JPH0560247A - Noncontact type mechanical seal - Google Patents
Noncontact type mechanical sealInfo
- Publication number
- JPH0560247A JPH0560247A JP21388991A JP21388991A JPH0560247A JP H0560247 A JPH0560247 A JP H0560247A JP 21388991 A JP21388991 A JP 21388991A JP 21388991 A JP21388991 A JP 21388991A JP H0560247 A JPH0560247 A JP H0560247A
- Authority
- JP
- Japan
- Prior art keywords
- seal
- dynamic pressure
- seal surface
- dimension
- seal ring
- 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
- 238000007789 sealing Methods 0.000 claims abstract description 28
- 239000012530 fluid Substances 0.000 claims abstract description 20
- 239000003575 carbonaceous material Substances 0.000 claims abstract description 8
- 239000000470 constituent Substances 0.000 claims 1
- 230000003068 static effect Effects 0.000 abstract 2
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 210000000078 claw Anatomy 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Landscapes
- Mechanical Sealing (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、例えばガスタービン、
ブロアーあるいはエアコンプレッサーなどの高圧流体機
器の軸封部に適用される非接触形メカニカルシールに関
するものである。BACKGROUND OF THE INVENTION The present invention relates to, for example, a gas turbine,
The present invention relates to a non-contact type mechanical seal applied to a shaft sealing portion of a high pressure fluid device such as a blower or an air compressor.
【０００２】[0002]
【従来の技術】従来より、例えばガスタービン、ブロア
ーあるいはエアコンプレッサーなどの高圧流体機器の軸
封部に適用されるシール装置として、図１に示すよう
に、被軸封機器の回転部材１（図示例では回転軸１Ａと
同時回転する回転スリーブ１Ｂ）と同時回転する回転密
封環２Ａを設けた回転側シール要素２と、被軸封機器の
ケーシング３側に固定されたスプリングリテーナ３Ａ
に、周方向に等間隔で配置した回り止めピン３Ｂを介し
て回転不能に保持され、かつスプリング３Ｃにより回転
密封環２Ａ側に常時付勢される静止密封環４Ａを設けた
固定側シール要素４とを有し、上記回転密封環２Ａのシ
ール面２ａには、図５に示すように、円周方向に等間隔
で径方向にのびる幅狭深底の流体導入溝５を複数形成
し、これら流体導入溝５のそれぞれに連通し、かつ円周
方向の一方（例えば矢印ａで示す回転方向の反対側）に
のびる幅広浅底の動圧発生グルーブ６を形成した非接触
形メカニカルシールが知られている。2. Description of the Related Art Conventionally, as a sealing device applied to a shaft sealing portion of a high pressure fluid device such as a gas turbine, a blower or an air compressor, as shown in FIG. In the illustrated example, a rotary sleeve 1B) which rotates simultaneously with the rotary shaft 1A and a rotary seal element 2 provided with a rotary sealing ring 2A which rotates simultaneously, and a spring retainer 3A fixed to the casing 3 side of the shaft-sealed device.
The stationary-side sealing element 4 is provided with a stationary sealing ring 4A that is non-rotatably held via detent pins 3B that are arranged at equal intervals in the circumferential direction, and that is constantly biased toward the rotating sealing ring 2A side by a spring 3C. As shown in FIG. 5, a plurality of narrow and deep fluid introduction grooves 5 extending in the radial direction at equal intervals in the circumferential direction are formed on the sealing surface 2a of the rotary seal ring 2A. A non-contact type mechanical seal is known in which a dynamic pressure generating groove 6 having a wide and shallow bottom which communicates with each of the fluid introduction grooves 5 and extends in one circumferential direction (for example, the opposite side to the rotational direction indicated by arrow a) is formed. ing.
【０００３】このメカニカルシールでは、回転密封環２
Ａが回転すると、高圧側Ｙの流体が流体導入溝５から動
圧発生グルーブ６に流入して、シール面２ａと、静止密
封環４Ａのシール面４ａとの間に動圧を発生させ、シー
ル面４ａをシール面２ａから離す方向に付勢し、シール
面４ａをシール面２ａに当接させる方向に付勢している
スプリング３Ｃのばね力とのバランス点の圧力によっ
て、シール面２ａ，４ａ間に、例えば５〜２０μｍ程度
の狭いシール隙間を形成し低圧側Ｘと高圧側Ｙとを非接
触状態でシールするように構成されている。In this mechanical seal, the rotary seal ring 2 is used.
