JPH0454122B2 - - Google Patents
Info
- Publication number
- JPH0454122B2 JPH0454122B2 JP20099183A JP20099183A JPH0454122B2 JP H0454122 B2 JPH0454122 B2 JP H0454122B2 JP 20099183 A JP20099183 A JP 20099183A JP 20099183 A JP20099183 A JP 20099183A JP H0454122 B2 JPH0454122 B2 JP H0454122B2
- Authority
- JP
- Japan
- Prior art keywords
- condensate
- pump
- pressure
- power generation
- water
- 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
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 85
- 238000010248 power generation Methods 0.000 claims description 37
- 238000007789 sealing Methods 0.000 claims description 35
- 230000006870 function Effects 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 7
- 230000008878 coupling Effects 0.000 description 5
- 238000010168 coupling process Methods 0.000 description 5
- 238000005859 coupling reaction Methods 0.000 description 5
- 238000010612 desalination reaction Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- Mechanical Treatment Of Semiconductor (AREA)
- Eye Examination Apparatus (AREA)
- Jellies, Jams, And Syrups (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、復水タービンを備えた発電プラント
の復水昇圧装置に係り、特に、該昇圧装置の動力
損失防止及び蒸気発生装置用給水ポンプ封水供給
圧力低下防止を図り得るように改良した復水昇圧
装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a condensate pressure booster for a power plant equipped with a condensate turbine, and in particular to prevention of power loss in the booster and a feed water pump seal for a steam generator. This invention relates to a condensate pressure booster that has been improved to prevent a drop in water supply pressure.
従来の発電プラントにおける復水昇圧装置の１
例を第１図に示す。蒸気発生装置（図示せず）で
発生した蒸気は管路１により蒸気タービン２に導
入され、このタービンの中で膨張し、その熱エネ
ルギーは該タービンにより回転運動エネルギーに
変換され、タービンに連結された発電機３により
電力となる。タービン内で膨張した蒸気は復水器
４において、海水、河川水又は大気により冷却凝
縮し復水となる。復水は電動機６により駆動され
る復水ポンプ５により昇圧され、復水脱塩装置７
を経て、電動機９により駆動される復水昇圧ポン
プ８により、更に、昇圧される。再昇圧された復
水は管路１０を通して復水流量検出器１１により
流量を計測されたのち、脱気器水位調節弁１２、
低圧給水加熱器１３を介して脱気器１４に送水さ
れる。脱気器に一旦貯水された復水は連絡管１８
を経て、給水昇圧ポンプ１９、給水流量検出器１
６を介して給水ポンプ２４に送水され、給水ポン
プ２４において加圧され、管路２１により、蒸気
発生装置（図示せず）に送水される。給水昇圧ポ
ンプ１９は給水ポンプ２０の所要吸込水頭を給水
付与する目的で設置され、給水ポンプの軸封部２
４は、脱気器１４の器内圧加、該脱気器の静水頭
及び給水昇圧ポンプ１９の揚程の和に等しい圧力
となつている。この軸封部２４には、復水昇圧ポ
ンプ８の出口の管路１０から分岐した封水管２２
と封水調節弁２３を介して、低温の復水が封水と
して供給されている。脱気器水位調節弁１２は、
前記の復水流量検出器１１、脱気器水位検出器１
５及び給水流量検出器１６の各信号を加減演算す
る制御器１７により調節される。復水脱塩装置７
及び復水昇圧ポンプ８が設置されない場合もある
が、その場合の従来構成は復水脱塩装置７と復水
昇圧ポンプ８が無いこと以外は前記と同様であ
る。
1 of condensate booster in conventional power plant
An example is shown in FIG. Steam generated in a steam generator (not shown) is introduced into a steam turbine 2 through a line 1, expands in this turbine, and its thermal energy is converted into rotational kinetic energy by the turbine, which is connected to the turbine. Electric power is generated by the generator 3. The steam expanded in the turbine is cooled and condensed in the condenser 4 by seawater, river water, or the atmosphere, and becomes condensed water. The pressure of the condensate is increased by a condensate pump 5 driven by an electric motor 6, and the pressure is increased by a condensate desalination device 7.
