JPH0678787B2 - Annular sealing body - Google Patents
Annular sealing bodyInfo
- Publication number
- JPH0678787B2 JPH0678787B2 JP62043764A JP4376487A JPH0678787B2 JP H0678787 B2 JPH0678787 B2 JP H0678787B2 JP 62043764 A JP62043764 A JP 62043764A JP 4376487 A JP4376487 A JP 4376487A JP H0678787 B2 JPH0678787 B2 JP H0678787B2
- Authority
- JP
- Japan
- Prior art keywords
- coil spring
- sealing piece
- trunk
- sealing
- seal
- 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.)
- Expired - Fee Related
Links
Landscapes
- Sealing With Elastic Sealing Lips (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 この発明は、往復圧縮装置等に用いられるピストンとシ
リンダ間のシール構造に関する。Description: TECHNICAL FIELD The present invention relates to a seal structure between a piston and a cylinder used in a reciprocating compression device and the like.
スターリング機関や医療用に用いられる往復圧縮装置の
ピストンの接触式シールは潤滑油による作動流体の汚染
を防止するために無潤滑で用いられる。この種の接触式
シールとしてコイルばねを内包してそのばね力によって
シールの面圧を与えるものが用いられる。これは金属性
のコイルばねがシール材料そのものよりばね定数の温度
の影響が少ないこと、コイルばねが小さいばね定数を与
え得ること、荷重−たわみ特性の線形性が良好であるな
ど種々の利点をもつためである。このようなコイルばね
を用いて環状の封止体として構成した接触式シールの断
面図を第２図に示す。The contact type seal of the piston of a reciprocating compressor used for Stirling engines and medical applications is used without lubrication to prevent the working fluid from being contaminated by lubricating oil. As this type of contact-type seal, one that includes a coil spring and applies a surface pressure of the seal by the spring force is used. This has various advantages such that the metallic coil spring is less affected by the temperature of the spring constant than the sealing material itself, the coil spring can give a small spring constant, and the linearity of the load-deflection characteristic is good. This is because. FIG. 2 shows a sectional view of a contact type seal formed as an annular sealing body using such a coil spring.
第２図において環状封止体としてのシールリング１は、
円環状の幹体としてのウェブ２とシリンダ５および保持
体としてのピストン６の溝９に保持される封止片として
のシールリップ3,4とから成り、横断面形状がコの字形
の円環状をなしてあらかじめ設定された半径方向のたわ
みを与えられて保持体としてのピストン６の溝９に装着
されている。In FIG. 2, the seal ring 1 as an annular sealing body is
It is composed of a web 2 as an annular trunk body, a seal lip 3, 4 as a sealing piece held in a groove 9 of a cylinder 5 and a piston 6 as a holding body, and has a U-shaped cross section. It is mounted in the groove 9 of the piston 6 as a holding body by being given a predetermined radial deflection.
一対のシールリップ3,4の互いに対向する面内すなわち
前記のコの字形部分には例えば線材又は薄板材によって
作られた前述の円環に沿う中心軸をもつコイルばね７が
内包され該シールリップ3,4をそれぞれ保持体としての
ピストン６の溝９と、保持体と相対的に移動する移動面
８としてのシリンダ５の内面とに接触させて、シールす
る力を与えるようになっている。A coil spring 7 having a central axis along the above-mentioned circular ring made of, for example, a wire rod or a thin plate member is included in the mutually opposing surfaces of the pair of seal lips 3 and 4, that is, the U-shaped portion. 3 and 4 are respectively brought into contact with the groove 9 of the piston 6 serving as a holding body and the inner surface of the cylinder 5 serving as a moving surface 8 that moves relatively to the holding body, and a sealing force is applied.
また、前記シールリップ3,4には、互いに対向する面の
先端部に突起部10,11がそれぞれ設けられ、これら突起
部10,11と前記シールリング１のウェブ２によって、前
記コイルばね７の保持がなされている。Further, the seal lips 3 and 4 are provided with protrusions 10 and 11 respectively at the tips of the surfaces facing each other, and the protrusions 10 and 11 and the web 2 of the seal ring 1 cause the coil spring 7 to move. Has been held.