When A rotates, the fluid on the high-pressure side Y flows from the fluid introduction groove 5 into the dynamic pressure generating groove 6 to generate dynamic pressure between the seal surface 2a and the seal surface 4a of the stationary seal ring 4A, and to seal the seal. The seal surfaces 2a, 4a are pressed by the pressure at the balance point with the spring force of the spring 3C that urges the surface 4a away from the seal surface 2a and urges the seal surface 4a into contact with the seal surface 2a. A narrow seal gap of, for example, about 5 to 20 μm is formed between them so that the low pressure side X and the high pressure side Y are sealed in a non-contact state.
【０００４】[0004]
【発明が解決しようとする課題】ところで、シール面２
ａ，４ａ間に、十分に平行で一定のシール隙間を維持さ
せるためには、シール面２ａ，４ａによる自己整合機能
を有効に発揮させる必要がある。この自己整合機能は、
シール面２ａの径外端から動作発生グルーブ６の径方向
内側までの寸法と上記シール面の径方向の幅（以下、シ
ール面幅と称す）寸法に大きく左右されるが、従来のも
のでは、この点についての配慮がなされていないので、
自己整合機能を安定的に発揮させ得る保証がない。By the way, the sealing surface 2
In order to maintain a sufficiently parallel and constant seal gap between a and 4a, it is necessary to effectively exert the self-alignment function of the seal surfaces 2a and 4a. This self-alignment feature
The size from the outer radial end of the seal surface 2a to the radial inner side of the action-generating groove 6 and the radial width of the seal surface (hereinafter referred to as the seal surface width) greatly depend on the dimension. Since no consideration has been given to this point,
There is no guarantee that the self-alignment function can be exerted stably.
【０００５】本発明は上記のような問題点を解消するた
めになされたもので、自己整合機能を有効に発揮させる
ことができ、シール性能の信頼性を向上し得る非接触形
メカニカルシールを提供することを目的としている。The present invention has been made in order to solve the above problems, and provides a non-contact type mechanical seal which can effectively exhibit the self-alignment function and improve the reliability of the sealing performance. The purpose is to do.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、本発明に係る非接触形メカニカルシールは、シール
面の径外端から動圧発生グルーブの径方向の内側までの
寸法と上記シール面幅の寸法との比が０．３を越え、か
つ０．５未満に設定され、静止密封環を構成するカーボ
ン材の密度が１．７〜２．４ｇ／ｃｍ3 で、かつヤング
率が１２００〜２５００ｋｇ／ｍｍ2 に設定されたもの
である。In order to achieve the above object, a non-contact mechanical seal according to the present invention has a dimension from a radially outer end of a sealing surface to a radially inner side of a dynamic pressure generating groove and the sealing surface. The ratio to the width dimension is set to more than 0.3 and less than 0.5, the density of the carbon material forming the stationary seal ring is 1.7 to 2.4 g / cm 3 , and the Young's modulus is 1200. It is set to ˜2500 kg / mm 2 .
【０００７】[0007]
【作用】本発明によれば、回転密封環の回転により、流
体導入溝に連通する動圧発生グルーブに径外側（高圧
側）から流体が進入して動圧を発生させ、この動圧によ
って所定のシール隙間を形成して非接触状態でシールす
る。この時、シール面の径外側から動圧発生グルーブの
径方向の内側までの寸法と上記シール面幅の寸法との比
が０．３を越え、０．５未満に設定されているので、シ
ール面同志の自己整合機能が有効に発揮され、シール面
間の平行性が確実に保たれる。According to the present invention, the rotation of the rotary seal ring causes the fluid to enter the dynamic pressure generating groove communicating with the fluid introduction groove from the radially outer side (high pressure side) to generate the dynamic pressure. Seal gap is formed to seal in a non-contact state. At this time, since the ratio of the dimension from the radially outer side of the sealing surface to the radially inner side of the dynamic pressure generating groove and the dimension of the sealing surface width is set to more than 0.3 and less than 0.5, The face-to-face self-alignment function is effectively exerted, and the parallelism between the seal faces is reliably maintained.
