JPS6267206A - Warming up device for intermediate pressure turbine - Google Patents
Warming up device for intermediate pressure turbineInfo
- Publication number
- JPS6267206A JPS6267206A JP20652185A JP20652185A JPS6267206A JP S6267206 A JPS6267206 A JP S6267206A JP 20652185 A JP20652185 A JP 20652185A JP 20652185 A JP20652185 A JP 20652185A JP S6267206 A JPS6267206 A JP S6267206A
- Authority
- JP
- Japan
- Prior art keywords
- pressure turbine
- steam
- turbine
- warming
- intermediate pressure
- 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
Landscapes
- Control Of Turbines (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、蒸気タービンの暖機装置に係り、特に、中圧
タービンの暖機を行うのに好適な装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a warm-up device for a steam turbine, and particularly to a device suitable for warming up an intermediate-pressure turbine.
発明に最も近い公知例・・・特開昭５８−６７９０９大
容量蒸気タービンでは、主蒸気温度が５００℃以上とな
ることが主流となっている。このため、冷機起動時には
、タービンの金属温度と蒸気温度との差が大きいため、
過大な熱応力が発生し、機器の寿令を縮める心配がある
。特に、主蒸気導入部にある高圧タービンではこれが苛
酷であり、口−タは、遠心応力を伴うためロータ表面に
亀裂を生じることがある。さらに、ベースロード用１０
１００Ｏ級の大容量火力、原子カプラントの建設が進み
、従来の既設火力プラントは、電力の需給に合わせて運
用されるため、起動・停止が頻繁に行われ、タービンの
寿命を縮める心配がある。この冷機起動時のロータの寿
令消費を最小限にとどめるために、起動前にロータをタ
ーニングさせながら、高圧タービンへ補助蒸気系から適
度の加熱用蒸気を送り込み、ロータを一定の温度迄加熱
する、いわゆる、暖機運転を実施する方法が採用される
ようになった０通常の運転では、ボイラで発生した主蒸
気は、主蒸気管、主蒸気止め弁、加減弁を経て高圧ター
ビンに流入し、仕事をしたのち、高圧排気口を出て低温
再熱蒸気管を通り、再熱器に至る。再熱器で再び加熱さ
れた蒸気は、高温再熱蒸気管を通り、再熱蒸気止め弁を
経て、中圧タービンに入って仕事をした後、連絡管を通
り、低圧タービンに流入し仕事をし、復水器に至る系統
となっている。一方、冷機起動時、高圧タービンの暖機
を行う場合には、主蒸気止め弁、再熱蒸気止め弁を閉じ
てタービンを起動させる前に復水器を作動させ、タービ
ン内部を真空にしたのち、ターニングにより、ロータを
低速回転させ、且つ、高圧タービン入口にある加減弁を
開いた状態で暖機蒸気を低温再熱蒸気管に接続した暖機
蒸気管を通して補助蒸気へラダーから低温再熱蒸気管に
送り込む。暖機用蒸気は、低温再熱蒸気管から高圧排気
口を経て高圧タービンへ流入し、通常タービン運転状態
とは逆に高圧後段落から前段落側へと流れ、高圧ロータ
を加熱暖機する。暖機を終えた蒸気の大部分は、加減弁
を通って主蒸気止め弁後部に設けた主蒸気ドレン弁を経
て、主蒸気ドレン管により復水器に排出される。また、
暖機蒸気の一部は、高圧タービンの中圧タービン側に設
置されているグランドパツキンとロータとの微小隙間を
経て、中圧タービンに流入する。このようにして高圧タ
ービンの暖機が行われるが、中圧タービンの場合には、
中圧タービン排気口が低圧タービンと連絡管により連絡
されているために、中圧り−ビンに暖機蒸気を送り込ん
でも、中圧タービン排気口が連絡管によって低圧タービ
ンに接続されているために、常に、真空状態となってい
るため、中圧タービンは、はとんど加熱されない、この
ため、高圧タービンの寿令消費は緩和されるが、中圧タ
ービンの寿令消費は、はとんど緩和されない。Known example closest to the invention...Japanese Unexamined Patent Publication No. 58-67909 In large-capacity steam turbines, the main steam temperature is generally 500° C. or higher. For this reason, during cold startup, there is a large difference between the turbine metal temperature and the steam temperature.