After that, the pressure is further increased by the condensate pressure pump 8 driven by the electric motor 9. The re-pressurized condensate passes through the pipe line 10 and has its flow rate measured by the condensate flow rate detector 11, and then passes through the deaerator water level control valve 12,
Water is fed to the deaerator 14 via the low-pressure feedwater heater 13 . The condensate once stored in the deaerator is transferred to the connecting pipe 18.
After that, the water supply pressure pump 19, the water supply flow rate detector 1
6 to the water supply pump 24, the water is pressurized in the water supply pump 24, and the water is supplied to the steam generator (not shown) through the pipe line 21. The water supply booster pump 19 is installed for the purpose of supplying water with the required suction head of the water supply pump 20, and the water supply pump 20 has a shaft sealing portion 2.
4 is a pressure equal to the sum of the internal pressure of the deaerator 14, the static head of the deaerator, and the head of the feedwater boost pump 19. This shaft sealing portion 24 has a water sealing pipe 22 branched from the outlet pipe 10 of the condensate boost pump 8.
Low-temperature condensate is supplied as sealing water via the sealing water regulating valve 23. The deaerator water level control valve 12 is
The aforementioned condensate flow rate detector 11 and deaerator water level detector 1
5 and the water supply flow rate detector 16 by a controller 17 that adds and subtracts each signal. Condensate desalination equipment 7
In some cases, the condensate boost pump 8 is not installed, but in that case, the conventional configuration is the same as described above except that the condensate desalination device 7 and the condensate boost pump 8 are not provided.
第２図に、従来構成における復水昇圧装置の特
性を示す。復水ポンプの揚程曲線HCと復水昇圧
ポンプの揚程曲線HBは、従来構成においては、
定速回転であるため、発電プラントの発電量Ｌに
対し、図示の様に、それぞれ左上りの特性をもつ
単一の曲線となる。第１図に示した様に、復水ポ
ンプ５と復水昇圧ポンプ８とが直列に管路に連接
されているため、復水昇圧ポンプ出口の管路１０
における圧力は揚程曲線HCと揚程曲線HBとの合
成揚程HTによりあらわされる。システムヘツド
曲線PSは復水昇圧ポンプ８から脱気器１４までの
抵抗曲線を示したものであり、脱気器内圧力、管
路等の圧力損失、及び脱気器の静水頭から成る。 FIG. 2 shows the characteristics of a condensate booster with a conventional configuration. In the conventional configuration, the head curve H C of the condensate pump and the head curve H B of the condensate boost pump are:
Since the rotation is at a constant speed, the power generation amount L of the power generation plant becomes a single curve with an upward-left characteristic as shown in the figure. As shown in FIG. 1, since the condensate pump 5 and the condensate boost pump 8 are connected in series to the conduit, the condensate boost pump outlet conduit 10
The pressure at is expressed by the combined head H T of the head curve H C and the head curve H B. The system head curve P S shows the resistance curve from the condensate boost pump 8 to the deaerator 14, and is composed of the pressure inside the deaerator, the pressure loss in the pipes, etc., and the static head of the deaerator.
合成揚程HTは発電プラントの最大運転状態で
ある発電量L0において、システムヘツドよりも
ΔP0の余裕をもち、かつ、第１図に示した給水ポ
ンプの軸封部２４の封水に要する圧力よりも若干
高くなるように設定する。なお、第３図に封水圧
力曲線PBの説明図を添付した。封水圧力PBは、
脱気器器内圧力PD、脱気器の静水頭HS及び給水
昇圧ポンプの揚程曲線HBPの合計によりあらわさ
れる。 The composite head H T has a margin of ΔP 0 than the system head at the power generation amount L 0 , which is the maximum operating state of the power plant, and is required to seal the shaft seal 24 of the water pump shown in Fig. 1. Set it so that it is slightly higher than the pressure. An explanatory diagram of the water sealing pressure curve P B is attached to Figure 3. The sealing pressure P B is
It is expressed by the sum of the deaerator internal pressure P D , the static head H S of the deaerator, and the head curve H BP of the feedwater boost pump.
