JPH06281007A - Pressure ring - Google Patents
Pressure ringInfo
- Publication number
- JPH06281007A JPH06281007A JP7243493A JP7243493A JPH06281007A JP H06281007 A JPH06281007 A JP H06281007A JP 7243493 A JP7243493 A JP 7243493A JP 7243493 A JP7243493 A JP 7243493A JP H06281007 A JPH06281007 A JP H06281007A
- Authority
- JP
- Japan
- Prior art keywords
- ring
- convex portion
- pressure ring
- mating
- piston
- 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
Description
【０００１】[0001]
【産業上の利用分野】本発明は、圧力リングに係り、特
に優れた気密性を維持しつつ耐折損性を向上せしめた圧
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 which has improved breakage resistance while maintaining excellent airtightness.
【０００２】[0002]
【従来の技術】一般に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挙げられる。2. Description of the Related Art Generally, a piston of an internal combustion engine is equipped with a pressure ring and an oil ring 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. The conventional standard piston ring combination consists of a top ring and a second ring.
A combination of three pressure rings and one oil ring in total of three piston rings can be mentioned.
【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４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. 4 has been proposed (see Japanese Utility Model Publication No. 1-221616).
【０００５】この特殊合い口構造の圧力リングは、図４
に示すように、一方の合い口端部におけるシリンダ内壁
側の隅部に切欠凹部５０を設け、他方の合い口端部に内
燃機関用ピストンに装着され更にシリンダ内に装着され
たときに切欠凹部５０に収容される凸部６０を設けてい
る。The pressure ring of this special abutment structure is shown in FIG.
As shown in FIG. 5, a notch recess 50 is provided at a corner on the inner wall side of the cylinder at one end of the notch, and a notch recess is provided at the other end of the end when the piston is mounted on the internal combustion engine piston and further mounted in the cylinder. A convex portion 60 accommodated in 50 is provided.
【０００６】[0006]
【発明が解決しようとする課題】しかしながら、図４に
示す特殊合い口構造の圧力リングは、燃焼室方向へのオ
イル上りに対する気密特性が向上しているためオイル消
費量は低減するものの、基端部が細いこと及び基端部に
大きな曲げモーメントが加わるため、凸部６０の折損の
おそれがあった。However, the pressure ring of the special mouth structure shown in FIG. 4 has improved airtightness against oil rising toward the combustion chamber, so that the oil consumption is reduced, but the base end is reduced. Since the portion is thin and a large bending moment is applied to the base end portion, there is a risk of breakage of the convex portion 60.
【０００７】そこで、本発明は上記課題を解決するため
になされたものであり、特殊合い口構造のピストンリン
グが有する優れた気密性を維持し、かつ耐折損性の向上
が図られた圧力リングを提供することを目的とする。Therefore, the present invention has been made in order to solve the above-mentioned problems, and maintains the excellent airtightness of a piston ring having a special mating structure and has improved breakage resistance. The purpose is to provide.
【０００８】[0008]
【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
の合い口端部におけるシリンダ内壁側の隅部に切欠凹部
を設け、前記切欠凹部に収容される凸部を他方の合い口
端部に設け、前記切欠凹部の合い口端面がなす受け面と
前記凸部の合い口端面がなす合せ面とを対向させるよう
にした圧力リングにおいて、前記凸部の合せ面は、その
基部から先端に向って凸部が薄肉となる方向に傾斜して
伸び、且つ、その半径方向断面形状は四角形を呈し、前
記切欠凹部は、前記凸部の補形をなして前記凸部の合せ
面と切欠凹部の受け面とが接触して構成した。In order to achieve the above object, the present invention is a piston ring for an internal combustion engine, wherein a notch concave portion is provided at a corner portion of one of the mating end portions on the cylinder inner wall side. A pressure ring in which a convex portion to be accommodated in the concave portion is provided at the other end of the mating portion, and a receiving surface formed by the mating end surface of the notched concave portion and a mating surface formed by the mating end surface of the convex portion are opposed to each other. The mating surface of the convex portion extends from the base portion toward the tip in an inclined manner in a direction in which the convex portion becomes thin, and the radial cross-sectional shape thereof is a quadrangle, and the notch concave portion is of the convex portion. A complementary shape is formed so that the mating surface of the convex portion and the receiving surface of the notched concave portion are in contact with each other.