【０００８】また、静止密封環をカーボン材で構成し、
その密度を比較的小さく設定したので、傾きに対する追
従性が向上し、さらにヤング率も設定したので、歪易く
なって自己整合機能の向上に有利となる。Further, the stationary seal ring is made of carbon material,
Since the density is set to be relatively small, the followability with respect to the inclination is improved, and the Young's modulus is also set, so that the distortion easily occurs, which is advantageous for improving the self-alignment function.
【０００９】[0009]
【実施例】以下、本発明の実施例を図面にもとづいて説
明する。図１は非接触形メカニカルシールの全体構成を
示す縦断側面図、図２は回転密封環の一実施例を示す正
面図であり、本発明の特徴は、回転密封環のシール面に
動圧発生グルーブとの配置の寸法を特定した構成に係
り、この点を除く他の部材および構成は従来例と同一で
あるため、図２において、図５に相当する部分には、そ
れぞれ同一の符号を付して、その詳細な説明は省略す
る。Embodiments of the present invention will now be described with reference to the drawings. FIG. 1 is a vertical sectional side view showing the overall configuration of a non-contact mechanical seal, and FIG. 2 is a front view showing an embodiment of a rotary seal ring. The feature of the present invention is that a dynamic pressure is generated on the seal surface of the rotary seal ring. With respect to the configuration in which the dimension of the arrangement with the groove is specified, the other members and the configuration except this point are the same as the conventional example. Therefore, in FIG. 2, parts corresponding to FIG. The detailed description thereof will be omitted.
【００１０】図１および図２において、回転密封環２Ａ
のシール面２ａには、円周方向に等間隔で外端がシール
面２ａの径外側（高圧側Ｙ）に開口し、内端がシール面
２ａ内に存在して径内方向にのびる流体導入溝５が複数
（例えば１２個）形成されている。この流体導入溝５の
深さは５μｍ〜１ｍｍ程度である。６は各流体導入溝５
にそれぞれ連通して円周方向の一方（反時計方向）、即
ち、矢印ｂ方向へ延びる動圧発生グルーブであり、この
動圧発生グルーブ６は、深さが４〜８μｍであり、上記
円周方向の長さは４〜１０ｍｍであり、幅寸法Ｈはシー
ル面幅Ｗの３０％程に設定されているが、０．２＜Ｈ／
Ｗ≦０．３の範囲でもよい。また、シール面２ａの径外
側から動圧発生グルーブ６の径方向内側６ａまでの寸法
Ｄとシール面幅Ｗとの比は、０．３＜Ｄ／Ｗ＜０．５に
設定されている。この回転密封環２Ａとしては、耐食
性、熱伝導性、耐摩耗性に優れた硬質材料、たとえば超
硬合金やＳｉＣが選ばれる。1 and 2, the rotary seal ring 2A
The outer surface of the seal surface 2a is opened at an equal interval in the circumferential direction on the radially outer side (high pressure side Y) of the seal surface 2a, and the inner end is located inside the seal surface 2a and extends radially inward. A plurality of (for example, 12) grooves 5 are formed. The depth of the fluid introduction groove 5 is about 5 μm to 1 mm. 6 is each fluid introduction groove 5
Is a dynamic pressure generating groove extending in one direction (counterclockwise direction) in the circumferential direction, that is, in the direction of the arrow b. The dynamic pressure generating groove 6 has a depth of 4 to 8 μm. The length in the direction is 4 to 10 mm, and the width dimension H is set to about 30% of the sealing surface width W, but 0.2 <H /
The range may be W ≦ 0.3. Further, the ratio of the dimension D from the radially outer side of the seal surface 2a to the radially inner side 6a of the dynamic pressure generating groove 6 and the seal surface width W is set to 0.3 <D / W <0.5. As the rotary seal ring 2A, a hard material excellent in corrosion resistance, thermal conductivity and wear resistance, for example, cemented carbide or SiC is selected.
【００１１】一方、静止密封環４Ａは、起動時等に相手
シール面２ａと接触しても自己潤滑性を保って焼き付け
などが起こりにくいようにカーボン材で構成されてお
り、その密度は１．７〜２．４ｇ／ｃｍ3 に設定され、
かつ、ヤング率は１２００〜２５００ｋｇ／ｍｍ2 に設
定されている。On the other hand, the stationary seal ring 4A is made of a carbon material so that even if it comes into contact with the mating seal surface 2a at the time of start-up, the self-lubricating property is maintained and seizure is unlikely to occur. Set to 7-2.4 g / cm 3 ,
Moreover, the Young's modulus is set to 1200 to 2500 kg / mm 2 .
