JPS6257865B2 - - Google Patents

Info

Publication number
JPS6257865B2
JPS6257865B2 JP7152082A JP7152082A JPS6257865B2 JP S6257865 B2 JPS6257865 B2 JP S6257865B2 JP 7152082 A JP7152082 A JP 7152082A JP 7152082 A JP7152082 A JP 7152082A JP S6257865 B2 JPS6257865 B2 JP S6257865B2
Authority
JP
Japan
Prior art keywords
honeycomb
fluid
rotating shaft
stationary member
shaft
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
Application number
JP7152082A
Other languages
Japanese (ja)
Other versions
JPS58191374A (en
Inventor
Yasuo Kuramoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to JP7152082A priority Critical patent/JPS58191374A/en
Publication of JPS58191374A publication Critical patent/JPS58191374A/en
Publication of JPS6257865B2 publication Critical patent/JPS6257865B2/ja
Granted legal-status Critical Current

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
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/42—Sealings between relatively-moving surfaces by means of fluid kept in sealing position by centrifugal force

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Description

【発明の詳細な説明】 この発明は流体機械静止部材を貫通する回転軸
貫通部からの流体の漏洩損失を軽減する軸封装
置、特にハニカムを採用した軸封装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a shaft seal device that reduces leakage loss of fluid from a rotating shaft penetrating portion that passes through a stationary member of a fluid machine, and particularly to a shaft seal device that employs a honeycomb.