シールリング１は、摩耗係数が小さくて可撓性の大きい
例えば、充填材入り４フッ化エチレン樹脂で一体的に構
成され、コイルばね７は、ステンレス鋼，ハステロイ，
インコネルなどのばね性のある金属材料で構成されてい
る。The seal ring 1 is integrally formed of, for example, a filler-containing tetrafluoroethylene resin having a small wear coefficient and high flexibility, and the coil spring 7 is made of stainless steel, Hastelloy,
It is made of a metallic material having a spring property such as Inconel.
接触式シールの寿命時間Ｔ（hr）は一般に次式によって
与えられる。The life time T (hr) of a contact type seal is generally given by the following equation.
ここでR,K,P,Vはそれぞれ摩耗可能量（m3），材料によ
って定まる摩耗係数（cm3・min/kg f・ｍ・ｈ），シー
ル面圧（kg f/cm2），滑り速度（m/min）である。すな
わちシールの寿命時間Ｔを長くするためには、Ｒを大
に、K,P,Vを小にする対策が必要である。ここでシール
面圧Ｐは下記の各寄与分によって与えられる。 Here, R, K, P and V are wearable amount (m 3 ), wear coefficient determined by material (cm 3 · min / kg f · m · h), seal surface pressure (kg f / cm 2 ), slippage Speed (m / min). That is, in order to increase the life time T of the seal, it is necessary to take measures to increase R and decrease K, P and V. Here, the sealing surface pressure P is given by the following contributions.
Ｐ＝P1＋P2＋P3 （２） P1はばね力による面圧寄与分，P2はシールリングの剛性
による面圧寄与分，P3は差圧による面圧寄与分である。
（１）（２）においてR,K,V,P3はあらかじめ定めること
のできる量である。したがってＴを大にするにはP1＋P2
すなわちばね力とシールリングの剛性による面圧寄与分
の和をシール性を保ち得る範囲でできるだけ小さくし、
シールに必要な面圧をもっぱら差圧によって与える必要
がある。P = P 1 + P 2 + P 3 (2) P 1 is the surface pressure contribution due to the spring force, P 2 is the surface pressure contribution due to the rigidity of the seal ring, and P 3 is the surface pressure contribution due to the differential pressure.
In (1) and (2), R, K, V and P 3 are quantities that can be determined in advance. Therefore, to increase T, P 1 + P 2
That is, the sum of the surface pressure contributions due to the spring force and the rigidity of the seal ring is made as small as possible within the range where the sealability can be maintained,
It is necessary to apply the surface pressure required for the seal exclusively by the differential pressure.
ところで第２図の構成においては、シールリップ3,4の
先端部に突起部10,11をそれぞれ設けてあるのでシール
リップ先端部の肉厚が摩耗に関与する中間部12および中
間部13にくらべて厚くなり、突起部10,11を環状体とし
てみたとき、その剛性がいずれも大きくなり、半径方向
にたわませるのに大きな力を必要とする。このためシー
ルリップ３とシリンダ５との接触部の面圧特に突起部10
の接触部の面圧が大になる。これを避けて突起部10の外
径を小さめにとるとはやはり剛性が大であるために逆に
シール性を損なうおそれを生ずるという問題がある。By the way, in the configuration of FIG. 2, since the projections 10 and 11 are provided at the tips of the seal lips 3 and 4, respectively, the thickness of the tip of the seal lips is different from that of the intermediate portion 12 and the intermediate portion 13 which are involved in wear. When the projections 10 and 11 are viewed as annular bodies, their rigidity becomes large and a large force is required to bend them in the radial direction. Therefore, the contact pressure between the seal lip 3 and the cylinder 5, especially the protrusion 10
The surface pressure of the contact part of becomes large. If the outer diameter of the protrusion 10 is made smaller by avoiding this, the rigidity is still high, and conversely there is a problem that the sealing performance may be impaired.