【０００９】[0009]
【作用】圧力リングは、ピストンのリング溝に装着され
更にシリンダ内に装着された状態では、図１（Ｂ）に示
すようになる。この状態では、ピストンの上下動に応じ
て、凸部１２の合い口端部の上下方向に力が作用する。
しかし、凸部１２の基端部は太いので、凸部１２が折損
することがない。しかも、合せ面において、接触状態に
なった場合、周方向及び半径方向に接触力が分散するた
め、曲げモーメントが小さくなり耐折損性が向上する。When the pressure ring is mounted in the ring groove of the piston and further mounted in the cylinder, it becomes as shown in FIG. 1 (B). In this state, a force acts in the up-down direction of the mating end portion of the convex portion 12 according to the vertical movement of the piston.
However, since the base end portion of the convex portion 12 is thick, the convex portion 12 is not broken. Moreover, when the mating surfaces come into contact with each other, the contact force is dispersed in the circumferential direction and the radial direction, so that the bending moment is reduced and the breakage resistance is improved.
【００１０】[0010]
【実施例】以下、本発明を図示の実施例に基づいて説明
する。第１実施例 図１（Ａ）〜（Ｃ）に、第１実施例の圧力リングＲ1 の
斜視図，正面図，IC-IC 線方向から見た縦断面図を示
す。The present invention will be described below with reference to the illustrated embodiments. First Embodiment FIGS. 1 (A) to 1 (C) show a perspective view, a front view, and a vertical sectional view taken along the line IC-IC of a pressure ring R 1 according to the first embodiment.
【００１１】図１（Ａ）〜（Ｃ）に示すように、本実施
例の圧力リングＲ1 の合い口部は、一方の合い口端部１
におけるシリンダ内壁側の側面３の隅部に切欠凹部２が
設けられると共に、他方の合い口端部１１に内燃機関用
ピストンのリング溝３１に装着され更にシリンダ内に装
着されたときに前記切欠凹部２に収容される凸部１２が
設けられている。As shown in FIGS. 1 (A) to 1 (C), the abutment portion of the pressure ring R 1 of the present embodiment is one abutment end portion 1
A notch recess 2 is provided at a corner of a side surface 3 on the cylinder inner wall side, and the notch recess is provided when the other end part 11 is mounted in a ring groove 31 of a piston for an internal combustion engine and further mounted in the cylinder. 2 is provided with a protrusion 12.
【００１２】前記凸部１２のリング周方向の断面形状
は、基端部側が長く先端部側が短い台形をなし、前記凸
部１２のリング半径方向の断面形状は矩形をなしてい
る。そして、該凸部１２の合せ面１３は、先端部側から
基端部側に向けて下り勾配の斜面を形成している。The cross-sectional shape of the convex portion 12 in the ring circumferential direction is a trapezoid whose base end side is long and whose tip end side is short, and the cross-sectional shape of the convex portion 12 in the ring radial direction is rectangular. The mating surface 13 of the convex portion 12 forms a slope having a downward slope from the tip end side toward the base end side.
【００１３】前記切欠凹部２には、前記合せ面１３に対
応した受け面４が形成され、該受け面４の先端部側から
奥方に向けて上り勾配の斜面が形成されている。即ち、
前記切欠凹部２の受け面４は、前記凸部１２の合せ面１
３の補形をなしている。A receiving surface 4 corresponding to the mating surface 13 is formed in the cutout recess 2, and an upward slope is formed from the tip end side of the receiving surface 4 toward the inner side. That is,
The receiving surface 4 of the cutout concave portion 2 is the mating surface 1 of the convex portion 12.
It is a complement of 3.