流体機械における回転軸貫通部にハニカムによ
る軸封装置を適用する場合には、従来第１図、第
２図に示すような構造のものが採用されていた。
これを説明すれば、第１図、第２図は回転軸の中
心軸線方向要部縦断面の中心軸線に対する対称半
部概略図であり同一部分は同一符号にて示す。図
において１０は流体機械の静止部材（例えがケー
シング又はシール台部）であり、２０は前記静止
部材１０を貫通して回転する回転軸である。１１
はハニカムで第１図の場合にはハニカム１１は静
止部材１０の貫通孔１０′の回転軸対向面に接着
剤１２により全面的に接着されている。又第２図
の場合にはハニカム１１は回転軸２０の静止部材
１０に対向する円周面上に接着剤１２により全面
的に接着されている。従つて第１図の場合も第２
図の場合も接着されたハニカム１１は片側面のみ
が開口面となりハニカム１１を通じての流体の流
動はない。このような構造においては流体漏洩量
の低減はハニカム１１の開口面上を流体が通過す
る際の大きな流体抵抗すなわち小さな流量係数に
のみ依存している。なお第１図、第２図において
P1，P2はそれぞれハニカム１１による軸封部の両
側の流体圧力を示すもので、図の場合P1＞P2の場
合を示している。このような構造の軸封装置にお
いて、流体漏洩量を低減せしめるにはハニカム開
口面とその対向面との間の隙間を小さくするとか
隙間通路を凹凸状に形成する等の手段が採用され
る。しかしながら此等の手段は静止部材１０と回
転軸２０との接触事故を起し易く危険である、の
みならず静止部材１０と回転軸２０との広い範囲
にわたつて漏洩流体通路間隙を小さく維持する必
要があるので、工業が面倒で手間がかかり工作費
が高価となる不利益がある。なお第３図は第１図
及び第２図における−断面矢視方向展開図で
あり、１０は前記静止部材、１１はハニカムであ
り、第１図の場合は静止部材１０とハニカム１１
とは接着剤により接着されて静止部材側が閉塞さ
れているが第２図の場合はハニカム１１は回転軸
２０に接着されているので静止部材１０側は開口
していることは上述の通りであり、又漏洩流体は
ハニカム１１の開口側とこれに対向する回転軸２
０の周面もしくは静止部材１０に設けられた回転
軸貫通孔内周面との間に形成された間隙を流動し
てP1側からP2側に流動することは言うまでもない
（流体流動方向は第１図および第２図において太
い矢印にて表す） この発明は、叙上の危険性のあるかつ不利益な
手段を採用することなく、簡単かつ容易に工作で
きる手段により流体機械における流体漏洩量を減
少せしめることができるハニカムによる軸封装置
を提供するのをその目的とする。 When applying a shaft sealing device using a honeycomb to a rotating shaft penetrating portion of a fluid machine, a structure as shown in FIGS. 1 and 2 has conventionally been adopted.
To explain this, FIGS. 1 and 2 are schematic views of symmetrical halves with respect to the central axis of longitudinal sections of essential parts of the rotating shaft in the direction of the central axis, and the same parts are designated by the same reference numerals. In the figure, 10 is a stationary member (for example, a casing or a seal stand) of the fluid machine, and 20 is a rotating shaft that rotates through the stationary member 10. 11
In the case of FIG. 1, the honeycomb 11 is entirely bonded with adhesive 12 to the surface of the stationary member 10 facing the rotating shaft of the through hole 10'. In the case of FIG. 2, the honeycomb 11 is entirely bonded to the circumferential surface of the rotary shaft 20 facing the stationary member 10 with an adhesive 12. Therefore, in the case of Figure 1, the second
In the case of the figure as well, only one side of the bonded honeycomb 11 is open, and no fluid flows through the honeycomb 11. In such a structure, the reduction in the amount of fluid leakage depends only on the large fluid resistance when the fluid passes over the opening surface of the honeycomb 11, that is, on the small flow coefficient. In addition, in Figures 1 and 2
P 1 and P 2 each indicate the fluid pressure on both sides of the shaft sealing portion by the honeycomb 11, and the figure shows the case where P 1 >P 2 . In a shaft sealing device having such a structure, in order to reduce the amount of fluid leakage, measures such as reducing the gap between the honeycomb opening surface and its opposing surface or forming the gap passage in an uneven shape are adopted. However, such means are not only dangerous as they tend to cause contact accidents between the stationary member 10 and the rotating shaft 20, but also require that the leakage fluid passage gap be kept small over a wide range between the stationary member 10 and the rotating shaft 20. Since it is necessary, there is a disadvantage that the manufacturing process is troublesome and time-consuming, and the manufacturing cost is high. Note that FIG. 3 is a developed view in the direction of the - cross section in FIGS. 1 and 2, where 10 is the stationary member and 11 is the honeycomb.
The honeycomb 11 is bonded with adhesive and the stationary member side is closed, but in the case of FIG. 2, the honeycomb 11 is bonded to the rotating shaft 20, so the stationary member 10 side is open, as described above. , leakage fluid is leaked from the opening side of the honeycomb 11 and the rotating shaft 2 opposite thereto.
It goes without saying that the fluid flows from the P 1 side to the P 2 side through the gap formed between the peripheral surface of the rotary shaft 0 or the inner peripheral surface of the rotating shaft through hole provided in the stationary member 10 (the fluid flow direction is (Represented by thick arrows in FIGS. 1 and 2) This invention aims to reduce the amount of fluid leakage in fluid machines by means that can be easily and easily engineered without employing the above-mentioned dangerous and disadvantageous means. The object of the present invention is to provide a shaft sealing device using a honeycomb that can reduce the amount of damage.

この発明の要旨は叙上の特許請求の範囲に記載
した軸封装置の構成にある。 The gist of the invention lies in the structure of the shaft sealing device described in the claims above.

