JPS59505A - Steam turbine - Google Patents
Steam turbineInfo
- Publication number
- JPS59505A JPS59505A JP10994082A JP10994082A JPS59505A JP S59505 A JPS59505 A JP S59505A JP 10994082 A JP10994082 A JP 10994082A JP 10994082 A JP10994082 A JP 10994082A JP S59505 A JPS59505 A JP S59505A
- Authority
- JP
- Japan
- Prior art keywords
- packing
- labyrinth
- teeth
- steam
- steam turbine
- 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
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
- F16J15/44—Free-space packings
- F16J15/441—Free-space packings with floating ring
- F16J15/442—Free-space packings with floating ring segmented
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は回転体の周囲から蒸気の漏洩するのを防止する
ラビリンスパツキンを改良した蒸気タービンに関する。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a steam turbine having an improved labyrinth packing that prevents leakage of steam from around a rotating body.
蒸気タービンの漏洩防止装置としてラビリンスパツキン
形式を採るものは一般的に第1図に示す次の3ケ所であ
る。即ち第1はロータ・ケーシング端部グランドパツキ
ン(1)、第2はロータ・ノズルダイヤフラム内径部ノ
ズルラビリンスパツキン(2)、第3は羽根先端・ノズ
ルダイヤフラム間ラジアルスピルストリップ(3)であ
る。尚(11はタービンロータ、aυはタービンケーシ
ングである。The labyrinth packing type is generally used as a leakage prevention device for steam turbines at the following three locations as shown in FIG. That is, the first is the rotor casing end gland packing (1), the second is the rotor nozzle diaphragm inner diameter nozzle labyrinth packing (2), and the third is the radial spill strip between the blade tip and the nozzle diaphragm (3). Note that (11 is a turbine rotor, and aυ is a turbine casing.
上記に使用する従来のラビリンスパツキンの縦断面図を
第2図に示す。ラビリンス歯(4)はパツキン母材(5
)から削ル出し加工、又はパツキン母材(5)にかしめ
加工によシ矢印すで示す蒸気の流出方向に垂直に複数枚
が設置される。ロータ(111<又は羽根先端)とラビ
リンス歯(4)との径方向間隙を安全上杵される微少間
隙にすることによシ、ラビリンスパツキン前後の差圧P
ltP!によ電流れようとする蒸気に流路抵抗を与えて
漏洩防止する。FIG. 2 shows a longitudinal cross-sectional view of the conventional labyrinth packing used above. The labyrinth tooth (4) is attached to the packing base material (5
) is machined or caulked to the packing base material (5), and a plurality of sheets are installed perpendicularly to the steam outflow direction indicated by the arrow. By making the radial gap between the rotor (111<or blade tip) and the labyrinth tooth (4) a minute gap that can be safely punched, the differential pressure P before and after the labyrinth seal
ltP! This prevents leakage by providing flow path resistance to the steam that is about to flow.
漏洩量は下記のマーチンの(101)によシ算出される
。The leakage amount is calculated according to Martin's (101) below.
!えはラビリンス漏洩量(kf/H)
Kは電流係数(第3図の曲線(7)参照)fは漏洩面積
(cIrP)
ここで、
f=πX D X CI
Dはロータ(又は羽根の先端)の直径(ffi)CIは
パツキン半径方向間隙(cIR)ここで、
Plはパツキン入口側圧力(kglcrl abs )
P、はパツキン出口側圧力(kf/J abs )Nは
パツキン歯数
υ1はパツキン入口側比容積(−”/kf)上記の漏洩
量はいずれもタービン内部の蒸気の熱エネルギ→羽根回
転トルク→軸端出力というエネルギ変換システムをバイ
パスし、正規の仕事を得られないため、その減少はター
ビン効率増大のために重要である。! E is the labyrinth leakage amount (kf/H) K is the current coefficient (see curve (7) in Figure 3) f is the leakage area (cIrP) Here, f=π diameter (ffi) CI is the packing radial clearance (cIR) where Pl is the packing inlet pressure (kglcrl abs)
P is the pressure on the packing outlet side (kf/J abs) N is the number of packing teeth υ1 is the specific volume on the packing inlet side (-"/kf) The above leakage amounts are the thermal energy of the steam inside the turbine → blade rotation torque → Since the shaft end power bypasses the energy conversion system and cannot obtain regular work, its reduction is important for increasing turbine efficiency.