第４図は、従来構成における合成揚程HTとシ
ステムヘツド曲線PSとの差、すなわち、第１図の
脱気器水位調節弁１２の差圧を斜線部で示したも
のである。システムヘツド曲線PSは発電量Ｌが減
少するに従つて減少する。これは発電量にほぼ比
例し、脱気器の器内圧力が低下し、かつ、復水流
量も同様に発電量にほぼ比例して減少するため
に、復水昇圧ポンプから脱気器までの管路の摩擦
損失が減少することによるものである。一方、復
水ポンプと復水昇圧ポンプとの合成揚程HTは発
電量、すなわち、復水量が減少するのに従つて増
加する。この両者の特性の違いにより、高発電量
L0時にΔP0であつた脱気器水位調節弁の差圧は、
発電量L1においてΔP1に増大する。従来の構成に
おいては、この様に、発電量が低下するのに従
い、脱気器水位調節弁の差圧が増大し、弁の振
動、騒音及びエロージヨンの問題が生じるととも
に、低発電量時に復水ポンプや復水昇圧ポンプの
無効な消費動力を生じるという欠点があつた。 In FIG. 4, the difference between the synthetic head H T and the system head curve P S in the conventional configuration, that is, the differential pressure of the deaerator water level control valve 12 in FIG. 1 is shown by the shaded area. The system head curve P S decreases as the power generation amount L decreases. This is almost proportional to the amount of power generation, and the internal pressure of the deaerator decreases, and the condensate flow rate also decreases almost in proportion to the amount of power generation. This is due to the reduction in friction loss in the pipeline. On the other hand, the combined head H T of the condensate pump and the condensate boost pump increases as the amount of power generation, that is, the amount of condensate decreases. Due to the difference in characteristics between the two, the amount of power generated is high.
The differential pressure of the deaerator water level control valve, which was ΔP 0 at L 0 , is
Increases to ΔP 1 at power generation L 1 . In the conventional configuration, as the amount of power generation decreases, the differential pressure at the deaerator water level control valve increases, causing problems of valve vibration, noise, and erosion, and also causes problems with condensation when the amount of power generation is low. The drawback was that it resulted in ineffective power consumption of the pump and condensate boost pump.
本発明は上述の事情に鑑みて為され、その目的
とするところは、消費動力を可能な限り低減せし
め得る復水昇圧装置を提供するにある。
The present invention has been made in view of the above-mentioned circumstances, and its object is to provide a condensate pressure booster that can reduce power consumption as much as possible.
上記の目的を達成するため、本発明の復水昇圧
装置は、蒸気発生装置と、復水器を備えた蒸気タ
ービンと、上記復水器内の復水を加圧して前記蒸
気発生装置に還流させる可変回転速度形の復水加
圧ポンプと、上記復水加圧ポンプの下流に接続さ
れて軸封水部を備えた給水ポンプと、前記復水加
圧ポンプの下流側から分岐されて上記の軸封水部
に連通する封水管路とを設けた汽力発電プラント
において、前記復水加圧ポンプ下流側復水管に接
続された調節弁の流出、入口間の差圧を予め設定
された値に等しからしめるように、前記復水加圧
ポンプの回転速度を制御する手段を設けたことを
特徴とする。
In order to achieve the above object, the condensate booster of the present invention includes a steam generator, a steam turbine including a condenser, and pressurizes condensate in the condenser and returns it to the steam generator. a variable rotational speed type condensate pressurizing pump, a water supply pump connected downstream of the condensate pressurizing pump and equipped with a shaft water sealing part, and a water supply pump that is branched from the downstream side of the condensate pressurizing pump and having a shaft water sealing part connected downstream of the condensate pressurizing pump. In a steam power generation plant equipped with a water sealing pipe communicating with the shaft water sealing part of the condensate pressurizing pump, the differential pressure between the outlet and the inlet of the control valve connected to the condensate pipe on the downstream side of the condensate pressurizing pump is set to a preset value. The present invention is characterized in that means is provided for controlling the rotational speed of the condensate pressurizing pump so that the rotational speed of the condensate pressurizing pump is equal to .