また、シールリップ３が摩耗して、ばね力によってシー
ルリップ３を半径方向に拡張してシリンダとの接触を保
たせる場合においても、コイルばね７の力とシールリッ
プ３の剛性による力とが打消し合って前述のようにP1＋
P2をほぼ０にすることが望ましいが、温度などの周囲環
境やシールリップ３の摩耗状態によって突起部10の剛性
が変化するので、ばね力は、突起部10の比較的大きな初
期剛性に合わせて選定することになり、摩耗や温度変化
などに対してはばね力とシールリップ剛性による力の差
が生じる。この力の差は突起部10を含むシールリップ３
の剛性が大きい程大きくなり、この力によってシール面
圧を大きくしてしまうという問題もあった。In addition, even when the seal lip 3 is worn and the seal lip 3 is expanded in the radial direction by the spring force to keep contact with the cylinder, the force of the coil spring 7 and the force due to the rigidity of the seal lip 3 cancel each other out. As we mentioned above, P 1 +
Although it is desirable to set P 2 to almost 0, the rigidity of the protrusion 10 changes depending on the surrounding environment such as temperature and the wear state of the seal lip 3, so that the spring force is adjusted to a relatively large initial rigidity of the protrusion 10. Therefore, there is a difference between the spring force and the seal lip rigidity with respect to wear and temperature changes. This force difference is due to the seal lip 3 including the protrusion 10.
There is also a problem in that the greater the rigidity of, the greater the rigidity, and this force increases the sealing surface pressure.
さらに、コイルばね７の荷重が作用する点（荷重点）
は、第２図において矢印で示すように、コイルばね７の
軸心付近にあり、突起部10の剛性の変化の影響を受ける
ので、シリンダ５とシールリップ３の接触面に作用する
力のばらつきが大きくなるという問題もあった。Furthermore, the point where the load of the coil spring 7 acts (load point)
Is near the axial center of the coil spring 7 as shown by the arrow in FIG. 2 and is affected by the change in the rigidity of the protrusion 10, so that the variation in the force acting on the contact surface between the cylinder 5 and the seal lip 3 There was also the problem that
この発明は、上記の問題点を解決するためになされたも
ので、移動面側の封止片の摩耗に関与する部分の肉厚を
減少させることなく、封止片の剛性によるシール面圧寄
与分と、コイルばねによるシール面圧寄与を減少させる
とともに、これらが摩耗や温度変化の影響を受けぬよう
にして、シール寿命を延長させると同時にシール摩擦に
よる損失を小さくすることを目的とする。The present invention has been made to solve the above problems, and contributes to the sealing surface pressure due to the rigidity of the sealing piece without reducing the thickness of the portion of the moving surface that is involved in wear of the sealing piece. It is intended to reduce the contribution of the seal surface pressure by the coil spring and to prevent them from being affected by wear and temperature change, thereby extending the life of the seal and reducing the loss due to the seal friction.
上記の目的を達成するために、本発明によれば、 シリンダおよびピストンのいずれか一方を保持体とし、
円環状の幹体の内周部と外周部とにそれぞれ一方が保持
体側に他方がその保持体と相対的に移動する移動面側に
配された封止片を備えたコの字形の断面を持ち、そのコ
の字形部分に前記円環に沿う中心軸を持つコイルばねを
内包して前記封止片をそれぞれ前記保持体および移動面
に圧着してシリンダ内面およびピストン外面の間の空間
の流体を封止する可撓材料より成る封止体において、 移動面側の封止片は、前記コイルばねとの接触箇所と幹
体に設けられた薄肉部のコイルばね側の面との距離Ｌを
超え且つコイルばねの反幹体側に達しない長さと、前記
接触箇所近傍の領域において一定となる厚みを有し、 保持体側の封止片は、一部を幹体の厚肉部により設けら
れた前記コイルばねを収容する溝を有し、 て成るものとする。In order to achieve the above object, according to the present invention, one of a cylinder and a piston is a holding body,
A U-shaped cross-section with a sealing piece arranged on the inner peripheral portion and the outer peripheral portion of the annular trunk body, one on the side of the holding body and the other on the side of the moving surface that moves relatively to the holding body. A coil spring having a central axis along the circular ring in its U-shaped portion, and the sealing pieces are crimped to the holding body and the moving surface, respectively, and the fluid in the space between the cylinder inner surface and the piston outer surface is held. In the sealing body made of a flexible material for sealing the moving surface side, the sealing piece on the moving surface side has a distance L between the contact point with the coil spring and the surface of the thin portion provided on the trunk body on the coil spring side. The length that exceeds the length and does not reach the side opposite the trunk of the coil spring, and has a constant thickness in the region near the contact point, and the sealing piece on the holder side is partially provided by the thick part of the trunk. A groove for accommodating the coil spring is provided.
