 3a having a shape that engages with a is provided. Then, the pressure ring 1 is unfolded at the abutment ends 2 and 3 and mounted in the ring groove on the outer peripheral surface of the piston, and the notch convex portion 2a and the notch recess 3a are engaged with each other so that the abutment end portion 2 of the pressure ring 1 is engaged. It has a structure in which 3 and 3 are oil-sealed.
【０００６】また、上記特殊合い口構造の圧力リングに
おいては、図７に示すように、シリンダの内周面と当接
するピストンリングの外周面４に、厚さ１００〜１５０
μｍ程度のクロムメッキ処理５を施し、耐摩耗性を付与
している。Further, in the pressure ring having the special mouthpiece structure, as shown in FIG. 7, the outer peripheral surface 4 of the piston ring which is in contact with the inner peripheral surface of the cylinder has a thickness of 100 to 150.
A chrome plating treatment 5 of about μm is applied to impart wear resistance.
【０００７】[0007]
【発明が解決しようとする課題】しかしながら、上述し
た従来の特殊合い口構造の圧力リングは、ピストンリン
グの外周面４に施されるクロムメッキ５等の厚さｔが、
１００〜１５０μｍ程度と厚いため、その分ピストンリ
ングの幅（通常１．２ｍｍ〜１．５ｍｍ）および切欠凸
部２ａの幅Ｔが制約を受け、その結果、切欠凸部２ａの
曲げ強度を示す断面係数（Ｚ）（Ｎ方向）が小さくな
り、切欠凸部２ａが折れやすくなるという問題がある。However, in the pressure ring having the above-mentioned conventional special contact structure, the thickness t of the chromium plating 5 or the like applied to the outer peripheral surface 4 of the piston ring is
Since it is as thick as about 100 to 150 μm, the width of the piston ring (normally 1.2 mm to 1.5 mm) and the width T of the notch protrusion 2a are restricted accordingly, and as a result, a cross section showing the bending strength of the notch protrusion 2a. There is a problem that the coefficient (Z) (N direction) becomes small and the notch convex portion 2a easily breaks.
【０００８】また、クロムメッキ等は、摺動面摩耗によ
るピストンリング合い口の広がりによって、図２に示す
ラップ長ｌが減少し、特に高速回転時のオイルシール性
が悪化し、オイル消費が増大するという問題がある。す
なわち、ラップ長ｌとオイル消費量とは図３に示す関係
があり、ラップ長ｌの下限値はオイル消費量を考慮する
と約１．０ｍｍを確保する必要があり、ラップ長ｌが減
少し約１．０ｍｍ以下になるとオイルシール性が悪化
し、オイル消費が増大する。With chrome plating or the like, the lap length 1 shown in FIG. 2 decreases due to the expansion of the piston ring mating area due to wear of the sliding surface, and the oil sealability deteriorates especially at high speed rotation, increasing oil consumption. There is a problem of doing. That is, the lap length 1 and the oil consumption amount have the relationship shown in FIG. 3, and it is necessary to secure the lower limit value of the lap length 1 to be about 1.0 mm in consideration of the oil consumption amount. If it is 1.0 mm or less, the oil sealability deteriorates and the oil consumption increases.
【０００９】一方、図２に示すように、摩耗によるピス
トンリング合い口の広がりによってラップ長ｌが減少す
るのを補うため、あらかじめラップ長ｌをこの減少分だ
け長くすると、その分切欠凸部２ａの長さ（腕の長さ）
Ｌも長くなり、一定荷重が切欠凸部２ａに加わった場
合、基端部Ａにより大きな曲げモーメントが加わり、切
欠凸部２ａの細い基端部Ａが折れやすくなるという問題
がある。On the other hand, as shown in FIG. 2, in order to compensate for the decrease in the lap length 1 due to the expansion of the piston ring mating opening due to wear, if the lap length 1 is previously lengthened by this decrease, the cutout convex portion 2a is correspondingly increased. Length (arm length)
When L becomes long and a constant load is applied to the cutout protrusion 2a, a large bending moment is applied to the base end A, and the thin base end A of the cutout protrusion 2a is easily broken.
【００１０】本発明は上記問題点にがんがみてなされた
ものであり、特殊合い口構造を有する圧力リングにおけ
る合い口部の耐折損性を向上させた圧力リングの提供を
目的とする。The present invention has been made in view of the above problems, and an object of the present invention is to provide a pressure ring having improved breakage resistance of the mating portion in a pressure ring having a special mating structure.
