JPH02181002A

JPH02181002A - Double flow turbine plant

Info

Publication number: JPH02181002A
Application number: JP7289A
Authority: JP
Inventors: Yoshihide Nakamura; 吉秀中村
Original assignee: Individual
Current assignee: Individual
Priority date: 1989-01-05
Filing date: 1989-01-05
Publication date: 1990-07-13

Abstract

PURPOSE:To reduce variation in turbine inputs and eliminate also the drain of cooling water in the title turbine wherein the fluid steam having heat of condensation smaller than that of a water steam is used together with the water steam by recovering the heat of condensation in a condenser through a heat pump system. CONSTITUTION:Each fluid fed from a turbine 1 is condensated in liquid in a condenser 2, then being pressurized in a condensate pump 3, to be thus led in a separator 4. The fluid fed from the separator 4 is pressurized in a liquid feed pump 5 and a water feed pump 6, followed by heating in a fed liquid heater 7 to be evaporated in steam in an evaporator 8. The resultant steam is made to pass through plural auxiliary heaters 9, 10 and then returned to the turbine 1 through a steam mixer 11. Besides, refrigerant fed from a compressor 12 passes through an auxiliary heater 13 and then heats the liquid in the evaporator 8 while being expanded in respective expansion valves 15, 16 to absorb heat in the condenser 2 and respective evaporators 17, 18, followed by returning to the compressor 12 through the auxiliary heater 19. The turbine 1 is directly connected with the compressor 12 by means of an electric motor serving as a generator 20.

Description

【発明の詳細な説明】（産業上の利用分野）本発明は、一般用動力発生タービンプラント。[Detailed description of the invention] (Industrial application field) The present invention relates to a power generation turbine plant for general use.

複数のタービンを有する場合の低温低圧側タービンプラ
ント、温水熱源タービンプラントなどで、しかもタービ
ン内で流体の一部に凝縮（湿り蒸気）が発生するタービ
ンプラントに関する。ここで、低温とは約２００℃以下
のことをいう。The present invention relates to a turbine plant such as a low-temperature, low-pressure side turbine plant or a hot water heat source turbine plant that has a plurality of turbines, and in which condensation (wet steam) occurs in a part of the fluid within the turbine. Here, low temperature means about 200°C or lower.

（従来の技術）複数の作動流体をタービンに同時に使用して、かつ流体
間の凝縮比率を変化させる従来技術としては特開昭６３
−１５．９６０７号、特開昭６３１７０５０８号があっ
た。それらには作動流体として水蒸気および炭化水素（
Ｃ６Ｈ１４・・・ベキ１ナンなど、Ｃ７Ｈ１６・・・ヘ
プタンなど）などの蒸気が記載されている。(Prior art) A conventional technology for simultaneously using a plurality of working fluids in a turbine and changing the condensation ratio between the fluids is disclosed in Japanese Patent Laid-Open No. 63
-15.9607 and JP-A-63170508. They contain water vapor and hydrocarbons (
Vapors such as C6H14... 1nan, C7H16... heptane, etc.) are described.

また、タービンの凝縮器を冷却する水としては、従来は
一般に海水、河川水などの自然水によっていた。Furthermore, conventionally, natural water such as seawater or river water has been used as water for cooling the condenser of the turbine.

（発明が解決しようとする問題点〉凝縮器に捨てる熱を少なくしようとすれば、前記出願の
技術では炭化水素の蒸気の割合いを多くすることになる
。その場合、タービン内での膨張比率が小さく出力に対
しては不利であった。一方、膨張比率を大きくするには
凝縮器の温度を下げれば可能だが、冷却水として使用す
る海水、河１水などの自然水の温度のコントロールは困
難である。(Problem to be solved by the invention) In order to reduce the amount of heat discarded to the condenser, the technology of the above-mentioned application requires an increase in the proportion of hydrocarbon steam.In that case, the expansion ratio in the turbine increases. On the other hand, it is possible to increase the expansion ratio by lowering the temperature of the condenser, but it is difficult to control the temperature of natural water such as seawater or river water used as cooling water. Have difficulty.