【００１４】そして、シリンダ内でのピストンの往復運
動に伴う圧力リングの摺動時には、圧力リングは、図１
（Ｂ）に示す状態になる。ここに、符号３１ａ，３１ｂ
は前記リング溝３１の側壁である。前記図１（Ｂ）に示
した状態で、前記凸部１２の合せ面１３と切欠凹部２の
受け面４とが当接されるが、前記凸部１２の基端部は太
いので、凸部１２が折損することがない。しかも、合せ
面において、接触状態になった場合、周方向及び半径方
向に接触力が分散するため、曲げモーメントが小さくな
り耐折損性が向上する。第２実施例 図２（Ａ）〜（Ｃ）に示すように、第２実施例の圧力リ
ングＲ2 は、凸部１２Ａのリング周方向の断面形状は、
基端部側が長く先端部側が短い台形であり、凸部１２Ａ
のリング半径方向の断面形状は上辺の長い台形である。
そして、凸部１２Ａの下面が第１合せ面１３Ａ1 をな
し、斜面が第２合せ面１３Ａ2 をなしている。即ち、リ
ング半径方向の断面形状は、台形のリングの半径方向内
側の一辺１３ＡＡが、リングの側面に対応する辺のリン
グ半径方向内側端１３ＡＡ1 からシリンダ内壁面に向い
傾斜している。また、切欠凹部２Ａは、前記第１合せ面
１３Ａ1 に対応した第１受け面４Ａ1 と、前記第２合せ
面１３Ａ2 に対応する第２受け面４Ａ2 とからなる。When the pressure ring slides due to the reciprocating motion of the piston in the cylinder, the pressure ring moves as shown in FIG.
The state shown in FIG. Here, reference numerals 31a and 31b
Is a side wall of the ring groove 31. In the state shown in FIG. 1 (B), the mating surface 13 of the convex portion 12 and the receiving surface 4 of the notched concave portion 2 are in contact with each other, but since the base end portion of the convex portion 12 is thick, the convex portion 12 does not break. Moreover, when the mating surfaces come into contact with each other, the contact force is dispersed in the circumferential direction and the radial direction, so that the bending moment is reduced and the breakage resistance is improved. Second Embodiment As shown in FIGS. 2A to 2C, in the pressure ring R 2 of the second embodiment, the cross-sectional shape of the convex portion 12A in the ring circumferential direction is:
It has a trapezoidal shape with a long proximal end and a short distal end.
The cross-sectional shape of the ring in the radial direction is a trapezoid with a long upper side.
The lower surface of the convex portion 12A forms the first mating surface 13A 1 and the inclined surface forms the second mating surface 13A 2 . That is, the ring radial cross-sectional shape, the radially inner side 13AA trapezoidal ring is inclined toward the cylinder inner wall surface of the ring radially inner end 13AA 1 side corresponding to the side surface of the ring. The cutout recess 2A includes a first receiving surface 4A 1 corresponding to the first mating surface 13A 1 and a second receiving surface 4A 2 corresponding to the second mating surface 13A 2 .
【００１５】そして、圧力リングＲ2 がピストンに装着
され、更にシリンダに装着された場合には、前記凸部１
２Ａの第１合せ面１３Ａ1 と切欠凹部２Ａの第１受け面
４Ａ 1 とが当接され、前記凸部１２Ａの第２合せ面１３
Ａ2 と切欠凹部２Ａの第２受け面４Ａ2 とが当接される
が、凸部１２Ａの基端部が太いので、凸部１２Ａが折損
することがない。また、合せ面と受け面との接触面が大
きいので、密封性が向上する。しかも、合せ面におい
て、接触状態になった場合、周方向及び半径方向に接触
力が分散するため、曲げモーメントが小さくなり耐折損
性が向上する。第３実施例 図３（Ａ）〜（Ｃ）に示すように、第３実施例の圧力リ
ングＲ3 は、凸部１２Ｂのリング周方向の断面形状は、
基端部側が長く先端部側が短い台形であり、凸部１２Ｂ
のリング半径方向の断面形状は、上辺の短い台形であ
り、下面が第１合せ面１３Ｂ1 をなし、斜面が第２合せ
面１３Ｂ2 をなしている。即ち、凸部１２Ｂのリング半
径方向の断面形状は、台形のリングの半径方向内側の一
辺１３ＢＢが、リングの側面に対応する辺のリング半径
方向内側端１３ＢＢ1 からシリンダ内壁面に向い傾斜し
ている。また、切欠凹部２Ｂは、前記第１合せ面１３Ｂ
1 に対応した第１受け面４Ｂ1 と、前記第２合せ面１３
Ｂ2 に対応する第２受け面４Ｂ2 とからなる。The pressure ring R2Attached to the piston
When it is mounted on the cylinder, the projection 1
2A first mating surface 13A1And the first receiving surface of the cutout recess 2A
4A 1Are brought into contact with each other, and the second mating surface 13 of the convex portion 12A
A2And the second receiving surface 4A of the notch recess 2A2And are abutted
However, since the base end of the protrusion 12A is thick, the protrusion 12A is broken.
There is nothing to do. Also, the contact surface between the mating surface and the receiving surface is large.