以下に、本発明の実施の一例を詳述する。第５
図は、復水昇圧装置として、復水ポンプと復水昇
圧ポンプとを有し、該復水昇圧ポンプが流体継手
により、回転数制御される場合についての実施例
を示したものである。蒸気発生器（図示せず）か
らの蒸気は蒸気タービン２に入り、発電機３にて
発電を行う。タービンで仕事をした蒸気は、復水
器４で凝縮したのち、管路により、復水ポンプ
５、復水脱塩装置７、復水昇圧ポンプ８、管路１
０、復水流量検出器１１、脱気器水位調節弁１
２、低圧給水加熱器１３を経て、脱気器１４に一
旦貯水されたのち、管路１８、給水昇圧ポンプ１
９、給水ポンプ２０により蒸気発生装置（図示せ
ず）に還流することは従来技術と同一である。脱
気器水位調節弁１２には差圧検出器２５を設置
し、該検出器信号２６は演算器２７に送られる。
一方、高発電時の目標調節弁差圧を発生する関数
発生器２８と、低発電時の目標調節弁差圧を発生
する関数発生器２９の信号とは、それぞれ、演算
器３０に入力され、発電量又は発電量に比例した
信号３１により、いずれかの関数発生器の信号が
前記演算器２７に送られる。該演算器２７の信号
は比例積分演算器３２により、流体継手３３を制
御する信号となり、該流体継手を介して、電動機
９により駆動される復水昇圧ポンプ８の回転数が
制御される。尚、従来構成と同一の機器について
は同一の番号を付した。本実施例における、復水
昇圧装置の運転特性を第６図に示した。回転数制
御された復水昇圧ポンプの揚程曲線は、回転数が
低下するのにしたがつて、それぞれ、NB1，NB2，
NB3，NB4，NB5，NB6，NB7で示される様に変化
する。このため、一定回転で運転される復水ポン
プの揚程曲線HCとの合成揚程HTは、NT1，NT2，
NT3，NT4，NT5，NT6，NT7で示される様に変化
するが、その場合、復水昇圧ポンプ出口の圧力は
封水圧力PBを満足する必要がある。例えば、発
電量Loにおいて、封水圧力は図示PNT2の値が必要
であるため、回転数はNT2とする様に制御され
る。すなわち、脱気器水位調節弁の差圧が、図示
のΔPoになる様に回転数が制御される。この差圧
は、封水圧力PBとシステムヘツド曲線PSと、復
水ポンプの揚程曲線HCとで囲まれた領域となる。
発電量LSにおいては、封水圧力PNSを確保する必
要がある。第７図に前記関数器２８の関数の例
を、第８図に関数発生器２９の関数の例をそれぞ
れした。本発明によれば、脱気器水位調節弁の差
は、第９図の斜線部となり、従来構成に比べ、差
圧が大幅に減少し、弁の振動、騒音及びエロージ
ヨンの防止と復水昇圧ポンプの消費動力低減に効
果がある事は明らかである。また、第６図で明ら
かな様に、復水ポンプと復水昇圧ポンプを直列に
管路で連結した場合、復水ポンプの揚程曲線HC
とシステムヘツド曲線PSが交わる発電量LSよりも
低い発電量においては、復水昇圧ポンプを停止す
る事が可能である。上述の観点に基づいた実施例
を第１０図に示した。従来構成または前述の発明
の機器と同一の機器については、同一の番号を付
した。番号１〜３３の機器の名称は前述と同一で
ある。復水昇圧ポンプ８は流体継手３３を介して
電動機９により駆動される。負荷メモリー３４に
記憶された復水昇圧ポンプ停止可能発電量（第６
図の発電量LSに相当する。）と実発電量の信号３
５は演算器３６で比較され、電動機９を停止可能
か否かの判定がなされ、可能であれば、電力３７
は、開閉器３８により遮断され、電動機９は停止
する。本発明によれば、プラントの低発電運転
時、復水昇圧ポンプの消費動力を無くすことが可
能となる。
An example of implementing the present invention will be described in detail below. Fifth
The figure shows an embodiment in which the condensate pressure boosting device includes a condensate pump and a condensate pressure pump, and the rotation speed of the condensate pressure pump is controlled by a fluid coupling. Steam from a steam generator (not shown) enters a steam turbine 2, and a generator 3 generates electricity. The steam that has worked in the turbine is condensed in a condenser 4, and then sent to a condensate pump 5, a condensate desalination device 7, a condensate boost pump 8, and a conduit 1 through a condenser.