【００１１】[0011]
【課題を解決するための手段】上記目的を達成するため
に本発明の圧力リングは、内燃機関用ピストンリングで
あって、一方の合い口端部に切欠凸部を設けるととも
に、他方の合い口端部に前記切欠凸部と係合する形状の
切欠凹部を設けてなる特殊合い口構造の圧力リングにお
いて、シリンダの内周面と当接するピストンリングの外
周面に厚さ３〜３０μｍの耐摩耗性被膜を形成した構成
としてある。In order to achieve the above object, a pressure ring of the present invention is a piston ring for an internal combustion engine, in which a notch convex portion is provided at one end of the mating port and the other mating port is provided. A pressure ring having a special gap structure having a notch concave portion having a shape that engages with the notch convex portion at an end thereof, and a wear resistance having a thickness of 3 to 30 μm on the outer peripheral surface of the piston ring that abuts the inner peripheral surface of the cylinder. The film is formed with a conductive coating.
【００１２】また、本発明の圧力リングは、必要に応
じ、前記耐摩耗性被膜を、イオンプレーティング法、ス
パッタ法、真空蒸着法、または化学的蒸着法によって形
成した構成とし、あるいは、前記耐摩耗性被膜が、Ｃｒ
−Ｎ，Ｃｒ2 Ｎ，ＴｉＮ，Ｔｉ／ＴｉＮ，ＴａＮ，Ｚｒ
Ｎ，ＴｉＣ，ＴａＣ，ＳｉＣまたはＴａ2 Ｏ5 である構
成とした。Further, the pressure ring of the present invention has a structure in which the abrasion resistant coating is formed by an ion plating method, a sputtering method, a vacuum vapor deposition method, or a chemical vapor deposition method, if necessary. Abrasive coating is Cr
-N, Cr 2 N, TiN, Ti / TiN, TaN, Zr
The structure is N, TiC, TaC, SiC or Ta 2 O 5 .
【００１３】[0013]
【作用】上記構成からなる本発明の圧力リングは、図４
に示すように、シリンダの内周面と当接するピストンリ
ングの外周面４に施される耐摩耗性被膜５の厚さを３〜
３０μｍとしてあるので、従来（図７）に比べピストン
リングの幅および切欠凸部２ａの幅Ｔを長く取ることが
でき、その結果、切欠凸部２ａの曲げ強度アップに寄与
できる断面係数を大きくすることができ、したがって、
切欠凸部２ａが折れにくくなる。The pressure ring of the present invention having the above construction is shown in FIG.
As shown in FIG. 3, the thickness of the wear-resistant coating 5 applied to the outer peripheral surface 4 of the piston ring that contacts the inner peripheral surface of the cylinder is 3 to
Since the width is 30 μm, the width of the piston ring and the width T of the notch protrusion 2a can be made longer than in the conventional case (FIG. 7), and as a result, the section modulus that can contribute to the increase in bending strength of the notch protrusion 2a is increased. Can therefore be
The notch convex portion 2a becomes difficult to break.
【００１４】また、ピストンリングの外周面４に施され
る耐摩耗性被膜５の耐摩耗性は、従来のクロムメッキ等
に比べ耐摩耗性が大きいので、摩耗によるピストンリン
グの広がりによってラップ長が減少し、オイルシール性
が悪化し、オイル消費が増大しにくい。さらに、摩耗に
よるピストンリング合い口の広がりがなく、ラップ長を
その分短くできるので、曲げモーメントの腕の長さが短
くでき、切欠凸部２ａの細い基端部が折れにくい。Further, the wear resistance of the wear resistant coating 5 applied to the outer peripheral surface 4 of the piston ring is higher than that of the conventional chrome plating and the like, so that the wrap length is increased by the spread of the piston ring due to the wear. The oil consumption is reduced, the oil sealability is deteriorated, and the oil consumption is hard to increase. Further, since there is no spread of the piston ring mating due to wear and the lap length can be shortened accordingly, the arm length of the bending moment can be shortened and the thin base end of the notch convex portion 2a is hard to break.
【００１５】[0015]
【実施例】以下、本発明の実施例を図面を参照して説明
する。本発明の圧力リングは、図１に示すように、特殊
合い口構造（ダブルラップジョイント構造）の圧力リン
グ１であり、一方の合い口端部２には切欠凸部２ａが設
けてあり、他方の合い口端部３には前記切欠凸部２ａと
係合する形状の切欠凹部３ａを設けてある。Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the pressure ring of the present invention is a pressure ring 1 having a special mating structure (double lap joint structure), in which one of the mating end portions 2 is provided with a notch convex portion 2a, and the other A notch concave portion 3a having a shape that engages with the notch convex portion 2a is provided at the abutment end portion 3.