Because of the size, the sealing performance is improved. Moreover, it has a mating surface
Contact, it will make contact in the circumferential and radial directions.
Since the force is dispersed, the bending moment is reduced and the breakage resistance is increased.
The property is improved.Third embodiment As shown in FIGS. 3A to 3C, the pressure relief of the third embodiment is
Ngu R3Is the cross-sectional shape of the convex portion 12B in the ring circumferential direction,
It has a trapezoidal shape with a long base end side and a short tip end side.
The cross-sectional shape of the ring in the radial direction is a trapezoid with a short upper side.
The lower surface is the first mating surface 13B1The slope is the second match
Surface 13B2Is doing. That is, the ring half of the convex portion 12B
The radial cross-section is one inside the trapezoidal ring in the radial direction.
Side 13BB is the ring radius of the side corresponding to the side surface of the ring
Direction inner end 13BB1To the inner wall surface of the cylinder
ing. In addition, the notch recess 2B has the first mating surface 13B.
1First receiving surface 4B corresponding to1And the second mating surface 13
B2Second receiving surface 4B corresponding to2Consists of.
【００１６】そして、圧力リングＲ3 がピストンに装着
され、更にシリンダに装着された場合には、前記凸部１
２Ｂの第１合せ面１３Ｂ1 と切欠凹部２Ｂの第１受け面
４Ｂ 1 とが当接され、前記凸部１２Ｂの第２合せ面１３
Ｂ2 と切欠凹部２Ｂの第２受け面４Ｂ2 とが当接される
が、凸部１２Ｂの基端部が太いので、凸部１２Ｂが折損
することがない。また、合せ面と受け面との接触面が大
きいので、密封性が向上する。しかも、合せ面におい
て、接触状態になった場合、周方向及び半径方向に接触
力が分散するため、曲げモーメントが小さくなり耐折損
性が向上する。The pressure ring R3Attached to the piston
When it is mounted on the cylinder, the projection 1
2B first mating surface 13B1And the first receiving surface of the cutout recess 2B
4B 1Are brought into contact with each other, and the second mating surface 13 of the convex portion 12B
B2And the second receiving surface 4B of the cutout recess 2B2And are abutted
However, since the base end of the protrusion 12B is thick, the protrusion 12B is broken.
There is nothing to do. Also, the contact surface between the mating surface and the receiving surface is large.
Because of the size, the sealing performance is improved. Moreover, it has a mating surface
Contact, it will make contact in the circumferential and radial directions.
Since the force is dispersed, the bending moment is reduced and the breakage resistance is increased.
The property is improved.
【００１７】[0017]
【発明の効果】以上に説明したように、本発明によれ
ば、圧力リングをピストンに装着し更にシリンダに装着
した場合に、対向配置された凸部と切欠凹部とが当接さ
れても、凸部の基端部が太いので、凸部が折損すること
がない。As described above, according to the present invention, when the pressure ring is mounted on the piston and further mounted on the cylinder, even if the convex portion and the notched concave portion, which are arranged to face each other, come into contact with each other, Since the base end portion of the convex portion is thick, the convex portion does not break.
【図１】本発明の第１実施例の合い口部を示す部分説明
図であって、（Ａ）は斜視図、（Ｂ）は正面図、（Ｃ）
はIC-IC 線に沿う縦断面図である。FIG. 1 is a partial explanatory view showing a joint portion of a first embodiment of the present invention, in which (A) is a perspective view, (B) is a front view, and (C).
Is a vertical sectional view taken along the line IC-IC.
【図２】本発明の第２実施例の合い口部を示す部分説明
図であって、（Ａ）は斜視図、（Ｂ）は正面図、（Ｃ）
はIIC-IIC 線に沿う縦断面図である。2A and 2B are partial explanatory views showing a mating portion of a second embodiment of the present invention, in which FIG. 2A is a perspective view, FIG. 2B is a front view, and FIG.
Is a vertical sectional view taken along line IIC-IIC.
【図３】本発明の第３実施例の合い口部を示す部分説明
図であって、（Ａ）は斜視図、（Ｂ）は正面図、（Ｃ）
はIIIC-IIIC 線に沿う縦断面図である。3A and 3B are partial explanatory views showing a mating portion of a third embodiment of the present invention, in which FIG. 3A is a perspective view, FIG. 3B is a front view, and FIG.