一例として従来の一般的な蒸気タービンにおける損失に
占める漏洩損失の割合を第4図に示すが、その総量は約
4196にも達している。As an example, FIG. 4 shows the ratio of leakage loss to loss in a conventional general steam turbine, and the total amount reaches approximately 4196.
本発明はラビリンスからの蒸気漏洩量を減少して効率の
よい蒸気タービンを提供することを目的とする。An object of the present invention is to provide an efficient steam turbine by reducing the amount of steam leaking from the labyrinth.
本発明においては、環状のパツキン歯に交差して、回転
体の軸方向11Cl”iぼ平行な旋回防止歯を設けるこ
とにより、ラビリンス内の蒸気旋回を防止し、旋回によ
る動圧を低下させ、蒸気漏洩量を減少させるものである
。In the present invention, by providing anti-swivel teeth that intersect with the annular packing teeth and are approximately parallel to the axial direction of the rotating body, steam swirl within the labyrinth is prevented, and the dynamic pressure due to the swirl is reduced. This reduces the amount of steam leakage.
以下、本発明の一実施例について、第5図および第6図
を参照して説明する。尚この実施例の蒸気タービンの概
略立面図は従来例として説明した第1図と同様であるか
ら、これも参照されたい。An embodiment of the present invention will be described below with reference to FIGS. 5 and 6. Note that the schematic elevational view of the steam turbine of this embodiment is similar to FIG. 1 described as a conventional example, so please refer to this as well.
この実施例において社パツキン母材(5)に軸方向に並
列して設けられた複数個の環状(組立の都合上、円周方
向に分割されていても構わない)のパツキン歯(4)K
交差して、軸方向にほぼ平行(多少の傾斜があっても構
わない)な旋回防止歯(6)を円周方向に数個所設ける
。この旋回防止歯(6)の高さは、パツキン歯(4)と
同じか又はそれよシも低くし、ラビリンス歯(4)の回
転体との偶発的接触に対しても、旋回防止歯(6)が回
転体と接触する機会を少なくする。In this embodiment, a plurality of annular packing teeth (4) K (which may be divided in the circumferential direction for convenience of assembly) are provided in parallel in the axial direction on the packing base material (5).
Rotation prevention teeth (6) that intersect and are substantially parallel to the axial direction (some inclination is acceptable) are provided at several locations in the circumferential direction. The height of this anti-swivel tooth (6) is the same as or lower than that of the packing tooth (4), so that the anti-swivel tooth 6) Reduce the chances of contact with the rotating body.
次に作用について説明する。Next, the effect will be explained.
このように構成されたラビリンスパツキンは、隣υ合う
パツキン歯(4)、(4)間の蒸気が回転体であるロー
タQ1(又は羽根)の回転につれて矢印a方向に旋回す
ることを防止す名。これは従来、旋回によシ動圧が低下
し、バラキラ差圧の増加、蒸気漏洩量の増加という欠点
を解消する。矢印すは蒸気の漏洩方向を示す。The labyrinth packing configured in this way prevents the steam between adjacent packing teeth (4), (4) from swirling in the direction of arrow a as the rotor Q1 (or blades) rotates. . This eliminates the conventional drawbacks of a drop in dynamic pressure due to swirling, an increase in differential pressure, and an increase in the amount of steam leakage. The arrow indicates the direction of steam leakage.
無旋回による圧力増加は下記の(102)式、 (10
3)式の関係となる。The pressure increase due to no rotation is expressed by the following equation (102), (10
3) The relationship is as shown in Eq.
、・、 Pb > Pa ・・・
・・・(103)P3は旋回流のある時の圧力
Pbは旋回流のない時の圧力
■aは旋回流速
Vは比容積
lは重力加速度
上記ノ作用はラビリンスパツキンの流量係数にの減少と
なり、第3図曲線(8)として示され、(101)式に
おいて漏洩量の減少が得られる。,..., Pb > Pa...