There is a concern that excessive thermal stress will occur and the service life of the equipment will be shortened. This is particularly severe for high-pressure turbines located in the main steam introduction section, and cracks may occur on the rotor surface because the rotor is subject to centrifugal stress. In addition, 10 for base load
The construction of 100O class large capacity thermal power plants and nuclear power plants is progressing, and existing thermal power plants are operated according to the demand and supply of electricity, so they are started and stopped frequently, and there is a concern that the lifespan of the turbines will be shortened. In order to minimize the life consumption of the rotor during cold start-up, the rotor is turned before start-up, and an appropriate amount of heating steam is sent from the auxiliary steam system to the high-pressure turbine to heat the rotor to a certain temperature. During normal operation, the main steam generated in the boiler flows into the high-pressure turbine via the main steam pipe, main steam stop valve, and control valve. After doing its work, it exits the high-pressure exhaust port and passes through the low-temperature reheat steam pipe to the reheater. The steam reheated in the reheater passes through the high-temperature reheat steam pipe, passes through the reheat steam stop valve, enters the intermediate pressure turbine and performs work, and then passes through the connecting pipe and flows into the low pressure turbine where it performs work. The system is connected to the condenser. On the other hand, when warming up the high-pressure turbine during a cold start, before starting the turbine by closing the main steam stop valve and reheat steam stop valve, operate the condenser to create a vacuum inside the turbine. By turning, the rotor is rotated at a low speed, and the control valve at the high-pressure turbine inlet is opened, and the warm-up steam is passed through the warm-up steam pipe connected to the low-temperature reheat steam pipe to the auxiliary steam from the rudder to the low-temperature reheat steam. feed into the tube. The warm-up steam flows into the high-pressure turbine from the low-temperature reheat steam pipe through the high-pressure exhaust port, and flows from the high-pressure rear stage to the front stage side, contrary to the normal turbine operating state, to heat and warm up the high-pressure rotor. Most of the steam that has been warmed up passes through the control valve, passes through the main steam drain valve provided at the rear of the main steam stop valve, and is discharged to the condenser through the main steam drain pipe. Also,
A portion of the warm-up steam flows into the intermediate-pressure turbine through a small gap between the rotor and the gland packing installed on the intermediate-pressure turbine side of the high-pressure turbine. This is how high-pressure turbines are warmed up, but in the case of intermediate-pressure turbines,
Because the intermediate-pressure turbine exhaust port is connected to the low-pressure turbine by a connecting pipe, even if warm-up steam is sent to the intermediate-pressure turbine, the intermediate-pressure turbine exhaust port is connected to the low-pressure turbine by a connecting pipe. Since the intermediate pressure turbine is always in a vacuum state, it is hardly heated.For this reason, the life consumption of the high pressure turbine is alleviated, but the life consumption of the intermediate pressure turbine is extremely low. There is no relief.
また、冷機起動時は、回転体であるロータと静止体であ
る車室の熱膨張伸び増加率の差に起因する伸び差が過大
となり易く、このため、回転体と静止体との隙間も伸び
差を考慮した値として設定しである。冷機起動時は、ロ
ータの熱膨張伸び増加率が大きいため、伸び差を緩和す
るには、車室を予めある程度熱膨張させることが有効で
あるが、前述のように、高圧タービンの場合、暖機運転
により実施できるが、中圧タービンの場合は、はとんど
実施出来ないため、その効果が半減していた。In addition, when starting a cold machine, the difference in expansion due to the difference in the rate of increase in thermal expansion and elongation between the rotor, which is a rotating body, and the casing, which is a stationary body, tends to become excessive, and therefore the gap between the rotating body and the stationary body also increases. It is set as a value that takes into account the difference. When starting a cold engine, the rate of increase in thermal expansion and elongation of the rotor is large, so in order to alleviate the difference in expansion, it is effective to allow the casing to undergo some thermal expansion in advance.However, as mentioned above, in the case of a high-pressure turbine, This can be done by machine operation, but in the case of medium-pressure turbines, it is almost impossible to do so, and its effectiveness has been halved.