FIG. 3 is a vertical sectional view taken along line IIIC-IIIC.
【図４】従来の合い口構造を示す斜視図である。FIG. 4 is a perspective view showing a conventional abutment structure.
Ｒ…圧力リング １…一方の合い口端部 ２…切欠凹部 ４…受け面 １１…他方の合い口端部 １２…凸部 １３…合せ面 R ... Pressure ring 1 ... One of the mating end portions 2 ... Notched concave portion 4 ... Receiving surface 11 ... The other mating end portion 12 ... Convex portion 13 ... Mating surface
Claims (3)
方の合い口端部におけるシリンダ内壁側の隅部に切欠凹
部を設け、前記切欠凹部に収容される凸部を他方の合い
口端部に設け、前記切欠凹部の合い口端面がなす受け面
と前記凸部の合い口端面がなす合せ面とを対向させるよ
うにした圧力リングにおいて、 前記凸部の合せ面は、その基部から先端に向って凸部が
薄肉となる方向に傾斜して伸び、且つ、その半径方向断
面形状は四角形を呈し、前記切欠凹部は、前記凸部の補
形をなして前記凸部の合せ面と切欠凹部の受け面とが接
触している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 concave portion is provided at a corner portion on the cylinder inner wall side at one of the mating end portions, and a convex portion accommodated in the notch concave portion is provided at the other mating end portion. In the pressure ring, wherein the receiving surface formed by the mating end surface of the notched concave portion and the mating surface formed by the mating end surface of the convex portion are opposed to each other, the mating surface of the convex portion extends from the base to the tip. And the convex portion extends in a direction in which the convex portion becomes thin, and has a quadrangular cross-sectional shape in the radial direction, and the notched concave portion is a complementary shape of the convex portion, A pressure ring characterized by being in contact with the receiving surface.
が、リングの半径方向内側からシリンダ内壁面に向い傾
斜してい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 a side surface of the ring of the convex portion on a radially inner side is inclined from a radially inner side of the ring toward a cylinder inner wall surface.
が、リングの半径方向内側からリング中心方向に向い傾
斜していることを特徴とする請求項１記載の圧力リン
グ。3. The pressure ring according to claim 1, wherein a side surface of the convex portion on the inner side in the radial direction of the ring is inclined from the inner side in the radial direction of the ring toward the center of the ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7243493A JPH06281007A (en) | 1993-03-30 | 1993-03-30 | Pressure ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7243493A JPH06281007A (en) | 1993-03-30 | 1993-03-30 | Pressure ring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06281007A true JPH06281007A (en) | 1994-10-07 |
Family
ID=13489199
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7243493A Pending JPH06281007A (en) | 1993-03-30 | 1993-03-30 | Pressure ring |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06281007A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007182996A (en) * | 1995-05-31 | 2007-07-19 | Ntn Corp | Seal ring |
| CN102844596A (en) * | 2011-04-20 | 2012-12-26 | 丰田自动车株式会社 | Seal structure |
| WO2017186905A1 (en) * | 2016-04-28 | 2017-11-02 | Poclain Hydraulics Industrie | Disengageable hydraulic machine and vehicle provided with such a machine |
-
1993
- 1993-03-30 JP JP7243493A patent/JPH06281007A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007182996A (en) * | 1995-05-31 | 2007-07-19 | Ntn Corp | Seal ring |
| CN102844596A (en) * | 2011-04-20 | 2012-12-26 | 丰田自动车株式会社 | Seal structure |
| CN102844596B (en) * | 2011-04-20 | 2014-09-03 | 丰田自动车株式会社 | Seal structure |
| US8876116B2 (en) | 2011-04-20 | 2014-11-04 | Toyota Jidosha Kabushiki Kaisha | Sealing structure |
| WO2017186905A1 (en) * | 2016-04-28 | 2017-11-02 | Poclain Hydraulics Industrie | Disengageable hydraulic machine and vehicle provided with such a machine |
| FR3050773A1 (en) * | 2016-04-28 | 2017-11-03 | Poclain Hydraulics Ind | DEGRASABLE HYDRAULIC MACHINE AND VEHICLE EQUIPPED WITH SUCH A MACHINE |
| FR3050774A1 (en) * | 2016-04-28 | 2017-11-03 | Poclain Hydraulics Ind | DEGRASABLE HYDRAULIC MACHINE AND VEHICLE EQUIPPED WITH SUCH A MACHINE |
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