以下この発明をその実施例を示した図面を参照
しながら詳細に説明する。第４図はこの発明にか
かる軸封装置の基本的な実施例の回転軸中心軸線
方向縦断面の前記中心軸線に対する称対半部を示
すものであり、第５図は第４図における−断
面矢視方向図である。第４図、第５図において同
一部分はそれぞれ同一符号にて示す。第４図にお
いて１０aは流体機械の静止部材であり、２０aは
該静止部材１０aを貫通して回転する回転軸であ
る。該静止部材１０aとこれを貫通している回転
軸２０aとの間にはハニカム２１を装着するに充
分な間隙が形成されている。この回転軸２０aの
静止部材１０aに対向する部分に段部を形成して
拡径部２０bが設けられている。又静止部材１０a
の高圧P1を有する流体の入口附近における回転軸
２０aの中心軸線に直角方向の同一外周面上には
複数個の柱状突起２４……が放射状に突設され、
その高さは前記拡径部２０bの外周面と同一高さ
になるよう設定されている（第５図参照）前記回
転軸２０aの拡径部２０bの外周面上に静止部１０
aの内周面とあらかじめ設定された間隙を形成す
る高さh2を有するハニカム２１が接着剤２９によ
り接着されると共に前記拡径部２０bの高圧P1流
体側端部頂面と前記突起２４……頂面とにわたり
接着剤２９によりあらかじめ設定された高さh1を
有するハニカム２２が接着されている。したがつ
てハニカム２２は回転軸２０aを囲繞して回転軸
２０aに接着され前記拡径部２０bの高圧P1流体側
端部と前記突起２４……との間に空所２３を形成
しハニカム２２の両端は開口状態に回転軸２０a
に装着される。又前記突起２４……は複数個設け
られているので第５図に示す突起２４……相互間
の間隙２４′……を通つて高圧P1流体は空所２３
内に流入する。更に又ハニカム２２の高さh1とハ
ニカム２１の高さh2とは必ずしも同一とする要は
なく回転軸２０aの回転によりハニカム２２の遠
心フアン又は遠心ポンプのインペラ的の作用を大
きくするためh1＞h2としてもよい。この場合はハ
ニカム２２に対向する静止部材１０aの高圧P1流
体側側壁を高圧P1流体側に高圧P1流体の流入口を
中心として先開きに切欠くことがのぞましい。 Hereinafter, the present invention will be explained in detail with reference to the drawings showing embodiments thereof. FIG. 4 shows a symmetrical half of a longitudinal section of a basic embodiment of the shaft sealing device according to the present invention in the direction of the central axis of the rotating shaft with respect to the central axis, and FIG. 5 shows a - cross section in FIG. 4. FIG. Identical parts in FIGS. 4 and 5 are designated by the same reference numerals. In FIG. 4, 10a is a stationary member of the fluid machine, and 20a is a rotating shaft that rotates through the stationary member 10a . A gap sufficient for mounting the honeycomb 21 is formed between the stationary member 10a and the rotating shaft 20a passing through the stationary member 10a. An enlarged diameter portion 20 b is provided by forming a stepped portion in a portion of the rotating shaft 20 a that faces the stationary member 10 a . Also, stationary member 10 a
A plurality of columnar protrusions 24 are provided radially on the same outer peripheral surface in a direction perpendicular to the central axis of the rotating shaft 20 a near the inlet of the fluid having a high pressure P 1 of .
The height thereof is set to be the same height as the outer circumferential surface of the enlarged diameter portion 20 b (see FIG . 5).
A honeycomb 21 having a height h 2 that forms a preset gap with the inner circumferential surface of a is bonded with an adhesive 29, and the high pressure P 1 of the enlarged diameter portion 20 b is connected to the top surface of the fluid side end and the protrusion. 24... A honeycomb 22 having a preset height h 1 is bonded to the top surface with an adhesive 29. Therefore, the honeycomb 22 surrounds the rotating shaft 20a and is bonded to the rotating shaft 20a , forming a space 23 between the high pressure P1 fluid side end of the enlarged diameter portion 20b and the projections 24... Both ends of the honeycomb 22 are connected to the rotating shaft 20 a in an open state.
will be installed on the Also, since a plurality of the protrusions 24 are provided, the high pressure P1 fluid flows through the gaps 24' between the protrusions 24 shown in FIG.
flow inside. Furthermore, the height h 1 of the honeycomb 22 and the height h 2 of the honeycomb 21 do not necessarily have to be the same, but in order to increase the impeller-like action of the centrifugal fan or centrifugal pump of the honeycomb 22 by rotation of the rotating shaft 20 a . It is also possible to set h 1 > h 2 . In this case, it is preferable that the side wall of the stationary member 10 a facing the honeycomb 22 on the high pressure P 1 fluid side is cut out toward the high pressure P 1 fluid side so as to open toward the center around the inlet of the high pressure P 1 fluid.