移動面側の封止片には、コイルばねの反幹体側に達しな
い長さしか与えられていないので、封止片は移動面にコ
イルばねの荷重点近傍において接触するようになる。ま
た封止片の厚みが、接触箇所近傍の領域で一定であっ
て、特に剛性の高い部分を持たない。しかも封止片に連
なる部分の幹体の厚みを減少し薄肉部としているので、
封止片の取り付け部の剛性も小さい。従って、封止片の
剛性は極めて小となり、封止片を移動面に押しつける力
はコイルばねの撓み力のみで与えられ、封止片の磨耗に
よる厚みの変化、温度変化による幹体と封止片の剛性変
化は力に殆ど影響を及ぼさなくなる。しかも上述のよう
に、封止片がコイルばねの荷重点において移動面に接触
しているので、コイルばねの撓み力がそのまま接触部の
面圧を定めることとなり、所定の面圧を与えることが容
易となる。Since the length of the sealing piece on the moving surface side does not reach the side opposite the trunk of the coil spring, the sealing piece comes into contact with the moving surface in the vicinity of the load point of the coil spring. In addition, the thickness of the sealing piece is constant in the area near the contact point and does not have a particularly rigid portion. Moreover, since the thickness of the trunk body connected to the sealing piece is reduced to a thin portion,
The rigidity of the mounting portion of the sealing piece is also small. Therefore, the rigidity of the sealing piece becomes extremely small, and the force that presses the sealing piece against the moving surface is given only by the bending force of the coil spring. The change in stiffness of the piece has little effect on the force. Moreover, as described above, since the sealing piece is in contact with the moving surface at the load point of the coil spring, the bending force of the coil spring determines the surface pressure of the contact portion as it is, and a predetermined surface pressure can be applied. It will be easy.
一方、保持体側の封止片は、一部を幹体の厚肉部により
設けられたコイルばねを収容する溝を備えているので、
コイルばねはこの溝に保持される。よって、移動面側の
封止片が短くなり、突起部が無くなっても、コイルばね
が脱落することはない。On the other hand, the sealing piece on the holding body side is provided with a groove, part of which is provided with the coil spring provided by the thick portion of the trunk,
The coil spring is held in this groove. Therefore, even if the sealing piece on the moving surface side is shortened and the protrusion is removed, the coil spring does not fall off.
第１図に本発明の実施例を示す。環状封止体21としての
シールリングは幹体22としてのウェブと２個の封止片2
3,24としてのシールリップを備え、断面がコの字形に形
成され、そのコの字形の部分にコイルばね７を内包して
いる。ここで、幹体22は、削除部222により、薄肉部221
と厚肉部223とを有する。FIG. 1 shows an embodiment of the present invention. The seal ring as the annular sealing body 21 includes the web as the trunk body 22 and the two sealing pieces 2
The seal lips 3 and 24 are provided, and the cross section is formed in a U shape, and the coil spring 7 is included in the U shape part. Here, the trunk body 22 has the thin portion 221 by the deletion portion 222.
And a thick portion 223.
本実施例では、上記の環状封止体21は、保持体としての
ピストン６の溝９に保持されており、幹体22の外周部側
の封止片23が、シリンダ５の内面に接している。このシ
リンダ５の内面が、保持体としてのピストン６に対して
相対的に移動する移動面８となっている。In this embodiment, the annular sealing body 21 is held in the groove 9 of the piston 6 as a holding body, and the sealing piece 23 on the outer peripheral side of the trunk body 22 contacts the inner surface of the cylinder 5. There is. The inner surface of the cylinder 5 serves as a moving surface 8 that moves relative to the piston 6 as a holding body.