...(103) P3 is the pressure when there is a swirling flow Pb is the pressure when there is no swirling flow ■ a is the swirling flow velocity V is the specific volume l is the gravitational acceleration The above action results in a decrease in the flow coefficient of the labyrinth packing. , is shown as curve (8) in Figure 3, and a reduction in the leakage amount can be obtained in equation (101).
しかして旋回防止板(6)の挿入は、ノ(ツキン歯(4
)が全周一円輪でなく、複数円弧の合成にすることが一
般的であるから、各円弧間に挿入すればよく、実施が容
易である。However, when inserting the rotation prevention plate (6),
) is generally a composite of multiple circular arcs rather than a single circular ring around the entire circumference, so it is easy to implement as it only needs to be inserted between each circular arc.
尚、本発明は上記し、かつ図面に示した実施例のみに限
定されるものではなく、その要旨を変更しない範囲で、
種々変形して実施できることは勿論である。It should be noted that the present invention is not limited to the embodiments described above and shown in the drawings, but may include the following without changing the gist thereof:
Of course, it can be implemented with various modifications.
以上説明したように、本発明によれば、旋回防止歯によ
シ、ラビリンス内の蒸気旋回を防止する構造としたこと
によシ、旋回による動圧を低下させ、蒸気漏洩量を減少
させ、効率の良い蒸気タービンを提供することができる
。As explained above, according to the present invention, by using the anti-swivel teeth and a structure that prevents steam from swirling within the labyrinth, the dynamic pressure caused by swirling is reduced, and the amount of steam leakage is reduced. A highly efficient steam turbine can be provided.
第1図は従来および本発明の一実施例に共通な蒸気ター
ビンの概略構造を示す要部破断立面図、第2図は従来の
場合のラビリンスパツキンを示す縦断面図、第3図は流
量係数を示す曲線図、第4図はタービン損失の割合を示
す分類図、第5図は本発明の蒸気タービンの一実施例に
用いるラビリンスパツキンを示す要部斜視図、第6図は
第5図のA−A線に沿う矢視断面図である。
1・・・ロータ・ケーシング端部グランドラビリンスパ
ラ東−ン
2・・・ロータ・ノズルダイヤスラム内径部ノズルラビ
リンスパツキン
3・・・羽根先端・ノズルダイヤフラム間ラジアルスピ
ルストリップ
4・・・ラビリンス@ 5・・・パツキン母材6
・・・旋回防止歯 10・・・回転体であるロー
タ11・・・タービンケーシング
第 1 図
、1
第 2 図
、^
第3図
一本)力量lIQ隙
第 5 図
第 6 図Fig. 1 is a cutaway elevational view of essential parts showing the schematic structure of a steam turbine common to the conventional steam turbine and an embodiment of the present invention, Fig. 2 is a vertical sectional view showing the labyrinth packing in the conventional case, and Fig. 3 is a flow rate A curve diagram showing coefficients, FIG. 4 is a classification diagram showing the ratio of turbine loss, FIG. FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1... Rotor/casing end grand labyrinth para east 2... Rotor/nozzle diaphragm inner diameter nozzle labyrinth patch skin 3... Radial spill strip between vane tip/nozzle diaphragm 4... Labyrinth @ 5.・Packing base material 6
... Rotation prevention tooth 10 ... Rotor 11 which is a rotating body ... Turbine casing Fig. 1, 1 Fig. 2, ^ Fig. 3 One) Force lIQ gap Fig. 5 Fig. 6
Claims (1)
スパツキンを設置た蒸気タービンにおいて、ラビリンス
パツキンは回転体の外周を取巻く環状のパツキン歯に交
差して、回転体の軸方向にには平行な旋回防止歯を設け
た仁とを特徴とする蒸気タービン。In a steam turbine equipped with a labyrinth packing as a device to prevent steam leakage from around the rotating body, the labyrinth packing intersects with the annular packing teeth surrounding the outer periphery of the rotating body and rotates parallel to the axial direction of the rotating body. A steam turbine characterized by a groove provided with preventive teeth.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10994082A JPS59505A (en) | 1982-06-28 | 1982-06-28 | Steam turbine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10994082A JPS59505A (en) | 1982-06-28 | 1982-06-28 | Steam turbine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS59505A true JPS59505A (en) | 1984-01-05 |