0, condensate flow rate detector 11, deaerator water level control valve 1
2. After passing through the low-pressure feed water heater 13 and once stored in the deaerator 14, the water is transferred to the pipe line 18 and the feed water boost pump 1.
9. Returning the water to the steam generator (not shown) by the feed water pump 20 is the same as in the prior art. A differential pressure detector 25 is installed in the deaerator water level control valve 12, and the detector signal 26 is sent to a calculator 27.
On the other hand, the signals of the function generator 28 that generates the target control valve differential pressure during high power generation and the function generator 29 that generates the target control valve differential pressure during low power generation are input to the computing unit 30, respectively. A signal from one of the function generators is sent to the arithmetic unit 27 based on the amount of power generation or a signal 31 proportional to the amount of power generation. The signal from the calculator 27 is turned into a signal for controlling the fluid coupling 33 by the proportional-integral calculator 32, and the rotation speed of the condensate boost pump 8 driven by the electric motor 9 is controlled via the fluid coupling. Note that the same numbers are given to devices that are the same as those in the conventional configuration. FIG. 6 shows the operating characteristics of the condensate booster in this example. The head curve of a condensate boost pump with rotation speed control becomes N B1 , N B2 , and N B2 , respectively, as the rotation speed decreases.
It changes as shown by N B3 , N B4 , N B5 , N B6 , and N B7 . Therefore, the combined head H T with the head curve H C of the condensate pump operated at a constant rotation is N T1 , N T2 ,
The pressure changes as shown by N T3 , N T4 , N T5 , N T6 , and N T7 , but in that case, the pressure at the outlet of the condensate boost pump needs to satisfy the sealing water pressure P B . For example, in the power generation amount L o , the sealing pressure needs to have a value of PNT2 shown in the figure, so the rotation speed is controlled to be N T2 . That is, the rotation speed is controlled so that the differential pressure of the deaerator water level control valve becomes ΔP o as shown in the figure. This differential pressure is in the area surrounded by the sealing water pressure P B , the system head curve P S , and the condensate pump head curve H C.
For the power generation amount L S , it is necessary to ensure the water sealing pressure P NS . FIG. 7 shows an example of the function of the function generator 28, and FIG. 8 shows an example of the function of the function generator 29. According to the present invention, the difference in the deaerator water level control valve is shown in the shaded area in Figure 9, and the differential pressure is significantly reduced compared to the conventional configuration, preventing valve vibration, noise, and erosion, and increasing condensate pressure. It is clear that this method is effective in reducing the power consumption of the pump. Furthermore, as shown in Figure 6, when the condensate pump and the condensate booster pump are connected in series through a pipe, the head curve of the condensate pump H C
When the power generation amount is lower than the power generation amount L S at which the system head curve P S intersects with the system head curve P S , it is possible to stop the condensate boost pump. An embodiment based on the above-mentioned viewpoint is shown in FIG. The same numbers are given to devices that have the same conventional configuration or the devices of the invention described above. The names of devices numbered 1 to 33 are the same as above. The condensate boost pump 8 is driven by an electric motor 9 via a fluid coupling 33. The amount of power generation that can be stopped by the condensate booster pump stored in the load memory 34 (6th
This corresponds to the power generation amount L S in the figure. ) and actual power generation signal 3
5 is compared by the calculator 36, and it is determined whether or not the electric motor 9 can be stopped. If possible, the electric power 37 is
is shut off by the switch 38, and the electric motor 9 is stopped. According to the present invention, it is possible to eliminate the power consumption of the condensate boost pump during low power generation operation of the plant.