移動面８に接触する封止片23の長さは、コイルばね７と
の接触箇所231と幹体22の薄肉部221のコイルばね７側の
面との距離Ｌを超え、コイルばね７の反幹体側には達し
ない長さとなっており、もう一方の封止片24よりも短
く、その厚さはコイルばね７との接触箇所231近傍にお
いて一定にとられている。上記のように、この封止片23
に連なる部分の幹体22は薄肉部221となっている。幹体2
2のピストン６側、即ち幹体22の内周部側の封止片24
は、ピストンの溝９の幅とほぼ等しい長さを有し、一部
を幹体22の厚肉部223により設けられたコイルばね７を
収容する保持溝25が設けてあり、この溝25によりコイル
ばね７を保持する。よって、外周部の移動面側の封止片
23の長さが短くとも、コイルばね７が脱落することはな
い。The length of the sealing piece 23 that contacts the moving surface 8 exceeds the distance L between the contact point 231 with the coil spring 7 and the surface of the thin portion 221 of the trunk body 22 on the coil spring 7 side, and It has a length that does not reach the trunk side, is shorter than the other sealing piece 24, and has a constant thickness in the vicinity of the contact point 231 with the coil spring 7. As described above, this sealing piece 23
The trunk body 22 in the portion connected to is a thin portion 221. Trunk 2
Sealing piece 24 on the piston 6 side of 2, that is, on the inner peripheral side of the trunk 22
Is provided with a holding groove 25 having a length substantially equal to the width of the groove 9 of the piston and partially containing the coil spring 7 provided by the thick portion 223 of the trunk body 22. Hold the coil spring 7. Therefore, the sealing piece on the moving surface side of the outer peripheral portion
Even if the length of 23 is short, the coil spring 7 does not fall off.
上記の構成において、移動面８に接触する封止片23に
は、コイルばね７との接触箇所231と幹体の薄肉部との
距離Ｌを超え且つコイルばね７の反幹体側に達しない長
さしか与えられていない。よって、封止片23は、移動面
８にコイルばね７の荷重点近傍で接触するようになる。
従って、コイルばね７の撓み力が直接に接触部の面圧と
して伝達されるようになる。一方封止片23の厚みは、前
記の接触箇所231近傍において一定であり、従来技術の
ように剛性の高い突起部が無いため、コイルばね７が封
止片23を開こうとする力に殆ど抗しない。さらに幹体22
の封止片に連なる部分が厚みの薄い薄肉部221に形成さ
れているので、この部分の剛性も小となる。このため
（２）式におけるP2を零として差し支えなく、環状封止
体21の面圧はコイルばね７のたわみ量をあらかじめ所要
面圧を与える値に設定しておくことによって望み通りの
値を与えることが容易となる。そしてこのたわみには封
止片23の剛性と平衡させる分を考慮する必要は全くな
い。既に述べたようにこの値は接触部のシール性を保持
し得る範囲で極力小にとることとなり、このような微妙
な値をあらかじめ与えることが容易にできるようにな
る。しかも封止片23の摩耗による厚みの変化や、環境温
度変化による幹体22と封止片23の剛性の変化があって
も、封止片23の剛性がきわめて小さくなっているので、
これらの変化はコイルばね７のたわみ力によって与えら
れている接触部の面圧にほとんど影響を及ぼさなくな
る。In the above configuration, the sealing piece 23 that contacts the moving surface 8 has a length that exceeds the distance L between the contact portion 231 with the coil spring 7 and the thin portion of the trunk and does not reach the side opposite the trunk of the coil spring 7. Only given. Therefore, the sealing piece 23 comes into contact with the moving surface 8 in the vicinity of the load point of the coil spring 7.
Therefore, the bending force of the coil spring 7 is directly transmitted as the surface pressure of the contact portion. On the other hand, the thickness of the sealing piece 23 is constant in the vicinity of the contact point 231, and since there is no protrusion having high rigidity as in the prior art, the coil spring 7 has almost no force to open the sealing piece 23. Do not resist. Further trunk 22
Since the portion continuous with the sealing piece is formed in the thin portion 221, which has a small thickness, the rigidity of this portion also becomes small. Therefore, P 2 in the equation (2) can be set to zero, and the surface pressure of the annular sealing body 21 can be set to a desired value by setting the deflection amount of the coil spring 7 to a value that gives a required surface pressure in advance. It will be easy to give. Further, it is not necessary to consider the amount of the deflection balanced with the rigidity of the sealing piece 23 at all. As described above, this value is as small as possible within the range where the sealing property of the contact portion can be maintained, and it becomes possible to easily give such a delicate value in advance. Moreover, even if the thickness of the sealing piece 23 changes due to wear, or the rigidity of the trunk 22 and the sealing piece 23 changes due to environmental temperature changes, the rigidity of the sealing piece 23 is extremely small.