Family
ID=14522963
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP10994082A Pending JPS59505A (en) | 1982-06-28 | 1982-06-28 | Steam turbine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS59505A (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4643637A (en) * | 1985-09-13 | 1987-02-17 | Elliott Turbomachinery Co., Inc. | Remote operated turning gear engager |
JPH01247702A (en) * | 1988-02-18 | 1989-10-03 | Westinghouse Electric Corp <We> | Labylinth-seal |
US5439347A (en) * | 1994-08-31 | 1995-08-08 | Brandon; Ronald E. | Turbine tip seal damage protection means |
US5707064A (en) * | 1993-01-08 | 1998-01-13 | The Texas A&M University System | Modulated pressure damper seal |
US5794942A (en) * | 1993-01-08 | 1998-08-18 | The Texas A&M University System | Modulated pressure damper seals |
US6722850B2 (en) * | 2002-07-22 | 2004-04-20 | General Electric Company | Endface gap sealing of steam turbine packing seal segments and retrofitting thereof |
US6910856B2 (en) * | 2002-09-21 | 2005-06-28 | Mtu Aero Engines Gmbh | Run-in coating for axial-flow compressor of gas turbine engines and method of using and making same |
EP2249066A1 (en) * | 2009-05-07 | 2010-11-10 | Siemens Aktiengesellschaft | Sealing apparatus and method for steam turbines |
WO2013058112A1 (en) | 2011-10-21 | 2013-04-25 | 三菱重工業株式会社 | Seal device |
JP2015129512A (en) * | 2014-01-02 | 2015-07-16 | ゼネラル・エレクトリック・カンパニイ | Steam turbine and methods of assembling the same |
JP2015166636A (en) * | 2015-07-01 | 2015-09-24 | 三菱重工業株式会社 | Seal device |
-
1982
- 1982-06-28 JP JP10994082A patent/JPS59505A/en active Pending
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4643637A (en) * | 1985-09-13 | 1987-02-17 | Elliott Turbomachinery Co., Inc. | Remote operated turning gear engager |
JPH01247702A (en) * | 1988-02-18 | 1989-10-03 | Westinghouse Electric Corp <We> | Labylinth-seal |
US5707064A (en) * | 1993-01-08 | 1998-01-13 | The Texas A&M University System | Modulated pressure damper seal |
US5794942A (en) * | 1993-01-08 | 1998-08-18 | The Texas A&M University System | Modulated pressure damper seals |
US5439347A (en) * | 1994-08-31 | 1995-08-08 | Brandon; Ronald E. | Turbine tip seal damage protection means |
US6722850B2 (en) * | 2002-07-22 | 2004-04-20 | General Electric Company | Endface gap sealing of steam turbine packing seal segments and retrofitting thereof |
US6910856B2 (en) * | 2002-09-21 | 2005-06-28 | Mtu Aero Engines Gmbh | Run-in coating for axial-flow compressor of gas turbine engines and method of using and making same |
EP2249066A1 (en) * | 2009-05-07 | 2010-11-10 | Siemens Aktiengesellschaft | Sealing apparatus and method for steam turbines |
WO2010127944A1 (en) * | 2009-05-07 | 2010-11-11 | Siemens Aktiengesellschaft | Sealing apparatus and method for steam turbines |
CN102414490A (en) * | 2009-05-07 | 2012-04-11 | 西门子公司 | Sealing apparatus and method for steam turbines |
CN102414490B (en) * | 2009-05-07 | 2015-05-20 | 西门子公司 | Sealing apparatus and method for steam turbines |
WO2013058112A1 (en) | 2011-10-21 | 2013-04-25 | 三菱重工業株式会社 | Seal device |
JP2013087935A (en) * | 2011-10-21 | 2013-05-13 | Mitsubishi Heavy Ind Ltd | Seal device |
JP2015129512A (en) * | 2014-01-02 | 2015-07-16 | ゼネラル・エレクトリック・カンパニイ | Steam turbine and methods of assembling the same |
JP2015166636A (en) * | 2015-07-01 | 2015-09-24 | 三菱重工業株式会社 | Seal device |
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