【００１２】なお、上記静止密封環４Ａの外周は、スプ
リングリテーナ３Ａの内周面に対して０．３〜０．６ｍ
ｍ程度の微小隙間Ｇを設けて軸方向に移動可能に設定さ
れている。The outer circumference of the stationary seal ring 4A is 0.3 to 0.6 m with respect to the inner circumference of the spring retainer 3A.
It is set to be movable in the axial direction by providing a minute gap G of about m.
【００１３】このような構成であれば、回転密封環２Ａ
を矢印ａ方向に回転させることによって、流体導入溝５
から高圧側Ｙの流体が動圧発生グルーブ６に流入して、
回転密封環２Ａのシール面２ａと、静止密封環４Ａのシ
ール面４ａの間に動圧を発生させ、シール面２ａをシー
ル面４ａから離す方向に付勢し、スプリング３Ｃのばね
力とのバランス点の圧力によって、シール面２ａ，４ａ
間に、例えば５〜２０μｍ程度の狭いシール隙間を形成
して、低圧側Ｘと高圧側Ｙとを非接触状態でシールする
ものである。この時の圧力分布を図３に示す。With such a structure, the rotary seal ring 2A
The fluid introduction groove 5 by rotating the
Fluid from the high pressure side Y flows into the dynamic pressure generating groove 6 from
A dynamic pressure is generated between the seal surface 2a of the rotary seal ring 2A and the seal surface 4a of the stationary seal ring 4A to urge the seal surface 2a away from the seal surface 4a and balance with the spring force of the spring 3C. Depending on the point pressure, the sealing surfaces 2a, 4a
A narrow seal gap of, for example, about 5 to 20 μm is formed therebetween to seal the low pressure side X and the high pressure side Y in a non-contact state. The pressure distribution at this time is shown in FIG.
【００１４】上記動圧発生グルーブ６がシール面２ａの
径方向の一方に偏位していると、動圧発生作用が有効に
働かず、シール面２ａ，４ａの平行性を維持させにくい
が、上記のように０．３＜Ｄ／Ｗ＜０．５に設定するこ
とで、自己整合機能が高められ、シール面２ａ，４ａ同
志の接触が回避されるので、所定のシール隙間が確保さ
れてシール破壊を未然に防止することができる。If the dynamic pressure generating groove 6 is offset to one side in the radial direction of the seal surface 2a, the dynamic pressure generating action does not work effectively and it is difficult to maintain the parallelism between the seal surfaces 2a and 4a. By setting 0.3 <D / W <0.5 as described above, the self-alignment function is enhanced and contact between the seal surfaces 2a and 4a is avoided, so that a predetermined seal gap is secured. It is possible to prevent the seal from breaking.
【００１５】ところで、上記回転密封環２Ａに形成され
ている動圧発生グルーブ６の深さは４〜８μｍと浅いも
のであるが、回転密封環２Ａを超硬合金などで構成して
あるので、摩耗が抑制され、動圧発生機能を十分発揮さ
せることができる。一方、静止密封環４Ａは、起動時や
停止直前に相手方に接触されるおそれがあるが、これを
カーボン材で構成することにより、上記接触などがあっ
ても、自己潤滑性によって焼付けや損傷が生じるのを防
止することができる。とくに、上記カーボン材として、
その密度を比較的低く設定しているので、軽量化によっ
て追従性が高められ、さらにヤング率も比較的低く設定
したことによって、シール面圧に影響を受けない程度
で、適正に歪変形して自己整合機能を良好に維持させる
ことが可能になる。By the way, the depth of the dynamic pressure generating groove 6 formed in the rotary seal ring 2A is as shallow as 4 to 8 μm, but since the rotary seal ring 2A is made of cemented carbide or the like, Wear is suppressed, and the dynamic pressure generating function can be fully exerted. On the other hand, the stationary seal ring 4A may come into contact with the other party at the time of start-up or immediately before stopping. However, by constructing this with a carbon material, even if there is the above contact, seizure or damage is caused by self-lubricating property. It can be prevented from occurring. Especially, as the carbon material,
Since the density is set to a relatively low value, the followability is improved by reducing the weight, and the Young's modulus is also set to a relatively low value, so that the strain and deformation can be properly performed without being affected by the seal surface pressure. It is possible to maintain a good self-alignment function.