本発明の目的は、中圧タービンの暖機を可能として寿令
消費の緩和、冷機起動時の伸び差減少。The purpose of the present invention is to make it possible to warm up an intermediate-pressure turbine, reduce life consumption, and reduce the difference in growth when starting a cold engine.
起動時間の短縮を図り、より信頼性の高い高効率なター
ビンを提供することにある。The aim is to shorten start-up time and provide a more reliable and highly efficient turbine.
本発明は、中圧タービンと低圧タービンとの連絡管に仕
切り弁を設け、仕切り弁により中圧タービンと低圧ター
ビン間の流路を遮断し、中圧タービンの暖機が可能とな
るようにしたものである。The present invention provides a gate valve in the communication pipe between the intermediate pressure turbine and the low pressure turbine, and the gate valve blocks the flow path between the intermediate pressure turbine and the low pressure turbine, thereby making it possible to warm up the intermediate pressure turbine. It is something.
本発明の一実施例を図により説明する。An embodiment of the present invention will be described with reference to the drawings.
高圧タービン１と中圧タービン２は、一つの車室内に構
成されており、中間グランドパツキン３が高圧タービン
１から中圧タービン２への蒸気漏洩を最小限にするよう
に設けられている。中圧タービン２と、復水器４とを連
接した低圧タービン５は、連絡管６により連絡されてお
り、連絡管６の途中に、手動、あるいは、電動に依り作
動する仕切り弁７を設けである。冷機起動時の暖機運転
時には、主蒸気止め弁８．再熱蒸気止め弁９．抽気止め
弁１０．仕切り弁７を閉じ、高圧暖機蒸気１１を低温再
熱蒸気管１２へ送り、中圧タービン暖機蒸気１３を中圧
タービン抽気管１４へ送る。The high-pressure turbine 1 and the intermediate-pressure turbine 2 are arranged in one cabin, and an intermediate gland packing 3 is provided to minimize steam leakage from the high-pressure turbine 1 to the intermediate-pressure turbine 2. The medium-pressure turbine 2 and the low-pressure turbine 5 connected to the condenser 4 are connected by a connecting pipe 6, and a gate valve 7 that is operated manually or electrically can be provided in the middle of the connecting pipe 6. be. During warm-up operation when starting a cold engine, the main steam stop valve 8. Reheat steam stop valve9. Bleed stop valve 10. The gate valve 7 is closed, the high-pressure warm-up steam 11 is sent to the low-temperature reheat steam pipe 12, and the intermediate-pressure turbine warm-up steam 13 is sent to the intermediate-pressure turbine bleed pipe 14.
高圧タービン１および中圧タービン２は、はとんど密閉
された状態となるため、中圧タービンの暖機が可能とな
る。実施例によれば、中圧タービンの暖機が可能となる
ため、中圧タービンの冷機起動時の寿令消費を緩和出来
る。また、冷機起動時の伸び差を減少出来ることから回
転体と静止体との軸方向隙間を小さくすることにより、
熱効率を向上させ、起動時間も短縮することが出来る。Since the high-pressure turbine 1 and the intermediate-pressure turbine 2 are almost in a sealed state, the intermediate-pressure turbine can be warmed up. According to the embodiment, since the intermediate pressure turbine can be warmed up, the life consumption of the intermediate pressure turbine during cold startup can be alleviated. In addition, by reducing the axial gap between the rotating body and the stationary body, it is possible to reduce the difference in expansion when starting the cold machine.
It can improve thermal efficiency and shorten startup time.
本発明によれば、中圧タービンの暖機が可能となるため
、中圧タービンの冷機起動時の寿令消費の緩和、伸び差
減少、起動時間の短縮が図れ、より信頼性の高いタービ
ンを供給することが出来る。According to the present invention, since it is possible to warm up the intermediate pressure turbine, it is possible to alleviate the life consumption during cold startup of the intermediate pressure turbine, reduce the difference in elongation, and shorten the startup time, resulting in a more reliable turbine. can be supplied.
図は、本発明の一実施例の蒸気タービンの系統図である
。
２・・・中圧タービン、５・・・低圧タービン、６・・
・連絡管、７・・・仕切り弁。The figure is a system diagram of a steam turbine according to an embodiment of the present invention. 2...Intermediate pressure turbine, 5...Low pressure turbine, 6...