【００１６】本発明の圧力リング１においては、シリン
ダの内周面と当接するピストンリングの外周面４に厚さ
３〜３０μｍの耐摩耗性被膜５を形成してある。ここ
で、耐摩耗性被膜５の厚さを３〜３０μｍとすると、断
面係数は図５に示すようになり、断面係数の値が大きく
なると耐折損強度（疲労限界強度）は増大し、また、図
５から明らかなようにクロムメッキ厚１００μｍに対
し、本発明の耐摩耗性被膜３０μｍで計算した断面係数
の最小強度向上は、０．１４６〜０．１５３ｍｍ3 であ
り、クロムメッキ厚１５０μｍに対し、本発明の耐摩耗
性被膜３μｍで計算した断面係数の最大強度向上は、
０．１４６〜０．１６２ｍｍ3 である。In the pressure ring 1 of the present invention, the wear-resistant coating 5 having a thickness of 3 to 30 μm is formed on the outer peripheral surface 4 of the piston ring which abuts the inner peripheral surface of the cylinder. Here, assuming that the thickness of the wear-resistant coating 5 is 3 to 30 μm, the section modulus becomes as shown in FIG. 5, and as the value of the section modulus increases, the breakage resistance strength (fatigue limit strength) increases, and As is clear from FIG. 5, the minimum strength improvement of the section modulus calculated with the wear-resistant coating of 30 μm of the present invention is 0.146 to 0.153 mm 3 with respect to the chromium plating thickness of 100 μm, and with respect to the chromium plating thickness of 150 μm. The maximum strength improvement of the section modulus calculated with the wear-resistant coating of 3 μm of the present invention is
It is 0.146 to 0.162 mm 3 .
【００１７】本発明の圧力リングにおいて、厚さ３〜３
０μｍの耐摩耗性被膜を形成する方法としては、耐摩耗
性の点でメッキ法より耐摩耗性に優れるすべての処理が
挙げられる。In the pressure ring of the present invention, the thickness is 3 to 3
As a method for forming a 0 μm wear-resistant coating, all treatments that are superior to the plating method in terms of wear resistance can be mentioned.
【００１８】かかる処理としては、加熱蒸発させた蒸発
原子をアルゴングロー放電中でイオン化し、負に印加し
た素地表面上に衝突させ、凝固させるイオンプレーティ
ング法、アルゴングロー放電によって不活性ガスをイオ
ン化し、この不活性ガスイオンを負に印加したターゲッ
トに衝突させ、飛散したターゲット物質を素地表面上に
凝固させるスパッタ法、高真空中で金属を加熱蒸発さ
せ、蒸発原子を素地表面上に凝固させる真空蒸着法など
の物理的蒸着法（ＰＶＤ法）、あるいは、熱ＣＶＤ法、
プラズマＣＶＤ法、光ＣＶＤ法等の化学的蒸着法（ＣＶ
Ｄ法）等が挙げられる。Examples of such treatment include ion plating method in which vaporized atoms that have been heated and vaporized are ionized in an argon glow discharge and collided with the negatively applied substrate surface to solidify, and an inert gas is ionized by argon glow discharge. Then, the inert gas ions are made to collide with a negatively applied target to solidify the scattered target material on the surface of the substrate, the metal is heated and evaporated in a high vacuum, and evaporated atoms are solidified on the surface of the substrate. Physical vapor deposition (PVD) such as vacuum deposition, or thermal CVD,
Chemical vapor deposition (CV, such as plasma CVD, photo CVD, etc.)
D method) and the like.
【００１９】これらの方法で形成される耐摩耗性被膜
は、クロムメッキに比べ摩耗量が１／３６であり、ほと
んど摩耗がないため、０．１ｍｍのラップ長で間に合
う。したがって、ラップ長を必要最小限に抑え、腕の長
さＬを減じて耐折損強度の向上を図ることができる。ま
た、ラップ長が摩耗によって減少しないので、図３にお
いて説明したように、オイルシール性が悪化し、オイル
消費が増大することがない。The wear-resistant coating formed by these methods has a wear amount of 1/36 that of chromium plating, and since there is almost no wear, a lap length of 0.1 mm is sufficient. Therefore, the lap length can be suppressed to the necessary minimum, the arm length L can be reduced, and the breakage strength can be improved. Further, since the lap length is not reduced by wear, the oil sealability is not deteriorated and the oil consumption is not increased as described in FIG.