前述の様に、回転数制御を行う復水昇圧装置の
回転数は、脱気器水位調節弁の上流側の圧力が常
に封水圧力より高くなる様に制御する必要がある
が、以下に述べる発明によれば、その必要が無く
なる。上述の観点に基づいた実施例を第１１図に
示す。従来構成または前述の発明と同一の機器に
ついては、同一の番号を付した。第１１図におい
て、番号１〜３８の機器は既に述べた機能を有し
ている。本発明による構成の例を以下に述べる。
回転数制御を行う復水昇圧ポンプ８の出口の圧力
は、給水ポンプ２０の軸封部２４を封水するため
に必要な圧力以上である事が必要である。したが
つて、該復水ポンプの回転数は管路１０の圧力が
封水を行うために必要な圧力を確保出来るように
行うが、管路１０と軸封部２４を封水調節弁２３
を介して接続する管路２２に、封水昇圧ポンプ３
９を設置する事により、前記復水昇圧ポンプの回
転数は更に、低回転数での運転が可能となる。す
なわち、軸封部を封水するために必要な圧力とシ
ステムヘツドとの圧力差を、本発明による封水昇
圧ポンプがまかなうために、復水昇圧ポンプの回
転数はシステムヘツドにみあつて制御する事が可
能になる。第１２図に本発明の運転特性を示し
た。復水ポンプの揚程曲線HCと復水昇圧ポンプ
の揚程曲線HB，NB1，NB2，NB3，NB4，NB5，
NB6，NB7との合成揚程HT，NT1，NT2，NT3，
NT4，NT5，NT6，NT7，封水圧力PB及びシステム
ヘツド曲線PSは前記第６図と同様である。回転数
制御を行う復水昇圧ポンプ８は発電量La以上の
運転範囲においては、システムヘツド曲線PSが、
封水圧力PBより大きいため、復水昇圧ポンプは
システムヘツドに沿つて回転数を低下させても封
水圧力不足は生じない。発電量Laにおける復水
昇圧ポンプの回転数はNTaになる。発電量Lbにお
いては、封水圧力PBとシステムヘツド曲線PSと
の差ΔPSは、本発明による封水昇圧ポンプによ
り、昇圧されて給水ポンプ軸封部に送水されるた
め、復水昇圧ポンプの回転数はNTbまで低下させ
る事が可能となる。本発明によれば、復水昇圧ポ
ンプはシステムヘツドに沿つた運転が可能となる
ため、脱気器水位調節弁の差圧はほとんど無くな
ることになり、弁の騒音等の防止及び復水昇圧ポ
ンプの消費動力低減に効果がある事は明らかであ
る。但し、本発明を実施する場合、第７図及び第
８図に示した関数は、全発電域において、脱気器
水位制御上必要とされる弁の差圧、約0.5Kg／cm2
一定となる様にしなければならない。本発明を実
施した場合の脱気器水位調節弁の差圧を第１３図
に斜線部で示した。本図と前記第４図または第９
図とを比較すれば、弁の絞り（斜線部）の低減に
効果の有ることが現われている。 As mentioned above, the rotation speed of the condensate pressure booster that controls the rotation speed must be controlled so that the pressure on the upstream side of the deaerator water level control valve is always higher than the sealing water pressure. The invention eliminates that need. An embodiment based on the above-mentioned viewpoint is shown in FIG. The same numbers are given to devices having the same conventional configuration or the above-described invention. In FIG. 11, devices numbered 1 to 38 have the functions already described. An example of a configuration according to the present invention will be described below.
The pressure at the outlet of the condensate boost pump 8 that controls the rotation speed needs to be higher than the pressure required to seal the shaft seal 24 of the water supply pump 20 with water. Therefore, the rotational speed of the condensate pump is set so that the pressure in the pipe line 10 can maintain the pressure necessary for water sealing, but the water sealing control valve 23
A sealing booster pump 3 is connected to the conduit 22 connected via the
By installing 9, the condensate boost pump can be operated at a lower rotation speed. In other words, in order for the sealing booster pump according to the present invention to cover the difference between the pressure required to seal the shaft seal and the system head, the rotational speed of the condensate booster pump is controlled in accordance with the system head. It becomes possible to do. FIG. 12 shows the operating characteristics of the present invention. Condensate pump head curve H C and condensate boost pump head curve H B , N B1 , N B2 , N B3 , N B4 , N B5 ,
Combined head with N B6 and N B7 H T , N T1 , N T2 , N T3 ,
N T4 , N T5 , N T6 , N T7 , sealing pressure P B and system head curve P S are the same as in FIG. 6 above. In the operating range of the condensate boost pump 8 that performs rotation speed control over the power generation amount L a , the system head curve P S is
Since it is greater than the sealing pressure P B , the condensate boost pump will not run out of sealing pressure even if the rotational speed is reduced along the system head. The rotation speed of the condensate boost pump at the power generation amount L a is N Ta . In the power generation amount L b , the difference ΔP S between the seal water pressure P B and the system head curve P S is the condensate water that is increased in pressure by the water seal booster pump according to the present invention and sent to the water supply pump shaft seal. The rotation speed of the boost pump can be reduced to N Tb . According to the present invention, since the condensate boost pump can be operated along the system head, the differential pressure of the deaerator water level control valve is almost eliminated, and valve noise etc. can be prevented and the condensate boost pump It is clear that this method is effective in reducing power consumption. However, when implementing the present invention, the functions shown in FIGS. 7 and 8 are based on the valve differential pressure required for deaerator water level control, approximately 0.5 Kg/cm 2 in the entire power generation range.