These changes have almost no influence on the surface pressure of the contact portion given by the bending force of the coil spring 7.
したがって環状封止体21を構成するには、まずあらかじ
め設定したたわみ分だけ外径を大きめにとったコイルば
ね７を封止片24の保持溝25中に装着する。このようにし
て外周部の封止片21の外径が前記のあらかじめ設定した
たわみ分だけ径方向の寸法が大であるような環状封止体
21を保持体としてピストン６に設けた溝９に装着する。Therefore, in order to form the annular sealing body 21, first, the coil spring 7 having an outer diameter slightly larger by the preset deflection is mounted in the holding groove 25 of the sealing piece 24. Thus, the annular sealing body is such that the outer diameter of the sealing piece 21 at the outer peripheral portion is large in the radial direction by the amount of the preset deflection.
21 is attached to the groove 9 provided in the piston 6 as a holding body.
この実施例では環状封止体21をピストン６に装着したも
のを説明したので、保持体がピストン6,移動面８がシリ
ンダ５の内面となっているが、環状封止体１をシリンダ
５に装置してシリンダ５を保持体とし、移動面８をピス
トン外面としてもよいのはもちろんである。ただしこの
場合は封止片23は内周側になり、封止片24は外周側とな
る。In this embodiment, since the annular sealing body 21 is attached to the piston 6, the holding body is the piston 6 and the moving surface 8 is the inner surface of the cylinder 5, but the annular sealing body 1 is mounted on the cylinder 5. Of course, the cylinder 5 may be used as a holder and the moving surface 8 may be the outer surface of the piston. However, in this case, the sealing piece 23 is on the inner peripheral side and the sealing piece 24 is on the outer peripheral side.
本発明によれば、上記の構成を採用した結果、封止片が
移動面に接触する箇所が環状封止体に内包されたコイル
ばねの荷重点近傍となるとともに、封止片の剛性が極め
て小となる。このため、移動面との接触部の面圧をコイ
ルばねの撓み量のみで定めることが可能となり、封止が
可能な範囲でできるだけ小さな面圧を与え得る撓み量が
予め設定できるようになる。しかも封止片の剛性が小さ
いので、封止片の磨耗や環境温度の変化によってその剛
性が変わっても、接触部の面圧はその影響を殆ど受けな
い。従って、シール寿命を延長させるとともに摩擦損失
を低減させることができる。According to the present invention, as a result of adopting the above configuration, the location where the sealing piece comes into contact with the moving surface is near the load point of the coil spring included in the annular sealing body, and the rigidity of the sealing piece is extremely high. It will be small. Therefore, the surface pressure of the contact portion with the moving surface can be determined only by the amount of bending of the coil spring, and the amount of bending that can provide the smallest possible surface pressure within the sealable range can be set in advance. Moreover, since the rigidity of the sealing piece is small, even if the rigidity of the sealing piece changes due to wear of the sealing piece or a change in the ambient temperature, the surface pressure of the contact portion is hardly affected. Therefore, the seal life can be extended and the friction loss can be reduced.
保持体側の封止片には、一部が幹体の厚肉部であるコイ
ルばねを収容する保持溝を設けて、コイルばねを脱落さ
せることなく確実に保持し、上記の効果を奏することが
できる。The holding piece-side sealing piece is provided with a holding groove for accommodating a coil spring, a part of which is the thick-walled portion of the trunk body, so that the coil spring can be securely held without falling off, and the above effect can be obtained. it can.