【００２０】本発明の圧力リングにおいて、ピストンリ
ングの外周面に形成される耐摩耗性被膜の種類として
は、Ｃｒ−Ｎ，Ｃｒ2 Ｎのほか，ＴｉＮ，Ｔｉ／Ｔｉ
Ｎ，ＴａＮ，ＺｒＮ，ＴｉＣ，ＴａＣ，ＳｉＣ，Ｔａ2
Ｏ5 等が挙げられる。In the pressure ring of the present invention, the types of wear-resistant coatings formed on the outer peripheral surface of the piston ring include Cr-N and Cr 2 N, as well as TiN and Ti / Ti.
N, TaN, ZrN, TiC, TaC, SiC, Ta 2
O 5 and the like can be mentioned.
【００２１】なお、本発明の圧力リングの切欠凹部およ
び切欠凸部の形状は、図１に示す形状に限定されず、例
えば、図６（ａ）〜（ｃ）に示す形状であってもよい。The shapes of the notched concave portions and the notched convex portions of the pressure ring of the present invention are not limited to the shapes shown in FIG. 1, but may be the shapes shown in FIGS. 6 (a) to 6 (c), for example. .
【００２２】[0022]
【発明の効果】以上に説明したように本発明の圧力リン
グによれば、特殊合い口構造を有する圧力リングにおけ
る合い口部の耐折損性を向上させることができる。As described above, according to the pressure ring of the present invention, it is possible to improve the breakage resistance of the mating portion in the pressure ring having the special mating structure.
【図１】本発明の圧力リングの特殊合い口構造を示す斜
視図図である。FIG. 1 is a perspective view showing a special fitting structure of a pressure ring of the present invention.
【図２】図１の正面図である。FIG. 2 is a front view of FIG.
【図３】ラップ長さとオイル消費量の関係を示すグラフ
である。FIG. 3 is a graph showing the relationship between lap length and oil consumption.
【図４】本発明の圧力リングの特殊合い口構造部分の断
面図である。FIG. 4 is a cross-sectional view of a special joint structure portion of the pressure ring of the present invention.
【図５】断面係数と耐折損強度の関係を示すグラフであ
る。FIG. 5 is a graph showing the relationship between the section modulus and the breakage strength.
【図６】圧力リングの特殊合い口構造の他の態様を示す
斜視図図である。FIG. 6 is a perspective view showing another aspect of the special fitting structure of the pressure ring.
【図７】従来の圧力リングの特殊合い口構造部分の断面
図である。FIG. 7 is a cross-sectional view of a special fitting structure portion of a conventional pressure ring.
１…圧力リング ２…一方の合い口端部 ２ａ…切欠凸部 ３…他方の合い口端部 ３ａ…切欠凹部 ４…ピストンリングの外周面 ５…耐摩耗性被膜 DESCRIPTION OF SYMBOLS 1 ... Pressure ring 2 ... One abutment end 2a ... Notch convex part 3 ... The other abutment end 3a ... Notch concave part 4 ... Piston ring outer peripheral surface 5 ... Wear resistant coating
Claims (3)
方の合い口端部に切欠凸部を設けるとともに、他方の合
い口端部に前記切欠凸部と係合する形状の切欠凹部を設
けてなる特殊合い口構造の圧力リングにおいて、 シリンダの内周面と当接するピストンリングの外周面に
厚さ３〜３０μｍの耐摩耗性被膜を形成したことを特徴
とする圧力リング。1. A piston ring for an internal combustion engine, wherein a notch convex portion is provided at one of the mating end portions, and a notch concave portion having a shape that engages with the notch convex portion is provided at the other mating end portion. In the pressure ring having the special contact structure, the pressure ring is characterized in that a wear-resistant coating having a thickness of 3 to 30 μm is formed on the outer peripheral surface of the piston ring that abuts the inner peripheral surface of the cylinder.
ング法、スパッタ法、真空蒸着法、または化学的蒸着法
によって形成された被膜であることを特徴とする請求項
１記載の圧力リング。2. The pressure ring according to claim 1, wherein the wear resistant coating is a coating formed by an ion plating method, a sputtering method, a vacuum vapor deposition method, or a chemical vapor deposition method.