第６図は第４図に示す実施例の変形を示すもの
であつて、第４図と同一部分はそれぞれ同一符号
にて示す。第４図に示すハニカム２２の高さh1を
ハニカム軸封部のハニカム２１の高さh2より高く
し、かつハニカム２２の側壁と静止部材１０aの
側壁との間隙δを小さくしたものであつて、この
間隙δより外側は高圧P1流体側に静止部材１０a
が高圧P1流体の流入口を中心として先開きに切欠
かれている。第７図は第４図に示す実施例の他の
変形であつて第４図と同一部材はそれぞれ同一符
号にて示す。ハニカム２２の高さh1をハニカム軸
封部のハニカム２１の高さよりも高くし、ハニカ
ム２２が高圧P1流体のハニカム軸封部えの流入口
側に傾斜するようテーパ状に形成したものであつ
て、この場合第４図における回転軸２０aにおけ
る拡径部２０bの高圧P1流体側端部を先開き截頭
円錐状体に形成し更に回転軸２０aの高圧P1流体
側の回転軸２０aの中心軸線に直角方向の同一円
周上に、頂面に前記高圧P1流体側に形成された前
記截頭円錐状体のテーパに合致するテーパを有す
る柱状突起２４を複数個立設し、前記截頭円錐状
体と柱状突起２４……のそれぞれの上面にあらか
じめ設定された高さh1を有するハニカム２２が接
着剤２９にて接着されて構成されている。この場
合柱状突起２４……の高さは回転軸２０aの拡径
部２０bの高さよりも高く、かつハニカム２２を
接着剤２９にて接着した場合ハニカム２２の側壁
がハニカム２１の上面と静止部材１０aの貫通孔
との間に形成された間隙（高圧P1流体の漏洩通
路）入口を覆うように形成されると共にハニカム
２２から回転軸２０aの回転により噴出する斜流
も静止部材１０aの側壁に沿つて流れ流体カーテ
ンを形成して前記入口を覆うよう静止部材１０a
の高圧P1側側壁の下部は斜流の流出方向に先開き
状に形成されている。 FIG. 6 shows a modification of the embodiment shown in FIG. 4, and the same parts as in FIG. 4 are designated by the same reference numerals. The height h 1 of the honeycomb 22 shown in FIG. 4 is made higher than the height h 2 of the honeycomb 21 of the honeycomb shaft sealing part, and the gap δ between the side wall of the honeycomb 22 and the side wall of the stationary member 10 a is made small. Then, outside this gap δ, there is a stationary member 10a on the high pressure P1 fluid side.
A notch is opened at the center of the high-pressure P1 fluid inlet. FIG. 7 shows another modification of the embodiment shown in FIG. 4, and the same members as those in FIG. 4 are designated by the same reference numerals. The height h1 of the honeycomb 22 is made higher than the height of the honeycomb 21 of the honeycomb shaft sealing part, and the honeycomb 22 is formed in a tapered shape so as to be inclined toward the inlet side of the honeycomb shaft sealing part of the high pressure P1 fluid. In this case, the high pressure P1 fluid side end of the enlarged diameter portion 20b of the rotating shaft 20a in FIG. A plurality of columnar protrusions 24 are provided on the same circumference in a direction perpendicular to the central axis of the rotating shaft 20a , and each have a taper on the top surface that matches the taper of the truncated conical body formed on the high pressure P1 fluid side. A honeycomb 22 is erected and has a preset height h 1 on the upper surface of each of the truncated conical body and columnar protrusion 24 . . . and is bonded with an adhesive 29 . In this case, the height of the columnar protrusions 24 is higher than the height of the enlarged diameter portion 20 b of the rotating shaft 20 a , and when the honeycomb 22 is bonded with the adhesive 29, the side wall of the honeycomb 22 is stationary with the upper surface of the honeycomb 21. The stationary member 10 is formed to cover the entrance of the gap (leakage passage for high pressure P1 fluid) formed between the through hole of the member 10a, and also the diagonal flow ejected from the honeycomb 22 by the rotation of the rotating shaft 20a . Stationary member 10 a flows along the side wall of a to form a fluid curtain covering said inlet .
The lower part of the high-pressure P1 side wall is formed to open toward the outflow direction of the diagonal flow.