【００１６】図４は回転密封環２Ａの第２実施例を示す
正面図であり、この実施例では、上記第１実施例と同じ
構成の流体導入溝５に連通して円周方向の両方に向って
のびる第１実施例と同じ構成の動圧発生グルーブ６を形
成した構成となっている。このような構成であれば、回
転密封環２Ａを矢印ａ，ｂで示す正逆方向の回転時にお
いて、上記第１実施例と同じ作用効果を奏することがで
きる。即ち、回転方向が一方向にのみ制限されることな
く、正逆いずれの方向に回転密封環２Ａを回転させて
も、非接触状態でシールすることができるメカニカルシ
ールを提供し得るものである。FIG. 4 is a front view showing a second embodiment of the rotary seal ring 2A. In this embodiment, the rotary seal ring 2A is communicated with the fluid introducing groove 5 having the same structure as that of the first embodiment, and is arranged in both circumferential directions. The dynamic pressure generating groove 6 having the same structure as that of the first embodiment is formed. With such a configuration, the same operational effect as the first embodiment can be obtained when the rotary seal ring 2A is rotated in the forward and reverse directions indicated by the arrows a and b. That is, the rotation direction is not limited to one direction, and it is possible to provide a mechanical seal that can seal in a non-contact state even when the rotary sealing ring 2A is rotated in any of the forward and reverse directions.
【００１７】[0017]
【発明の効果】本発明は上述のとおり構成されているの
で、次のような効果を奏する。すなわち、この発明の非
接触形メカニカルシールにおいては、回転密封環の回転
により、流体導入溝に連通する動圧発生グルーブに径外
側（高圧側）から流体が進入して動圧を発生させ、この
動圧によって所定のシール隙間を形成して非接触状態で
シールすることができる。特に、シール面の径外側から
動圧発生グルーブの径方向内側までの寸法とシール面幅
との比を特定したことにより、自己整合機能が確実に発
揮されてシール面の平行性を保たせることができる。さ
らに、静止密封環の材質を特定したことによって、追従
性なども適正良好なものとして、所定の自己整合機能の
向上を確実に達成することができる。Since the present invention is configured as described above, it has the following effects. That is, in the non-contact mechanical seal of the present invention, the rotation of the rotary seal ring causes the fluid to enter the dynamic pressure generating groove communicating with the fluid introduction groove from the radially outer side (high pressure side) to generate the dynamic pressure. It is possible to form a predetermined seal gap by dynamic pressure and seal in a non-contact state. In particular, by specifying the ratio of the dimension from the outside of the seal surface to the inside of the dynamic pressure generating groove in the radial direction and the width of the seal surface, the self-alignment function can be reliably exerted and the parallelism of the seal surface can be maintained. You can Further, by specifying the material of the stationary seal ring, it is possible to reliably achieve the predetermined self-alignment function by appropriately setting the followability and the like.
【図１】本発明の一実施例による非接触形メカニカルシ
ールの全体構成を示す縦断側面図である。FIG. 1 is a vertical sectional side view showing an overall configuration of a non-contact mechanical seal according to an embodiment of the present invention.
【図２】回転密封環の第１実施例を示す拡大正面図であ
る。FIG. 2 is an enlarged front view showing the first embodiment of the rotary seal ring.
【図３】シール面の圧力分布図である。FIG. 3 is a pressure distribution diagram of a seal surface.
【図４】回転密封環の第２実施例を示す拡大正面図であ
る。FIG. 4 is an enlarged front view showing a second embodiment of the rotary seal ring.
【図５】従来のものの回転密封環の上半部を示す拡大正
面図である。FIG. 5 is an enlarged front view showing an upper half portion of a conventional rotary seal ring.