また、凝縮器を冷却する冷却水の温度は季節変動を受け
て変化するため季節によるタービンの出力変動もあった
。さらに、暖まった冷却水の排水による環境への影響も
存在した。Additionally, since the temperature of the cooling water used to cool the condenser changes with seasonal fluctuations, there were seasonal fluctuations in the output of the turbine. Furthermore, there was also an environmental impact due to the discharge of warm cooling water.

（問題点を解決するための手段）本発明は、水の蒸気と、水より凝縮熱の小さい少なくと
も１つの流体の蒸気とをタービン内で同時に用い、ター
ビン内で水の蒸気が凝縮する割合いが、水の蒸気の割合
いに比べて大きい複流体ターンプラントにおいて、凝縮
器での凝縮熱をヒートポンプ系統で回収することを特徴
とする複流体タービンプラントからなる。(Means for Solving the Problems) The present invention uses water vapor and the vapor of at least one fluid having a smaller heat of condensation than water at the same time in a turbine, and increases the rate at which the water vapor condenses in the turbine. However, in a multi-fluid turn plant where the proportion of steam is larger than that of water, the plant consists of a multi-fluid turbine plant characterized in that the heat of condensation in the condenser is recovered by a heat pump system.

（作用）単流体（水蒸気）タービンプラン１〜の凝縮熱をヒート
ポンプ系統で回収することは、このプラントの熱効率か
低くて全く不利なことであったか、一方、本復流体ター
ビンプラン１〜は熱効率が高いので凝縮器に排出する熱
も少なく、ピー１〜ポンプ系統と組合わせても全くの不
利ではなく、凝縮器の温度をコントロールでき、なおか
つ環境への影響も少ない、。(Function) Recovering the condensation heat of the single fluid (steam) turbine plan 1~ using the heat pump system would have been completely disadvantageous due to the low thermal efficiency of this plant. Since it is expensive, less heat is discharged to the condenser, so there is no disadvantage at all even if it is combined with the P1 pump system, the temperature of the condenser can be controlled, and there is little impact on the environment.

本発明でいうピー１〜ポンプ系統とは、圧縮機、蒸発器
、彫版弁、凝縮器なとの、ビー１〜ポンプは能を発揮す
るために必要な機器類の集合をいう、。In the present invention, the P1 pump system refers to a collection of equipment such as a compressor, evaporator, engraving valve, condenser, etc. that are necessary for the B1 pump to perform its functions.

また、タービンの作動流体は、水と第２流体との組合わ
せの他に、水以外の流体（例えば、各種アルコール類・
・・凝縮熱が第２流体より高い）と第２流体との組合わ
せも右−効である、。In addition to the combination of water and the second fluid, the working fluid of the turbine may also include fluids other than water (for example, various alcohols,
...the heat of condensation is higher than the second fluid) and the second fluid are also right-effect.

（実施例）第１図は２本発明の実施例である。(Example) FIG. 1 shows two embodiments of the present invention.