この発明は基本的には第４図に示す構成を有す
るので、回転軸２０aの回転により両端開口状態
に高圧P1流体側回転軸２０aに装着されているハ
ニカム２２に充満していた高圧P1流体は遠心力に
よりハニカム２２からその外周に回転軸２０aの
半径方向に吐出されると共にこれを補うため軸封
装置入口側の高圧P1流体が回転軸２０aに形成さ
れた空所２３に回転軸２０aの周上に突設された
複数個の柱状突起２４間と回転軸２０aの外周面
とによつて形成された第５図に示す通路２４′…
…を通り空所２３内に連続的に流入する。一方ハ
ニカム２２から吐出された高圧P1流体の回転軸半
径方向流は対向する静止部材１０aの対向壁面に
向つて吐出されるが、該対向壁面は前記吐出流体
の流れの方向を壁面に沿つて曲げ（第４図、第６
図、第７図における太い矢印方向）その方向は軸
封部における静止部材１０aと回転軸２０aに接着
されたハニカム２１とが形成する間隙とは反対方
向である。その結果軸封部入口はこの半径方向流
による流体カーテンで塞がれる事になる。又第６
図の構成においてはハニカム２２の高さを高くし
たためハニカム２２の遠心フアンは遠心ポンプの
それぞれのインペラ的作用が強まりハニカム２２
から吐出する高圧P1流体半径方向流の軸封部入口
に対する閉塞効果は増す。又ハニカム２２と静止
部１０aの側壁との間隙δを小さくすることによ
りハニカム２２が摩擦ポンプ的に作用しこの部分
えの高圧P1流体の漏洩流入を防害する。更に第７
図に示す実施例においてはハニカム２２が傾斜し
ているためハニカム２２は斜流フアン又は斜流ポ
ンプのそれぞれのインペラ的作用をなし、ハニカ
ム２２内えの高圧P1流体の流れは第４図、第６図
に示す実施例のものより円滑となり、かつその循
環量も大きくなり軸封部入口の閉塞もより効果的
となる。 This invention basically has the configuration shown in FIG. 4 , so that the rotation of the rotating shaft 20a causes the high pressure P1 to open at both ends. The P 1 fluid is discharged from the honeycomb 22 to its outer periphery in the radial direction of the rotating shaft 20 a due to centrifugal force, and to compensate for this, the high pressure P 1 fluid on the inlet side of the shaft sealing device is discharged into the cavity formed in the rotating shaft 20 a . A passage 24' shown in FIG. 5 is formed between a plurality of columnar protrusions 24 protruding from the circumference of the rotating shaft 20a and the outer peripheral surface of the rotating shaft 20a .
... and continuously flows into the cavity 23. On the other hand, the flow of high-pressure P1 fluid discharged from the honeycomb 22 in the radial direction of the rotating shaft is discharged toward the opposing wall surface of the opposing stationary member 10a , which faces the direction of flow of the discharged fluid along the wall surface. bending (Fig. 4, 6)
7) This direction is opposite to the gap formed between the stationary member 10a in the shaft seal portion and the honeycomb 21 bonded to the rotating shaft 20a . As a result, the shaft seal inlet is blocked by a fluid curtain caused by this radial flow. Also the 6th
In the configuration shown in the figure, since the height of the honeycomb 22 is increased, the centrifugal fan of the honeycomb 22 has a stronger impeller-like action of each of the centrifugal pumps, and the honeycomb 22 has a higher height.
The blocking effect of the high-pressure P1 fluid radial flow discharged from the shaft seal inlet increases. Further, by reducing the gap δ between the honeycomb 22 and the side wall of the stationary part 10a , the honeycomb 22 acts like a friction pump, thereby preventing leakage and inflow of the high pressure P1 fluid in this part. Furthermore, the seventh
In the embodiment shown in the figure, since the honeycomb 22 is inclined, the honeycomb 22 acts like an impeller of a mixed flow fan or a mixed flow pump, and the flow of high pressure P1 fluid inside the honeycomb 22 is as shown in FIG. The flow is smoother than that of the embodiment shown in FIG. 6, and the amount of circulation is also larger, so that the shaft seal inlet can be more effectively blocked.