【図面の簡単な説明】 第１図はこの発明の実施例の断面図，第２図は従来技術
による環状封止体の断面図である。 1:シールリング（環状封止体）、2:ウェブ（幹体）、3,
4:シールリップ（封止片）、5:シリンダ、6:ピストン
（保持体）、7:コイルばね、8:移動面、21:環状封止
体、22:幹体、23,24:封止片、25:保持溝。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of an embodiment of the present invention, and FIG. 2 is a sectional view of an annular sealing body according to the prior art. 1: Seal ring (annular sealing body), 2: Web (trunk body), 3,
4: Seal lip (sealing piece), 5: Cylinder, 6: Piston (holding body), 7: Coil spring, 8: Moving surface, 21: Annular sealing body, 22: Trunk body, 23, 24: Sealing Piece 25: Retaining groove.
Claims (1)
保持体とし、円環状の幹体の内周部と外周部とにそれぞ
れ一方が保持体側に他方がその保持体と相対的に移動す
る移動面側に配された封止片を備えたコの字形の断面を
持ち、そのコの字形部分に前記円環に沿う中心軸を持つ
コイルばねを内包して前記封止片をそれぞれ前記保持体
および移動面に圧着してシリンダ内面およびピストン外
面の間の空間の流体を封止する可撓材料より成る封止体
において、 移動面側の封止片は、前記コイルばねとの接触箇所と幹
体に設けられた薄肉部のコイルばね側の面との距離Ｌを
超え且つコイルばねの反幹体側に達しない長さと、前記
接触箇所近傍の領域において一定となる厚みを有し、 保持体側の封止片は、一部を幹体の厚肉部により設けら
れた前記コイルばねを収容する溝を有し、 て成ることを特徴とする環状封止体。1. A moving surface in which one of a cylinder and a piston serves as a holding body, and one of the inner peripheral portion and the outer peripheral portion of an annular trunk body moves toward the holding body and the other moves relative to the holding body. Having a U-shaped cross-section with a sealing piece disposed on the side, and enclosing a coil spring having a central axis along the ring in the U-shaped portion, the sealing piece is respectively held by the holder and In a sealing body made of a flexible material that is pressure-bonded to the moving surface to seal the fluid in the space between the inner surface of the cylinder and the outer surface of the piston, the sealing piece on the moving surface side is the contact point with the coil spring and the trunk body. Has a length that exceeds the distance L between the thin-walled portion and the surface on the coil spring side and does not reach the side opposite the trunk of the coil spring, and has a constant thickness in the region near the contact point. The stopper is partly provided by the thick part of the trunk Annular sealing body, characterized in that a groove for accommodating the coil spring, comprising Te.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62043764A JPH0678787B2 (en) | 1987-02-26 | 1987-02-26 | Annular sealing body |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62043764A JPH0678787B2 (en) | 1987-02-26 | 1987-02-26 | Annular sealing body |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63210468A JPS63210468A (en) | 1988-09-01 |
| JPH0678787B2 true JPH0678787B2 (en) | 1994-10-05 |
Family
ID=12672822
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62043764A Expired - Fee Related JPH0678787B2 (en) | 1987-02-26 | 1987-02-26 | Annular sealing body |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0678787B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017163992A1 (en) * | 2016-03-22 | 2017-09-28 | Nok株式会社 | Sealing device |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2001001022A1 (en) * | 1999-06-29 | 2001-01-04 | Ampo, S. Coop. | Superelastic seal for liquid natural gas processing plants |
| JP2003028302A (en) * | 2001-07-16 | 2003-01-29 | Nok Corp | Sealing device |
| JP5327611B2 (en) * | 2009-03-18 | 2013-10-30 | 株式会社リコー | Cleaning device, image forming apparatus, and process cartridge |
| US10598241B2 (en) * | 2014-02-26 | 2020-03-24 | Bal Seal Engineering, Inc. | Multi deflection canted coil springs and related methods |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4655462A (en) * | 1985-01-07 | 1987-04-07 | Peter J. Balsells | Canted coiled spring and seal |
-
1987
- 1987-02-26 JP JP62043764A patent/JPH0678787B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017163992A1 (en) * | 2016-03-22 | 2017-09-28 | Nok株式会社 | Sealing device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63210468A (en) | 1988-09-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |