JPH0656214B2 - Dry gas seal device - Google Patents
Dry gas seal deviceInfo
- Publication number
- JPH0656214B2 JPH0656214B2 JP2182858A JP18285890A JPH0656214B2 JP H0656214 B2 JPH0656214 B2 JP H0656214B2 JP 2182858 A JP2182858 A JP 2182858A JP 18285890 A JP18285890 A JP 18285890A JP H0656214 B2 JPH0656214 B2 JP H0656214B2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- dry gas
- bush
- sealing
- web
- 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 - Lifetime
Links
- 238000007789 sealing Methods 0.000 claims description 51
- 230000002093 peripheral effect Effects 0.000 claims description 25
- 238000012856 packing Methods 0.000 claims description 10
- 230000001050 lubricating effect Effects 0.000 claims 1
- 230000000694 effects Effects 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 230000035515 penetration Effects 0.000 description 4
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 229910000990 Ni alloy Inorganic materials 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000002411 adverse Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910001374 Invar Inorganic materials 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 1
- 229910010271 silicon carbide Inorganic materials 0.000 description 1
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 1
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
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3436—Pressing means
- F16J15/346—Pressing means the pressing force varying during operation
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Sealing Devices (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、ケーシング壁を通つて回転する軸のための、
軸方向滑りリングパツキンとして構成された乾式ガスシ
ール装置であつて、前記軸と共に回転しシール面の担体
として構成された軸ブシユと、ガスによつて前記シール
面に圧着されかつ潤滑される滑り面を有する周方向定位
の滑りリングとを備えた形式のものに関する。Description: FIELD OF THE INVENTION The present invention relates to a shaft rotating through a casing wall,
A dry gas sealing device configured as an axial sliding ring packing, comprising a shaft bushing configured as a carrier for a sealing surface that rotates together with the shaft, and a sliding surface that is pressed and lubricated by the gas with the sealing surface. With a circumferentially oriented slide ring having
このような軸方向の軸シール装置は例えば欧州特許第１
３６７８号明細書に基づいて公知であり、ターボ機械例
えばターボ圧縮機又はタービンの、或る圧力下にあるケ
ーシング内室を、外部へ又は中間室への軸の貫通部のと
ころでシールしてケーシング内室からの圧力媒体の流出
を阻止するために使用される。この流出阻止は遮断媒
体、例えばシールガスを用いて行われ、該遮断媒体は滑
りリングの滑り面をシール面に接圧し、ひいてはケーシ
ング内室からのガスの流出を最小限に抑え、その場合シ
ール装置の漏れは相応のパツキンリングによつて最小可
能値に保たれる。同時にシール装置を無接触式に回転さ
せるためのギヤツプが形成される。Such an axial shaft seal device is disclosed, for example, in European Patent No. 1
Known from U.S. Pat. No. 3,678,312, in which the casing inner chamber of a turbomachine, for example a turbocompressor or turbine, under a certain pressure, is sealed at the shaft penetration to the outside or to the intermediate chamber Used to prevent the flow of pressure medium out of the chamber. This outflow prevention is carried out by means of a blocking medium, for example a sealing gas, which presses the sliding surface of the sliding ring against the sealing surface and thus minimizes the outflow of gas from the housing interior, in which case the sealing Leakage of the device is kept to a minimum possible value by means of a corresponding packing ring. At the same time, a gear cup for contactlessly rotating the sealing device is formed.
この場合特に、摂氏数百度に及ぶ高いガス温度で稼働す
るターボ機械において不利な点は、ケーシング壁におけ
る軸貫通部で高い昇温と大きな温度変動が発生して、そ
の結果個々の部材を熱膨張させることである。この熱膨
張によつて、シール作用を害なわせる許容不能な変形が
惹起される。昇温が比較的高く、これによつて軸の膨張
が生じた場合には更に又、軸ブシユ及び、大抵はセラミ
ツクから成るシール体は、該シール体を破損させターボ
機械にダメージを及ぼすような機械的応力を受ける。ま
た特に高速運転のターボ機械では、部分的に著しく大き
な遠心力が生じ、やはり変形を惹起する。この変形の結
果、周速度が一層高くなると、例えば軸ブシユはシール
体と共に軸から離間し、つまり特定の位置及びセンタリ
ングはもはや維持されなくなる。これによつて不釣合が
生じ、かつシールギヤツプに許容不能の変化が生じる。
遠心力の作用を受けて軸ブシユとシール体との伸びが異
なることに基づいてシール体における機械的応力が増大
しかつダメージの虞れが生じる。それゆえに公知のガス
遮断式軸方向の軸シール装置では許容温度及び温度変動
並びに回転数は制限を受けている。In this case, in particular, the disadvantage of turbomachines operating at gas temperatures as high as several hundred degrees Celsius is that high temperature rises and large temperature fluctuations occur in the shaft penetrations in the casing wall, resulting in thermal expansion of the individual components. It is to let. This thermal expansion causes an unacceptable deformation that impairs the sealing action. If the temperature rise is relatively high, which results in shaft expansion, the shaft bushing and, more often, the sealing body, which is usually made of ceramic, may damage the sealing body and damage the turbomachine. Subject to mechanical stress. Further, particularly in a turbomachine operating at a high speed, a remarkably large centrifugal force is partially generated, which also causes deformation. As a result of this deformation, at higher circumferential speeds, for example, the shaft bushing moves away from the shaft together with the sealing body, i.e. the specific position and centering are no longer maintained. This causes imbalances and unacceptable changes in the seal gap.
Due to the difference in elongation between the shaft bush and the seal body due to the action of centrifugal force, the mechanical stress in the seal body increases and there is a risk of damage. Therefore, in the known gas-sealed axial shaft seal device, the permissible temperature, the temperature fluctuation, and the rotational speed are limited.
本発明の課題は、先行技術の前記欠点を排除し、特に冒
頭で述べた形式の軸方向の軸シール装置を改良して、い
かなる温度でも、温度に変動が生じても、また周速度及
び回転数が増大しても、ダメージを受ける虞れなく軸を
適正にシールできるようにすることである。The object of the present invention is to eliminate the above-mentioned drawbacks of the prior art, and in particular to improve an axial shaft sealing device of the type mentioned at the outset so that at any temperature, variations in temperature, peripheral speed and rotation Even if the number increases, the shaft can be properly sealed without being damaged.
前記課題を解決する本発明の構成手段は、シールフラン
ジを有する軸ブシユが軸を半径方向遊びを以て内包しか
つ形状嵌合式のセンタリング継手によって前記軸と結合
されており、前記センタリング継手が軸の膨張時に前記
軸ブシユに対してばね弾性的であり、しかも軸に対する
前記シール面の区域における軸ブシユの膨張を阻止する
ように構成されている点にある。According to the constituent means of the present invention for solving the above-mentioned problems, a shaft bush having a seal flange includes the shaft with radial play and is connected to the shaft by a centering joint of a form-fitting type, and the centering joint expands the shaft. Sometimes it is spring-elastic with respect to the shaft bush and is arranged to prevent expansion of the shaft bush in the area of the sealing surface relative to the shaft.
その場合、軸ブシユと軸との間の前記のようなばね弾性
的なセンタリング継手を特に有利に製作するためには、
軸は、その外周面を半径方向間隔をおいて取囲む円筒リ
ング状のウエブを有し、該ウエブは軸ブシユの円筒環状
の溝内に嵌合し、しかも該溝の半径方向外寄りの周壁が
ばね弾性的であるのに対して、半径方向内寄りの周壁が
剛性に構成されている。温度が上昇し、それに基づいて
軸が拡張しかつウエブが半径方向にずれ動く際に、溝の
前記半径方向外寄りの周壁は弾性的に変形され、かつ軸
上における軸ブシユの形状嵌合式センタリングを固定的
にするために役立つ。軸ブシユ自体はその際変形せず、
むしろシール面の位置に不都合な影響を及ぼさないよう
に自動調心される。回転数の増大時の遠心力に基づく軸
ブシユの溝の拡張は、該溝の剛性的な半径方向内寄りの
周壁と軸の剛性的なウエブとの間の形状嵌合によつて阻
止される。In that case, in order to manufacture the spring-elastic centering joint between the shaft bush and the shaft in a particularly advantageous manner,
The shaft has a cylindrical ring-shaped web that surrounds the outer peripheral surface of the shaft at radial intervals, and the web fits in the cylindrical annular groove of the shaft bush, and the peripheral wall of the groove radially outward. Is spring-elastic, whereas the circumferentially inner peripheral wall is rigid. When the temperature rises and the shaft expands accordingly and the web moves in the radial direction, the radially outer peripheral wall of the groove is elastically deformed, and the shape-fitting centering of the shaft bush on the shaft is performed. Helps to be fixed. The shaft bush itself does not deform at that time,
Rather, it is self-aligned so as not to adversely affect the position of the sealing surface. The expansion of the groove of the shaft bush due to the centrifugal force at increasing rotational speed is prevented by the form fit between the rigid radially inward peripheral wall of the groove and the rigid web of the shaft. .
従つて本発明のシール装置の機能は事実上、ターボ機械
の運転温度には無関係になり、また軸回転数又は周速度
にも無関係になる。本発明による前記ばね弾性的なセン
タリング継手は、いかなる場合にも、シールギヤツプに
影響を及ぼす諸部分の温度、周速度及び材料には無関係
に、軸上における軸ブシユの固定的なセンタリングを保
証し、すなわち軸と軸ブシユのために、熱膨張係数の異
なつた材料を使用することが可能である。これによつて
特に例えば、軸ブシユの熱膨張をシール体の熱膨張に適
合させることが可能になり、ひいてはシール効果が一層
改善され、かつ破損の危険率が一層低下されることにな
る。The functioning of the sealing device according to the invention is therefore virtually independent of the operating temperature of the turbomachine and also independent of the shaft speed or the peripheral speed. The spring-elastic centering joint according to the invention guarantees in each case a fixed centering of the shaft bush on the shaft, irrespective of the temperature, peripheral speed and material of the parts affecting the sealing gear. That is, it is possible to use materials having different coefficients of thermal expansion for the shaft and the shaft bush. This makes it possible, for example, to adapt the thermal expansion of the shaft bushing to the thermal expansion of the sealing body, which in turn improves the sealing effect and reduces the risk of breakage.
次に図面に基づいて本発明の実施例を詳説する。 Next, an embodiment of the present invention will be described in detail with reference to the drawings.
図示の実施例では軸１は例えばターボ機械のケーシング
壁２を通つて、高圧Pi部位から低圧Pa部位へ気密にガイ
ドされている。シール装置は、軸１に装着された軸ブシ
ユ３を有し、該軸ブシユは軸１を半径方向遊び４を以て
内包しているので、運転中の加熱による軸１の直径変動
は軸ブシユ３の変形なしに吸収される。これに対して軸
１の外部域１″寄りでは軸ブシユ３はスリーブ状端部
３″によつて軸１にばね弾性的に支承されているので、
ここでも軸変形は、シールギヤツプに影響を及ぼすこと
なく吸収される。軸ブシユ３は、軸１の熱膨張係数に対
比して小さな熱膨張係数を有する金属、例えばアンバー
（Invar）という商品名で公知になつている高ニツケル
合金鋼、から成つているのが有利である。軸ブシユ３は
外周面にシール体５を支持し、該シール体はその外周面
に円環状シール面６を形成している。該シール体５は、
軸ブシユ３に類似した熱膨張係数を有する超硬金属、例
えば炭化珪素から成るのが有利である。しかし炭化タン
グステンや類似の滑り特性を有する別の材料も適してい
る。In the embodiment shown, the shaft 1 is hermetically guided from the high-pressure Pi site to the low-pressure Pa site, for example through a casing wall 2 of the turbomachine. The sealing device has a shaft bush 3 mounted on the shaft 1, which encloses the shaft 1 with a radial play 4, so that the diameter variation of the shaft 1 due to heating during operation is different from that of the shaft bush 3. Absorbed without deformation. On the other hand, near the outer region 1 "of the shaft 1, the shaft bush 3 is spring-elastically supported on the shaft 1 by the sleeve-like end 3",
Here too, axial deformation is absorbed without affecting the sealing gear. The shaft bush 3 is advantageously made of a metal having a small coefficient of thermal expansion compared to the coefficient of thermal expansion of the shaft 1, for example a high nickel alloy steel known under the trade name Invar. is there. The shaft bush 3 supports a seal body 5 on the outer peripheral surface thereof, and the seal body forms an annular seal surface 6 on the outer peripheral surface thereof. The seal body 5 is
Advantageously, it consists of a cemented carbide, for example silicon carbide, which has a coefficient of thermal expansion similar to that of the axial bush 3. However, tungsten carbide and other materials with similar sliding properties are also suitable.
またシール装置は、ケーシング壁２内に挿入されたパツ
キンホールダ２′内に周方向では定位に、すなわち回転
不能に配置されているが軸方向では幾分摺動可能な滑り
リング７を有し、該滑りリングは内周面側７′でパツキ
ンホールダ２′の付加部８に対してセンタリングされて
いる。滑りリング７及びパツキンホールダ２′もやは
り、熱膨張能の低い金属、例えばアンバーという商品名
で公知になつているような高ニツケル合金鋼、から成つ
ているのが有利である。滑りリング７は内部寄りの両側
に、円環状シール面６に向いた滑り面９′を有する滑り
体９を保持し、該滑り体は良好な滑り特性の材料、例え
ばカーボンセラミツク材から成り、該材料には、熱伝導
性の改善のために金属添加剤が添加されていてもよい。The sealing device also has a sliding ring 7 which is arranged circumferentially in the packing holder 2'inserted in the casing wall 2 in the circumferential direction, i.e. non-rotatable but somewhat slidable in the axial direction, The sliding ring is centered on the inner peripheral surface side 7'with respect to the additional portion 8 of the packing holder 2 '. The sliding ring 7 and the packing holder 2'also advantageously consist of a metal with a low thermal expansion capacity, for example a high nickel alloy steel as is known under the trade name Amber. The sliding ring 7 carries on both sides towards the inside a sliding body 9 with a sliding surface 9 ′ facing the annular sealing surface 6, said sliding body comprising a material of good sliding properties, for example a carbon ceramic material, A metal additive may be added to the material to improve thermal conductivity.
軸シール装置には導管１０を介してケーシング壁２を通
してシールガスが圧力Psで供給され、該圧力はターボ機
械のシールすべき高圧Piよりも僅かに高くてもよい。そ
の場合圧力Psはターボ機械自体から取出されるか又は外
部ガスとして供給されてもよい。シールガスはギヤツプ
１１を通つて滑りリング７の背面７″に達して該滑りリ
ングを軸ブシユ３に圧着するので、回転するシール体５
のシール面６は、周方向定位の滑り体９の滑り面９′に
当接し、こうしてケーシングの内部からのガスの流出が
充分に防止される。それにもかかわらず流出する微量ガ
スは導管１３を介して導出される。その場合、滑り面の
潤滑は公知の方式で、例えば滑り面又はシール面に設け
たポケツト又は条溝を介して空気動力学的にか、又は、
滑り体を通してガスを滑り面に供給することによつて空
気静力学的に行われる。The shaft sealing device is supplied with the sealing gas at pressure Ps through the casing wall 2 via the conduit 10, which pressure may be slightly higher than the high pressure Pi to be sealed in the turbomachine. The pressure Ps may then be taken from the turbomachine itself or supplied as external gas. The sealing gas passes through the gear 11 and reaches the back surface 7 ″ of the sliding ring 7 and presses the sliding ring onto the shaft bush 3 so that the rotating sealing body 5
The sealing surface 6 of the abutting member abuts on the sliding surface 9'of the sliding body 9 positioned in the circumferential direction, so that the outflow of gas from the inside of the casing is sufficiently prevented. Nevertheless, the trace gas that escapes is discharged via conduit 13. In that case, the lubrication of the sliding surface is in a known manner, for example aerodynamically via a pocket or a groove provided on the sliding surface or the sealing surface, or
This is done aerostatically by supplying gas to the sliding surface through the sliding body.
本実施例では前記シール装置以外に、シール効果を一層
改善するために、あるいは故障発生時の非常シール装置
として、ほぼ同様に構成された滑りリングシール装置１
４が設けられているが、該滑りリングシール装置は、場
合によつては省くこともできる。In the present embodiment, in addition to the above sealing device, a sliding ring sealing device 1 having substantially the same structure is provided to further improve the sealing effect or as an emergency sealing device when a failure occurs.
4 is provided, but the sliding ring sealing device can optionally be omitted.
軸１と軸ブシユ３が著しく異なつた温度をもつことのあ
るような、ケーシング壁における軸貫通部ではターボ機
械の運転中に、昇温時に軸１の外径が軸ブシユ３の内径
よりも著しく拡張するという問題が生じる。逆に又、回
転数が高くなると軸ブシユ３が軸１よりも著しく拡張す
る傾向がある。このような、軸１と軸ブシユ３の直径変
動を吸収するために軸ブシユ３はばね弾性継手によつて
軸１と連結されており、該ばね弾性継手は、連結部位に
おいて半径方向膨張差の発生を許容するが、シール効果
にとつて重要な軸ブシユ３の位置とシール面域における
軸ブシユの寸法に不都合な影響を及ぼすことのないよう
な継手である。When the temperature rises, the outer diameter of the shaft 1 is significantly larger than the inner diameter of the shaft bush 3 at the time of turbomachine operation at the shaft penetration portion in the casing wall, where the shaft 1 and the shaft bush 3 may have significantly different temperatures. The problem of expansion arises. On the contrary, the shaft bush 3 tends to expand more remarkably than the shaft 1 as the rotation speed increases. The shaft bush 3 is connected to the shaft 1 by a spring elastic joint in order to absorb such a diameter variation of the shaft 1 and the shaft bush 3, and the spring elastic joint has a radial expansion difference at the connecting portion. It is a joint that allows generation but does not adversely affect the position of the shaft bush 3 and the size of the shaft bush in the sealing surface area, which are important for the sealing effect.
このために軸１は内部域１′において、該軸を環状間隙
15′を以て取囲む円筒リング状のウエブ１５を有してい
る。他方、軸ブシユ３の対応端部３′は円筒環状の溝１
６を有し、該溝は、軸１に一体成形されたウエブ１５を
係合させて冷却状態で形状嵌合式のセンタリング座を形
成するように設計されている。この目的のために前記円
筒環状の溝１６の半径方向内寄りの周壁16′は、壁が比
較的剛性で、要するに変形されないような壁厚に構成さ
れている。半径方向内寄りの周壁16′の外周面はウエブ
１５に対してｏリング状のパツキン16″によつてシール
されており、該パツキンはウエブ１５の或る程度の直径
変動に追従することができる。半径方向内寄りの周壁1
6′の内周面は全軸ブシユ３と同じように軸１に対して
半径方向遊び４を有し、該半径方向遊びは加熱時の軸の
充分な直径増大を接触なしに許容する。これに対して円
筒環状の溝１６の半径方向外寄りの周壁17はばね弾性的
に構成されておりかつ内向き環部17′によつてウエブ１
５に接圧し、これによつて軸１の昇温時にも確実なセン
タリング嵌合を保証することができる。しかし内部域
１′における軸１の熱膨張時、ひいては又、ウエブ１５
の直径増大時には半径方向外寄りの周壁１７は弾性的に
拡張される。しかしながら軸ブシユ３はこの弾性的な変
形可能性のゆえにシール面の区域ではその位置に留ま
り、いかなる応力も受けない。要するに運転中の軸１の
昇温によつてシールギヤツプの変形は生ぜず、軸シール
装置の機能がダメージを受ける虞れもない訳である。他
面において軸ブシユ３の円筒環状の溝１６の拡張は、該
溝の剛性的な半径方向内寄りの周壁16′と軸１の円筒リ
ング状のウエブ１５との係合によつて阻止されるので、
この場合も軸ブシユ３はシールギヤツプの変形なしにそ
の位置とセンタリングを維持する。For this purpose, the shaft 1 is arranged in the inner region 1 ',
It has a cylindrical ring-shaped web 15 which is surrounded by 15 '. On the other hand, the corresponding end 3'of the shaft bush 3 has a cylindrical annular groove 1
6, the groove being designed to engage a web 15 integrally formed with the shaft 1 to form a form-fitting centering seat in the cooled state. For this purpose, the peripheral wall 16 'radially inward of the cylindrical annular groove 16 is constructed with a wall thickness such that the wall is relatively rigid and, in effect, is not deformed. The outer peripheral surface of the radially inner wall 16 ′ is sealed to the web 15 by an o-ring-shaped packing 16 ″, which can follow a certain diameter variation of the web 15. . Radial inner peripheral wall 1
The inner peripheral surface of 6'has a radial play 4 with respect to the shaft 1, like the full-shaft bush 3, which allows a sufficient diameter increase of the shaft during heating without contact. On the other hand, the radially outer peripheral wall 17 of the cylindrical annular groove 16 is spring-elastically configured and is provided by the inwardly facing ring portion 17 'with the web 1.
It is possible to ensure a reliable centering fit even when the temperature of the shaft 1 is raised. However, during the thermal expansion of the shaft 1 in the inner zone 1 ', and thus also the web 15
When the diameter increases, the peripheral wall 17 radially outward is elastically expanded. However, due to this elastic deformability, the axial bush 3 remains in its position in the area of the sealing surface and is not subject to any stress. In short, the temperature rise of the shaft 1 during operation does not cause the deformation of the seal gear cup, and there is no fear that the function of the shaft seal device will be damaged. On the other side, the expansion of the cylindrical annular groove 16 of the shaft bush 3 is prevented by the engagement of the rigid radially inward peripheral wall 16 'of the groove with the cylindrical ring-shaped web 15 of the shaft 1. So
In this case as well, the shaft bush 3 maintains its position and centering without deformation of the sealing gear.
要するに本発明の軸シール装置は、運転中に軸貫通部に
著しい温度変動を生ぜしめるような高い温度のターボ機
械のために、また回転数及び周速度の高いターボ機械の
ためにも適している。また本発明の軸シール装置は、経
費のかかる冷却手段を講じることなしにターボ機械の高
い運転温度を許容すると同時に、高い回転数による運転
を可能にする。In short, the shaft seal device of the invention is suitable for high temperature turbomachines which cause significant temperature fluctuations in the shaft penetration during operation, and also for turbomachines with high speed and peripheral speed. . The shaft seal device of the present invention also allows high operating temperatures of turbomachines without the need for costly cooling measures, while at the same time allowing high rotational speed operation.
同等のことは、外部域１″の低圧Pa寄りの滑りリングシ
ール装置１４における軸と軸ブシユとのセンタリング継
手についても当て嵌まり、この場合軸ブシユは、温度に
基づく軸の膨張がシール面区域においていかなる変形も
軸ブシユに伝達しないように弾性的に構成されている。The same applies to the centering joint between the shaft and the shaft bushing in the sliding ring sealing device 14 near the low pressure Pa in the outer region 1 ″, in which case the shaft bushing causes expansion of the shaft due to temperature in the sealing surface area. It is elastically configured so that no deformation is transmitted to the shaft bush.
図面は本発明による乾式ガスシール装置の１実施例とし
ての軸パツキンの軸線に沿つた断面図である。 １…軸、１′…内部域、１″…外部域、２…ケーシング
壁、２′…パツキンホールダ、３…軸ブシユ、３′…対
応端部、３″…スリーブ状端部、４…半径方向遊び、５
…シール体、６…円環状シール面、７…滑りリング、
７′…内周面側、７″…背面、８…付加部、９…滑り
体、９′…滑り面、１０，１３…導管、Pi…高圧、Pa…
低圧、Ps…シールガスの圧力、１４…滑りリングシール
装置、１５…円筒リング状のウエブ、15′…環状間隙、
１６…円筒環状の溝、16′…半径方向内寄りの周壁、1
6″…ｏリング、１７…半径方向外寄りの周壁、17′…
内向き環部The drawing is a sectional view along the axis of a shaft packing as an embodiment of the dry gas seal device according to the present invention. 1 ... Shaft, 1 '... Inner zone, 1 "... Outer zone, 2 ... Casing wall, 2' ... Packing holder, 3 ... Shaft bush, 3 '... Corresponding end portion, 3" ... Sleeve end portion, 4 ... Radius Directional play, 5
... Sealing body, 6 ... Annular sealing surface, 7 ... Sliding ring,
7 '... inner peripheral surface side, 7 "... back surface, 8 ... additional portion, 9 ... sliding body, 9' ... sliding surface 10,13 ... conduit, Pi ... high pressure, Pa ...
Low pressure, Ps ... Seal gas pressure, 14 ... Sliding ring sealing device, 15 ... Cylindrical ring-shaped web, 15 '... Annular gap,
16 ... Cylindrical annular groove, 16 '... Peripheral wall radially inward, 1
6 ″ ... o-ring, 17 ... peripheral wall radially outward, 17 ′ ...
Inward ring
Claims (5)
（１）のための、軸方向滑りリングパツキンとして構成
された乾式ガスシール装置であつて、前記軸（１）と共
に回転しシール面（６）の担体として構成された軸ブシ
ユ（３）と、ガスによつて前記シール面（６）に圧着さ
れかつ潤滑される滑り面(9′）を有する周方向定位の滑
りリング（７）とを備えたものにおいて、シールフラン
ジを有する軸ブシユ（３）が軸（１）を半径方向遊び
（４）を以て内包しかつ形状嵌合式のセンタリング継手
（15,16）によつて前記軸（１）と結合されており、前
記センタリング継手が軸（１）の膨張時に前記軸ブシユ
（３）に対してばね弾性的であり、しかも軸（１）に対
する前記シール面（６）の区域における軸ブシユ（３）
の膨張を阻止するように構成されていることを特徴とす
る、乾式ガスシール装置。1. A dry gas sealing device in the form of an axial sliding ring packing for a shaft (1) rotating through a casing wall (2), said sealing surface rotating with said shaft (1). A circumferentially oriented sliding ring (7) having a shaft bush (3) configured as a carrier of (6) and a sliding surface (9 ') that is pressed against the lubricating surface (6) and lubricated by gas. In which a shaft bush (3) having a seal flange encloses the shaft (1) with radial play (4) and by means of a form-fitting type centering joint (15, 16) the shaft (1) ), The centering joint is spring-elastic with respect to the shaft bush (3) when the shaft (1) expands, and in the area of the sealing surface (6) with respect to the shaft (1). (3)
A dry gas seal device, wherein the dry gas seal device is configured to prevent expansion of the gas.
グ継手が一方の部材（１）に円筒リング状のウエブ（１
５）を有し、該ウエブが他方の部材（３）に設けた円筒
環状の溝（１６）内に嵌合し、しかも前記センタリング
継手の少なくとも一部分（１７）が半径方向で弾性的に
構成されている、請求項１記載の乾式ガスシール装置。2. A centering joint between a shaft (1) and a shaft bush (3) has a cylindrical ring-shaped web (1) on one member (1).
5), wherein the web fits in a cylindrical annular groove (16) provided in the other member (3) and at least a part (17) of the centering joint is radially elastically configured. The dry gas sealing device according to claim 1.
域(1′）で軸１にケーシング外部域の方に向つて軸方向
に設けられていて該軸を間隙を以て取囲む円筒リング
（１５）として構成されており、かつ円筒環状の溝が、
軸ブシユ(3)のシールフランジの、シール面（６）とは
反対の側に設けられていて前記円筒リング(15)を囲む溝
（１６）として構成されている、請求項２記載の乾式ガ
スシール装置。3. A cylindrical ring (15) in which a cylindrical ring-shaped web is axially provided on the shaft 1 in the casing inner region (1 ') toward the casing outer region and surrounds the shaft with a gap. And a cylindrical annular groove,
3. Dry gas according to claim 2, characterized in that it is provided as a groove (16) on the side of the sealing flange of the shaft bush (3) opposite the sealing surface (6) and enclosing the cylindrical ring (15). Sealing device.
ツキン（16″）によつてシールされた半径方向内寄りの
剛性的な周壁（16′）と、少なくとも内部域寄り端部
（17′）で前記ウエブ（１５）の外周面に圧着する半径
方向外寄りのばね弾性的な周壁（１７）とによつて形成
されている、請求項３記載の乾式ガスシール装置。4. A radially inwardly rigid peripheral wall (16 '), in which a groove (16) is sealed to the web (15) by a packing (16 "), and at least an inner region end. 4. A dry gas sealing device according to claim 3, characterized in that it is formed by means of a spring-elastic peripheral wall (17) which is radially outwardly pressed against the outer peripheral surface of the web (15) at (17 ').
熱膨張係数よりも小さい、請求項１から４までのいずれ
か１項記載の乾式ガスシール装置。5. The dry gas sealing device according to claim 1, wherein the coefficient of thermal expansion of the shaft bush (3) is smaller than the coefficient of thermal expansion of the shaft (1).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH261189A CH680606A5 (en) | 1989-07-12 | 1989-07-12 | |
| CH2611/89-8 | 1989-07-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0351582A JPH0351582A (en) | 1991-03-05 |
| JPH0656214B2 true JPH0656214B2 (en) | 1994-07-27 |
Family
ID=4237666
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2182858A Expired - Lifetime JPH0656214B2 (en) | 1989-07-12 | 1990-07-12 | Dry gas seal device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH0656214B2 (en) |
| CH (1) | CH680606A5 (en) |
| DE (1) | DE3925403C2 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH684495A5 (en) * | 1991-09-04 | 1994-09-30 | Escher Wyss Ag | Turbomachinery. |
| US5183270A (en) * | 1991-09-16 | 1993-02-02 | Allied-Signal Inc. | Composite seal rotor |
| CH686525A5 (en) * | 1992-07-02 | 1996-04-15 | Escher Wyss Ag | Turbomachinery. |
| DE4239586C1 (en) * | 1992-11-25 | 1994-01-13 | Ruhrgas Ag | Turbomachinery system and method for sealing a turbomachine |
| DE4419379A1 (en) * | 1994-05-27 | 1995-12-07 | Mannesmann Ag | Turbocompressor system for gases |
| EP0870136B1 (en) * | 1996-01-19 | 2002-09-04 | Ceramic Engineering Consulting, Inc. | Circumferential seal with ceramic rotor |
| DE29612203U1 (en) * | 1996-07-12 | 1996-09-05 | Feodor Burgmann Dichtungswerke GmbH & Co, 82515 Wolfratshausen | Mechanical seal arrangement |
| UA67807C2 (en) * | 1998-11-20 | 2004-07-15 | Везувіус Крусібл Компані | Stopper rod |
| DE19923530A1 (en) * | 1999-05-21 | 2000-11-23 | Univ Dresden Tech | Radial or axial shaft sealing ring has sealing lip and optionally protective lip and is made from homogeneous and/or non-homogeneous ceramic organic/inorganic composite material |
| US6655695B1 (en) * | 2001-02-13 | 2003-12-02 | Honeywell International Inc. | Face seal assembly with composite rotor |
| US7905495B2 (en) | 2007-11-29 | 2011-03-15 | Rolls-Royce Corporation | Circumferential sealing arrangement |
| US8657573B2 (en) | 2010-04-13 | 2014-02-25 | Rolls-Royce Corporation | Circumferential sealing arrangement |
| FR2961258B1 (en) * | 2010-06-15 | 2012-06-08 | Snecma | CARBON SEALING AND SEALING DEVICE WITH INTEGRATED SMOOTH BEARING FOR A TURBOMACHINE |
| DE102011007073A1 (en) | 2011-04-08 | 2012-10-11 | Siemens Aktiengesellschaft | A shaft seal assembly |
| US9664289B2 (en) * | 2012-06-06 | 2017-05-30 | General Electric Technology Gmbh | Pump sealing device |
| EP3293425A1 (en) | 2016-09-13 | 2018-03-14 | Siemens Aktiengesellschaft | Gas seal |
| EP3293426A1 (en) | 2016-09-13 | 2018-03-14 | Siemens Aktiengesellschaft | Gas seal |
| JP2019196721A (en) * | 2018-05-08 | 2019-11-14 | アイシン精機株式会社 | Water pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1426864A1 (en) * | 1965-08-17 | 1969-03-27 | Siemens Ag | Sealing arrangement for thermal engines |
| US4212475A (en) * | 1979-01-15 | 1980-07-15 | Crane Packing Co. | Self aligning spiral groove face seal |
| GB2154674B (en) * | 1984-02-22 | 1987-06-24 | Gits Bros Mfg Co | Shaft seal |
| FI74121C (en) * | 1986-01-22 | 1988-08-01 | Safematic Ltd Oy | Mechanical seals |
-
1989
- 1989-07-12 CH CH261189A patent/CH680606A5/de not_active IP Right Cessation
- 1989-08-01 DE DE19893925403 patent/DE3925403C2/en not_active Expired - Fee Related
-
1990
- 1990-07-12 JP JP2182858A patent/JPH0656214B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE3925403C2 (en) | 1993-12-16 |
| CH680606A5 (en) | 1992-09-30 |
| DE3925403A1 (en) | 1991-01-24 |
| JPH0351582A (en) | 1991-03-05 |
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