Ｎ，ＴｉＮ，Ｔｉ／ＴｉＮ，ＴａＮ，ＺｒＮ，ＴｉＣ，
ＴａＣ，ＳｉＣまたはＴａ2 Ｏ5 であることを特徴とす
る請求項１または２記載の圧力リング。3. The wear resistant coating is Cr—N, Cr 2
N, TiN, Ti / TiN, TaN, ZrN, TiC,
Pressure ring according to claim 1 or 2, characterized in that it is TaC, SiC or Ta 2 O 5 .
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29071593A JPH07139631A (en) | 1993-11-19 | 1993-11-19 | Pressure ring |
| GB9422513A GB2284037B (en) | 1993-11-19 | 1994-11-08 | Piston ring |
| DE19944441136 DE4441136A1 (en) | 1993-11-19 | 1994-11-18 | Pressure ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29071593A JPH07139631A (en) | 1993-11-19 | 1993-11-19 | Pressure ring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07139631A true JPH07139631A (en) | 1995-05-30 |
Family
ID=17759587
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP29071593A Pending JPH07139631A (en) | 1993-11-19 | 1993-11-19 | Pressure ring |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH07139631A (en) |
| DE (1) | DE4441136A1 (en) |
| GB (1) | GB2284037B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007182996A (en) * | 1995-05-31 | 2007-07-19 | Ntn Corp | Seal ring |
| JP2010519468A (en) * | 2007-02-17 | 2010-06-03 | フェデラル−モーグル ブルシャイト ゲゼルシャフト ミット ベシュレンクテル ハフツング | piston ring |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100467112B1 (en) * | 1999-10-29 | 2005-01-24 | 닛폰 피스톤 린구 가부시키가이샤 | Combination of cylinder liner and piston ring of internal combustion engine |
| DE10011917C2 (en) * | 2000-03-11 | 2003-06-18 | Federal Mogul Burscheid Gmbh | Piston ring with wear protection layer and wear protection layer for a piston ring |
| DE10207078B4 (en) | 2002-02-20 | 2004-02-12 | Federal-Mogul Burscheid Gmbh | Piston ring with a PVD coating |
| DE102006046915C5 (en) * | 2006-10-04 | 2015-09-03 | Federal-Mogul Burscheid Gmbh | Piston ring for internal combustion engines |
| DE102006046917C5 (en) * | 2006-10-04 | 2014-03-20 | Federal-Mogul Burscheid Gmbh | Piston ring for internal combustion engines |
| DE102017104221A1 (en) | 2017-03-01 | 2018-09-06 | Federal-Mogul Burscheid Gmbh | piston ring |
| DE202020003862U1 (en) | 2020-09-11 | 2021-12-14 | Bümach Engineering lnternational B.V. | piston ring |
| EP4211372A1 (en) * | 2020-09-11 | 2023-07-19 | Bümach Engineering International B.V. | Piston ring |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1069448B (en) * | 1953-11-16 | 1959-11-19 | MetallgeseMschaft Aktiengesellschaft, Frankfurt/M | Gears |
| GB1222072A (en) * | 1967-04-12 | 1971-02-10 | Wellworthy Ltd | Improvements in or relating to sealing rings |
| US4256318A (en) * | 1980-04-28 | 1981-03-17 | Sealed Power Corporation | Piston ring |
| DE3305920A1 (en) * | 1982-03-12 | 1983-09-22 | Dana Corp., 43615 Toledo, Ohio | PISTON RING |
| JPH04362370A (en) * | 1991-06-04 | 1992-12-15 | Riken Corp | Compression ring for internal combustion engine |
-
1993
- 1993-11-19 JP JP29071593A patent/JPH07139631A/en active Pending
-
1994
- 1994-11-08 GB GB9422513A patent/GB2284037B/en not_active Expired - Fee Related
- 1994-11-18 DE DE19944441136 patent/DE4441136A1/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007182996A (en) * | 1995-05-31 | 2007-07-19 | Ntn Corp | Seal ring |
| JP2010519468A (en) * | 2007-02-17 | 2010-06-03 | フェデラル−モーグル ブルシャイト ゲゼルシャフト ミット ベシュレンクテル ハフツング | piston ring |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2284037B (en) | 1996-11-20 |
| GB2284037A (en) | 1995-05-24 |
| DE4441136A1 (en) | 1995-07-20 |
| GB9422513D0 (en) | 1995-01-04 |
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