１ 回転部材 ２ 回転側シール要素 ２Ａ 回転密封環 ２ａ シール面 ３ ケーシング ３Ｃ スプリング ４ 固定側シール要素 ４Ａ 静止密封環 ５ 流体導入溝 ６ 動圧発生グルーブ ６ａ 径方向内側 Ｄ シール面の径外側から動圧発生クルーブの径方向内
側までの寸法 Ｗ シール面幅DESCRIPTION OF SYMBOLS 1 rotating member 2 rotating side sealing element 2A rotating sealing ring 2a sealing surface 3 casing 3C spring 4 fixed side sealing element 4A stationary sealing ring 5 fluid introduction groove 6 dynamic pressure generating groove 6a radial direction inside D dynamic pressure from outside the sealing surface Dimension to the inside of the generating claw in the radial direction
Claims (1)
転密封環を設けた回転側シール要素と、被軸封機器のケ
ーシング側に回転不能に保持され、かつスプリングによ
り回転密封環側に常時付勢される静止密封環を設けた固
定側シール要素とを備え、回転密封環のシール面に円周
方向に等間隔で外端が径外側に開口しかつ内端がシール
面内に存在して径内方向にのびる流体導入溝が複数形成
され、これら流体導入溝に連通し、かつ円周方向の一方
にのびる動圧発生グルーブが形成された非接触形メカニ
カルシールにおいて、上記シール面の径外側から動圧発
生グルーブの径方向の内側までの寸法と上記シール面の
径方向の幅寸法との比が０．３を越え、かつ０．５未満
に設定され、さらに、静止密封環を構成するカーボン材
の密度が１．７〜２．４ｇ／ｃｍ3 で、かつヤング率が
１２００〜２５００ｋｇ／ｍｍ2 に設定されていること
を特徴とする非接触形メカニカルシール。1. A rotation-side sealing element provided with a rotary sealing ring that rotates simultaneously with a rotating member of a shaft-sealed device, and a non-rotatable holding member on the casing side of the shaft-sealed device and a spring on the rotary sealing ring side. A stationary seal element provided with a stationary seal ring that is constantly urged, and the outer end opens radially outward and the inner end exists in the seal surface at equal intervals in the circumferential direction on the seal surface of the rotary seal ring. A plurality of fluid introduction grooves extending radially inward are formed, and a non-contact type mechanical seal communicating with these fluid introduction grooves and having a dynamic pressure generating groove extending in one circumferential direction is formed. The ratio of the dimension from the radially outer side to the radially inner side of the dynamic pressure generating groove and the radial width dimension of the sealing surface is set to more than 0.3 and less than 0.5. The density of the constituent carbon material is 1.7 to 2 A non-contact type mechanical seal characterized in that the Young's modulus is set to 1200 to 2500 kg / mm 2 at 0.4 g / cm 3 .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21388991A JPH0560247A (en) | 1991-08-26 | 1991-08-26 | Noncontact type mechanical seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21388991A JPH0560247A (en) | 1991-08-26 | 1991-08-26 | Noncontact type mechanical seal |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0560247A true JPH0560247A (en) | 1993-03-09 |
Family
ID=16646697
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21388991A Pending JPH0560247A (en) | 1991-08-26 | 1991-08-26 | Noncontact type mechanical seal |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0560247A (en) |
Cited By (28)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0989119A (en) * | 1995-09-29 | 1997-03-31 | Nippon Pillar Packing Co Ltd | Shaft sealing device for liquid apparatus |
| US5664787A (en) * | 1994-03-22 | 1997-09-09 | Nippon Pillar Packing Co., Ltd. | Non-contacting shaft sealing device |
| WO2006115118A1 (en) | 2005-04-22 | 2006-11-02 | Eagle Industry Co., Ltd. | Mechanical seal device, sliding part, and method of producing the sliding part |
| JP2012002295A (en) * | 2010-06-17 | 2012-01-05 | Canon Machinery Inc | Plane sliding mechanism |
| WO2014024742A1 (en) | 2012-08-04 | 2014-02-13 | イーグル工業株式会社 | Sliding component |