この発明は叙上の構成及び作用を有するので、
この発明に従えば、流体機械における静止部材を
貫通する回転軸貫通部にハニカムを採用した軸封
装置において、軸封装置入口部における簡単な構
造により高圧流体の軸封装置内えの漏洩量を効果
的に低減せしめることができると共に軸封部にお
ける高圧漏洩流体の通路の間隙を減少したり又は
軸封部を構成するハニカム開口部に凹凸を形成し
て高圧漏洩流体の通路を曲折せしめる等の手間の
かかる面倒複雑な作業を要する事がないので工業
上ならびに経済上の効果は極めて著しい。 Since this invention has the structure and operation described above,
According to the present invention, in a shaft seal device in which a honeycomb is adopted as a rotating shaft penetrating portion that passes through a stationary member of a fluid machine, the amount of leakage of high-pressure fluid within the shaft seal device is reduced by a simple structure at the shaft seal device inlet. This can be effectively reduced by reducing the gap in the high-pressure leakage fluid passage in the shaft seal, or by forming irregularities in the honeycomb opening that constitutes the shaft seal to bend the high-pressure leakage fluid passage. The industrial and economical effects are extremely significant because no time-consuming and complicated work is required.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図及び第２図は従来のハニカムを採用した
流体機械における回転軸貫通部の軸封装置の説明
用中心軸線方向要部縦断図の中心軸線に対する対
称半部概略図、第３図は第１図、第２図における
−断面矢視方向展開図、第４図はこの発明の
基本的実施例の中心軸線方向縦断面の中心軸線に
対する対称半部概略図、第５図は第４図における
−断面矢視方向図、第６図、第７図はそれぞ
れこの発明の変形実施例における説明用中心軸線
方向要部縦断面の中心軸線に対する対称半部概略
図である。 １０a……流体機械の静止部材、２０a……回転
軸、２０b……回転軸拡径部、２１，２２……ハ
ニカム、２３……空所、２４……柱状突起、２
４′……流体通路、２９……接着剤、h1，h2……
ハニカム高さ、P1……高圧流体、P2……P1に対し
低圧流体。 1 and 2 are schematic diagrams of a symmetrical half of a longitudinal sectional view of a main part in the central axis direction for explaining a shaft sealing device for a rotating shaft penetrating portion in a fluid machine employing a conventional honeycomb, and FIG. 1 and 2, FIG. 4 is a schematic diagram of a symmetrical half of a longitudinal section in the central axis direction of the basic embodiment of the present invention with respect to the central axis, and FIG. - A cross-sectional view in the direction of arrows, FIGS. 6 and 7 are schematic views of a symmetrical half of a longitudinal section of a main part in the direction of the central axis in a modified embodiment of the present invention, respectively, with respect to the central axis. DESCRIPTION OF SYMBOLS 10a ...Stationary member of fluid machine, 20a ...Rotating shaft, 20b ...Rotating shaft enlarged diameter part, 21, 22...Honeycomb, 23...Vacancy, 24...Columnar projection, 2
4'...Fluid passage, 29...Adhesive, h1 , h2 ...
Honeycomb height, P 1 ...High pressure fluid, P 2 ...Low pressure fluid relative to P1 .