・Communication pipe, 7...gate valve.
Claims (1)
気タービンにおいて、前記中圧タービンと前記低圧ター
ビンの連絡管に仕切り弁を設けたことを特徴とする中圧
タービン暖機装置。1. An intermediate-pressure turbine warm-up device, characterized in that, in a steam turbine in which a low-pressure turbine and a central turbine are connected through a connecting pipe, a gate valve is provided in the connecting pipe between the intermediate-pressure turbine and the low-pressure turbine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20652185A JPS6267206A (en) | 1985-09-20 | 1985-09-20 | Warming up device for intermediate pressure turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20652185A JPS6267206A (en) | 1985-09-20 | 1985-09-20 | Warming up device for intermediate pressure turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6267206A true JPS6267206A (en) | 1987-03-26 |
Family
ID=16524739
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20652185A Pending JPS6267206A (en) | 1985-09-20 | 1985-09-20 | Warming up device for intermediate pressure turbine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6267206A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012517550A (en) * | 2009-02-10 | 2012-08-02 | シーメンス アクティエンゲゼルシャフト | Turbine shaft heating method |
| US11333564B2 (en) | 2018-04-09 | 2022-05-17 | Nidec Copal Electronics Corporation | Strain sensor fixing device for a torque sensor to prevent sensor performance decrease |
-
1985
- 1985-09-20 JP JP20652185A patent/JPS6267206A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012517550A (en) * | 2009-02-10 | 2012-08-02 | シーメンス アクティエンゲゼルシャフト | Turbine shaft heating method |
| US11333564B2 (en) | 2018-04-09 | 2022-05-17 | Nidec Copal Electronics Corporation | Strain sensor fixing device for a torque sensor to prevent sensor performance decrease |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0605156B1 (en) | Method of effecting start-up of a cold steam turbine system in a combined cycle plant | |
| CN109826681B (en) | Industrial heating system for gas-steam combined cycle unit steam extraction integration and operation method thereof | |
| CN109869204B (en) | Heat supply and power peak regulation coupling system for gas-steam combined cycle unit and operation method thereof | |
| JPS61237802A (en) | Warming-up method for steam turbine | |
| CN207245763U (en) | A kind of high temperature gas cooled reactor Turbine Steam gland sealing steam supply system | |
| CN113404551A (en) | Shaft seal steam supply system of gas-steam combined cycle heat supply unit and operation method | |
| CN110793011A (en) | Two-stage steam extraction type medium-temperature and medium-pressure waste incineration power generation system and use method thereof | |
| CN109869784B (en) | Combined cycle device for steam extraction integration and heat accumulation peak shaving coupling and operation method thereof | |
| US11879365B2 (en) | Steam turbine plant and operation method, combined cycle plant and operation method | |
| CN211975088U (en) | Reverse-heating cold-state starting system of condensing turbine generator set | |
| JP3559574B2 (en) | Startup method of single-shaft combined cycle power plant | |
| US20160146060A1 (en) | Method for operating a combined cycle power plant | |
| JPS6267206A (en) | Warming up device for intermediate pressure turbine | |
| RU137999U1 (en) | MANEUVERED HEATING TURBO INSTALLATION | |
| JP2004245184A (en) | Reheat steam turbine plant and starting method for the plant | |
| JPH09303114A (en) | Steam cycle for combined cycle using steam cooling type gas turbine | |
| CN212673163U (en) | Steam heating starting system of once-through boiler | |
| CN110925036B (en) | Low-pressure cylinder flexible output cooling system under steam extraction heat supply working condition and operation method thereof | |
| JPS5993907A (en) | Quick starting device for combined-cycle power generation plant | |
| SU1125393A1 (en) | Method of starting cold and non-cooled electric power station power unit | |
| JPS60159311A (en) | Starting method for steam turbine | |
| CN216110877U (en) | Gas-steam combined cycle heat supply unit shaft seal steam supply system | |
| CN219452197U (en) | Steam turbine exhaust utilization system | |
| SU682662A1 (en) | Starting system of a power unit | |
| CN219344774U (en) | Quick jar system of heating of unit |