| WO2018092829A1 (en) | 2016-11-18 | 2018-05-24 | イーグル工業株式会社 | Sliding members |
| CN109058156A (en) * | 2018-08-17 | 2018-12-21 | 浙江工业大学 | One kind is like the combined mechanical seal end surface structure of comb dynamic and static pressure |
| WO2019013233A1 (en) | 2017-07-13 | 2019-01-17 | イーグル工業株式会社 | Sliding member |
| CN109253260A (en) * | 2018-11-30 | 2019-01-22 | 哈尔滨广瀚动力技术发展有限公司 | A kind of oil sealing arrangement of the gas turbine with flag-shaped slot rotating ring |
| CN109538762A (en) * | 2019-01-14 | 2019-03-29 | 东营海森密封技术有限责任公司 | A kind of shaft end mechanical seal structure |
| WO2019069887A1 (en) | 2017-10-03 | 2019-04-11 | イーグル工業株式会社 | Sliding component |
| WO2020196145A1 (en) | 2019-03-22 | 2020-10-01 | イーグル工業株式会社 | Sliding component |
| CN113439167A (en) * | 2019-02-04 | 2021-09-24 | 伊格尔工业股份有限公司 | Sliding component |
| US11320052B2 (en) | 2018-02-01 | 2022-05-03 | Eagle Industry Co., Ltd. | Sliding components |
| US11391376B2 (en) | 2016-08-15 | 2022-07-19 | Eagle Industry Co., Ltd. | Sliding component |
| US11603934B2 (en) | 2018-01-12 | 2023-03-14 | Eagle Industry Co., Ltd. | Sliding component |
| US11913454B2 (en) | 2020-07-06 | 2024-02-27 | Eagle Industry Co., Ltd. | Sliding component |
| US11933303B2 (en) | 2020-07-06 | 2024-03-19 | Eagle Industry Co., Ltd. | Sliding component |
| US12104598B2 (en) | 2020-07-06 | 2024-10-01 | Eagle Industry Co., Ltd. | Eccentric sliding assembly with a plurality of dynamic pressure generation mechanisms |
| US12135030B2 (en) | 2020-07-06 | 2024-11-05 | Eagle Industry Co., Ltd. | Sliding component |
| US12152676B2 (en) | 2020-07-06 | 2024-11-26 | Eagle Industry Co., Ltd. | Sliding component |
| US12196320B2 (en) | 2020-03-31 | 2025-01-14 | Eagle Industry Co., Ltd. | Sliding component |
| US12209668B2 (en) | 2019-02-04 | 2025-01-28 | Eagle Industry Co., Ltd. | Sliding component |
| US12259043B2 (en) | 2019-02-04 | 2025-03-25 | Eagle Industry Co., Ltd. | Sliding component |
| US12404935B2 (en) | 2020-07-06 | 2025-09-02 | Eagle Industry Co., Ltd. | Sliding component |
| US12449040B2 (en) | 2020-05-11 | 2025-10-21 | Eagle Industry Co., Ltd. | Sliding component |
| US12560239B2 (en) | 2021-08-25 | 2026-02-24 | Eagle Industry Co., Ltd. | Sliding components |
| USRE50849E1 (en) | 2016-11-16 | 2026-03-31 | Eagle Industry Co., Ltd. | Sliding component |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01295079A (en) * | 1988-05-20 | 1989-11-28 | Nippon Pillar Packing Co Ltd | Contactless mechanical seal |
| JPH02236067A (en) * | 1989-03-03 | 1990-09-18 | Nippon Pillar Packing Co Ltd | Non-contact end face type mechanical seal |
-
1991
- 1991-08-26 JP JP21388991A patent/JPH0560247A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01295079A (en) * | 1988-05-20 | 1989-11-28 | Nippon Pillar Packing Co Ltd | Contactless mechanical seal |
| JPH02236067A (en) * | 1989-03-03 | 1990-09-18 | Nippon Pillar Packing Co Ltd | Non-contact end face type mechanical seal |
Cited By (38)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5664787A (en) * | 1994-03-22 | 1997-09-09 | Nippon Pillar Packing Co., Ltd. | Non-contacting shaft sealing device |
| JPH0989119A (en) * | 1995-09-29 | 1997-03-31 | Nippon Pillar Packing Co Ltd | Shaft sealing device for liquid apparatus |
| WO2006115118A1 (en) | 2005-04-22 | 2006-11-02 | Eagle Industry Co., Ltd. | Mechanical seal device, sliding part, and method of producing the sliding part |