Claims (1)

【特許請求の範囲】[Claims] １ 流体機械の静止部材に穿設された貫通孔を貫
通して配設される回転軸の貫通孔内周面に対向す
る部分の外周面に一方側が閉塞状態に接着剤にて
接着されて設けられたハニカム２１と、前記ハニ
カム２１の圧力流体入口側基部に流体機械内高圧
流体に連通するよう形成された空所２３と、該空
所２３を囲繞して一端は回転軸外周面上に、他端
は該回転軸の中心軸線に直角方向の外周面上の放
射状位置に配設固定された複数個の柱状突起の頂
面にそれぞれ接着剤にて接着して前記空所２３の
位置にて上下両側がそれぞれ開口状態に設けられ
たハニカム２２とを具える回転軸を、前記貫通孔
内に回転軸における前記ハニカム２１の上面と前
記貫通孔内周面との間の間隙があらかじめ設定さ
れた幅となるよう配設すると共に前記ハニカム２
２から回転軸の回転により吐出される流体が前記
静止部材の側壁に沿つて半径方向流を形成して流
体機械内方向に流れるよう前記静止部材の流体入
口部形状を形成してなることを特徴とする軸封装
置。1. A rotary shaft that is disposed through a through hole drilled in a stationary member of a fluid machine, and is bonded with an adhesive to the outer circumferential surface of a portion opposite to the inner circumferential surface of the through hole, with one side closed. a hollow space 23 formed at the pressure fluid inlet side base of the honeycomb 21 so as to communicate with the high pressure fluid in the fluid machine; The other end is attached with adhesive to the top surface of a plurality of columnar projections arranged and fixed at radial positions on the outer peripheral surface in a direction perpendicular to the central axis of the rotating shaft, and placed in the space 23. A rotation shaft including a honeycomb 22 with both upper and lower sides open, respectively, is provided in the through hole, and a gap between the upper surface of the honeycomb 21 on the rotation shaft and the inner circumferential surface of the through hole is set in advance. The honeycomb 2 is arranged so that the width of the honeycomb 2 is
The fluid inlet portion of the stationary member is shaped so that the fluid discharged from No. 2 by rotation of the rotating shaft forms a radial flow along the side wall of the stationary member and flows inward of the fluid machine. Shaft sealing device.
JP7152082A 1982-04-30 1982-04-30 Shaft seal device Granted JPS58191374A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP7152082A JPS58191374A (en) 1982-04-30 1982-04-30 Shaft seal device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP7152082A JPS58191374A (en) 1982-04-30 1982-04-30 Shaft seal device

Publications (2)

Publication Number Publication Date
JPS58191374A JPS58191374A (en) 1983-11-08
JPS6257865B2 true JPS6257865B2 (en) 1987-12-03

Family

ID=13463071

Family Applications (1)

Application Number Title Priority Date Filing Date
JP7152082A Granted JPS58191374A (en) 1982-04-30 1982-04-30 Shaft seal device

Country Status (1)

Country Link
JP (1) JPS58191374A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0431640Y2 (en) * 1985-11-14 1992-07-29
KR20230062306A (en) * 2021-10-28 2023-05-09 캐롯손해보험 주식회사 Method and Device for Detecting Driving Behavior without Calculating Yaw

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2250789B (en) * 1990-12-12 1994-03-30 Rolls Royce Plc Brush seal arrangement
EP2913567B1 (en) * 2012-12-06 2016-10-19 Mitsubishi Heavy Industries Compressor Corporation Sealing device and rotating machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0431640Y2 (en) * 1985-11-14 1992-07-29
KR20230062306A (en) * 2021-10-28 2023-05-09 캐롯손해보험 주식회사 Method and Device for Detecting Driving Behavior without Calculating Yaw

Also Published As

Publication number Publication date
JPS58191374A (en) 1983-11-08

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