タービン１から出た流体は、凝縮器（復液器）２で液体
となった後に凝縮ポンプ３て加圧され、分離器（比重に
よる方式）４に入る。分離器４を出たそれぞれの流体は
給液ポンプ５及び給水ポンプ６で加圧され、給液加熱器
７．で加熱され、蒸発器８で蒸気となり、補助加熱器９
，１０を通過し、蒸気混合器１１て混合されＣタービン
に戻る一方、ヒフ１〜ポンプ系統では、圧縮機１２を出
た冷媒は、補助加熱器１３を通過し、蒸発器（作動流体
は蒸発、冷媒は凝縮）８でタービン系統の流体を加熱し
、彫版弁１５．１６で彫版し、凝縮器（作動流体は凝縮
、冷媒は蒸発）２及び蒸発器１７．１８で熱を吸収し、
補助加熱器１９を通過して圧縮機１２に戻る。ここで、
補助加熱器１３は、主に冷媒の加熱に、補助加熱器１９
は、冷媒の加熱、加圧にそれぞれ必要に応じて用いられ
る。また、蒸発器１７．１８の熱源としては、温水や海
水（好ましくは暖かい黒潮）でもよい。The fluid discharged from the turbine 1 becomes a liquid in a condenser (condenser) 2, is pressurized by a condensing pump 3, and enters a separator (type based on specific gravity) 4. Each fluid exiting the separator 4 is pressurized by a feed pump 5 and a feed water pump 6, and then sent to a feed liquid heater 7. It is heated in
. , refrigerant is condensed) 8 heats the fluid in the turbine system, engraving valve 15.16 engraves, condenser (working fluid condenses, refrigerant evaporates) 2 and evaporator 17.18 absorbs heat. ,
It passes through the auxiliary heater 19 and returns to the compressor 12. here,
The auxiliary heater 13 is mainly used for heating the refrigerant, and the auxiliary heater 19
are used for heating and pressurizing the refrigerant, respectively, as necessary. Further, the heat source for the evaporators 17 and 18 may be warm water or seawater (preferably warm Kuroshio current).

タービンと圧縮機は電動機兼発電機２０と直結している
。起動時は、電動機として使用し、タービンの出力が高
くなるにしたがって電動機としての役割が減少する。そ
してタービン出力が圧縮機駆動力を上回ると発電機とし
て使用する。The turbine and compressor are directly connected to a motor/generator 20. At startup, it is used as an electric motor, and as the output of the turbine increases, its role as an electric motor decreases. When the turbine output exceeds the compressor driving force, it is used as a generator.

第２図は、ピー１〜ポンプ系統のなかの圧縮機と彫版弁
を各２次にしたもので熱効率の向上を意図したものであ
る。また、それらの各々の次数は２段以上の複数次でも
よい。なお、この場合のタービン系統は第１図のものと
同一である。１次圧縮は３１を出た冷媒は、熱交換器３
６で加熱され、２次圧縮機３２で加圧され、補助加熱器
３３を通過し、蒸発器３４でタービン系統の流体を蒸発
させ、１次彫版弁で彫版され、熱交換器３６を通り、２
次彫版弁３７．３８でさらに彫版され、凝縮器４３と蒸
発器３９．　／ＩＯで熱を受け、補助加熱器／１．１を
経て１次圧縮機３１に戻る。FIG. 2 shows a system in which the compressor and the engraving valve in the P1-pump system are each made secondary, with the intention of improving thermal efficiency. Further, each of these orders may be of two or more stages. Note that the turbine system in this case is the same as that shown in FIG. For primary compression, the refrigerant that exits 31 is transferred to heat exchanger 3
6, is pressurized by the secondary compressor 32, passes through the auxiliary heater 33, evaporates the turbine system fluid in the evaporator 34, is engraved by the primary engraving valve, and passes through the heat exchanger 36. street, 2
The next engraving valves 37, 38 are further engraved, the condenser 43 and the evaporator 39. /IO receives heat and returns to the primary compressor 31 via the auxiliary heater /1.1.

（発明の効果〉本発明によれば、ヒートポンプ系統で凝縮器を冷却する
ので、凝縮器の温度の］ン］〜日−ルが可能でありター
ビン出力の変動も小さくできる。また、冷却水の排水が
不要になるため環境への影響も少ない。(Effects of the Invention) According to the present invention, since the condenser is cooled by the heat pump system, it is possible to adjust the temperature of the condenser to ~10 days, and to reduce fluctuations in the turbine output. It also has less impact on the environment as no waste water is required.

[Brief explanation of the drawing]

第１図、第２図は、この発明による実施例。１・・・タービン、１２・・・圧縮機。 FIG. 1 and FIG. 2 show an embodiment according to the present invention. 1...Turbine, 12...Compressor.

Claims

[Claims]

(1) Water vapor and at least one substance with a smaller heat of condensation than water
In a dual-fluid turbine plant, the condensation rate of the water vapor in the turbine is larger than that of the water vapor. A dual-fluid turbine plant that is characterized by the fact that it recovers at