| JP2012002295A (en) * | 2010-06-17 | 2012-01-05 | Canon Machinery Inc | Plane sliding mechanism |
| WO2014024742A1 (en) | 2012-08-04 | 2014-02-13 | イーグル工業株式会社 | Sliding component |
| US9772037B2 (en) | 2012-08-04 | 2017-09-26 | Eagle Industry Co., Ltd. | Sliding component |
| US11391376B2 (en) | 2016-08-15 | 2022-07-19 | Eagle Industry Co., Ltd. | Sliding component |
| USRE50849E1 (en) | 2016-11-16 | 2026-03-31 | Eagle Industry Co., Ltd. | Sliding component |
| WO2018092829A1 (en) | 2016-11-18 | 2018-05-24 | イーグル工業株式会社 | Sliding members |
| US10808752B2 (en) | 2016-11-18 | 2020-10-20 | Eagle Industry Co., Ltd | Sliding members |
| WO2019013233A1 (en) | 2017-07-13 | 2019-01-17 | イーグル工業株式会社 | Sliding member |
| WO2019069887A1 (en) | 2017-10-03 | 2019-04-11 | イーグル工業株式会社 | Sliding component |
| KR20200039788A (en) | 2017-10-03 | 2020-04-16 | 이구루코교 가부시기가이샤 | Sliding parts |
| US11708911B2 (en) | 2017-10-03 | 2023-07-25 | Eagle Industry Co., Ltd. | Sliding component |
| US11603934B2 (en) | 2018-01-12 | 2023-03-14 | Eagle Industry Co., Ltd. | Sliding component |
| US11320052B2 (en) | 2018-02-01 | 2022-05-03 | Eagle Industry Co., Ltd. | Sliding components |
| US11619308B2 (en) | 2018-02-01 | 2023-04-04 | Eagle Industry Co., Ltd. | Sliding components |
| CN109058156A (en) * | 2018-08-17 | 2018-12-21 | 浙江工业大学 | One kind is like the combined mechanical seal end surface structure of comb dynamic and static pressure |
| CN109253260A (en) * | 2018-11-30 | 2019-01-22 | 哈尔滨广瀚动力技术发展有限公司 | A kind of oil sealing arrangement of the gas turbine with flag-shaped slot rotating ring |
| CN109538762A (en) * | 2019-01-14 | 2019-03-29 | 东营海森密封技术有限责任公司 | A kind of shaft end mechanical seal structure |
| US12209668B2 (en) | 2019-02-04 | 2025-01-28 | Eagle Industry Co., Ltd. | Sliding component |
| CN113439167A (en) * | 2019-02-04 | 2021-09-24 | 伊格尔工业股份有限公司 | Sliding component |
| CN113439167B (en) * | 2019-02-04 | 2023-06-02 | 伊格尔工业股份有限公司 | sliding parts |
| US12498044B2 (en) | 2019-02-04 | 2025-12-16 | Eagle Industry Co., Ltd. | Sliding component |
| US12259043B2 (en) | 2019-02-04 | 2025-03-25 | Eagle Industry Co., Ltd. | Sliding component |
| WO2020196145A1 (en) | 2019-03-22 | 2020-10-01 | イーグル工業株式会社 | Sliding component |
| US12467538B2 (en) | 2019-03-22 | 2025-11-11 | Eagle Industry Co., Ltd. | Sliding component |
| KR20210126113A (en) | 2019-03-22 | 2021-10-19 | 이구루코교 가부시기가이샤 | sliding parts |
| CN113508238A (en) * | 2019-03-22 | 2021-10-15 | 伊格尔工业股份有限公司 | sliding parts |
| US12196320B2 (en) | 2020-03-31 | 2025-01-14 | Eagle Industry Co., Ltd. | Sliding component |
| US12449040B2 (en) | 2020-05-11 | 2025-10-21 | Eagle Industry Co., Ltd. | Sliding component |
| US12104598B2 (en) | 2020-07-06 | 2024-10-01 | Eagle Industry Co., Ltd. | Eccentric sliding assembly with a plurality of dynamic pressure generation mechanisms |
| US12135030B2 (en) | 2020-07-06 | 2024-11-05 | Eagle Industry Co., Ltd. | Sliding component |
| US12152676B2 (en) | 2020-07-06 | 2024-11-26 | Eagle Industry Co., Ltd. | Sliding component |
| US11933303B2 (en) | 2020-07-06 | 2024-03-19 | Eagle Industry Co., Ltd. | Sliding component |
| US11913454B2 (en) | 2020-07-06 | 2024-02-27 | Eagle Industry Co., Ltd. | Sliding component |
| US12404935B2 (en) | 2020-07-06 | 2025-09-02 | Eagle Industry Co., Ltd. | Sliding component |
| US12560239B2 (en) | 2021-08-25 | 2026-02-24 | Eagle Industry Co., Ltd. | Sliding components |
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