It must be kept constant. The differential pressure of the deaerator water level control valve when the present invention is implemented is shown in the shaded area in FIG. This figure and the above figure 4 or 9
A comparison with the figure shows that it is effective in reducing the valve throttle (shaded area).
以上詳述したように、本発明の復水昇圧装置
は、蒸気の発生装置と、復水器を備えた蒸気ター
ビンと、上記気復水器内の復水を加圧して前記蒸
気発生装置に還流させる可変回転速度形の復水加
圧ポンプと、上記復水加圧ポンプの下流に接続さ
れて軸封水部を備えた給水ポンプと、前記復水加
圧ポンプの下流側から分岐されて上記の軸封水部
に連通する封水管路とを設けた汽力発電プラント
において、前記復水加圧ポンプ下流側復水管に接
続された調節弁の流出、入口間の差圧を予め設定
された値に等しからしめるように、前記復水加圧
ポンプの回転速度を制御する手段を設けることに
より、復水昇圧装置の消費動力を低減し得るとい
う優れた実用的効果を奏し、発電プラント全体と
しての熱効率の改善、経済性の向上に貢献すると
ころ多大である。
As described in detail above, the condensate booster of the present invention includes a steam generator, a steam turbine equipped with a condenser, and a steam generator that pressurizes the condensate in the steam condenser and supplies the steam generator with steam. A variable rotational speed type condensate pressurizing pump for refluxing, a water supply pump connected downstream of the condensate pressurizing pump and equipped with a shaft water sealing part, and a water supply pump branched from the downstream side of the condensate pressurizing pump. In a steam power generation plant equipped with a water sealing pipe communicating with the shaft water sealing section, the differential pressure between the outlet and the inlet of the control valve connected to the condensate pipe on the downstream side of the condensate pressurizing pump is set in advance. By providing a means for controlling the rotational speed of the condensate pressure pump so that the value is equal to the value, the power consumption of the condensate pressure pump can be reduced, which is an excellent practical effect, and the power consumption of the entire power plant is reduced. This greatly contributes to improving thermal efficiency and economic efficiency.
第１図は従来技術における復水昇圧系統を示す
系統図、第２図は従来の復水昇圧装置の圧力とプ
ラントの発電量を示す図表、第３図は給水ポンプ
の封水圧力を説明する図表、第４図は従来技術に
おける脱気器水位調節弁の絞りを示す図表、第５
図は本発明の復水昇圧装置の１実施例における系
統図、第６図は上記実施例における復水昇圧装置
の圧力とプラントの発電量とを示す図表、第７図
及び第８図は上記実施例の制御装置の関数を示す
図表、第９図は同じく脱気器水位調節弁の絞りを
示す図表、第１０図及び第１１図はそれぞれ前記
と異なる実施例における系統図、第１２図は上記
実施例における封水昇圧ポンプの昇圧量を説明す
る図表、第１３図は同じく脱気器水位調節弁の絞
りを示す図表である。
１……管路、２……蒸気タービン、３……発電
機、４……復水器、５……復水ポンプ、６……電
動機、７……復水脱塩装置、８……復水昇圧ポン
プ、９……電動機、１０……管路、１１……復水
流量検出器、１２……脱気器水位調節弁、１３…
…低圧給水加熱器、１４……脱気器、１５……脱
気器水位検出器、１６……給水流量検出器、１７
……制御器、１８……連絡管、１９……給水昇圧
ポンプ、２０……給水ポンプ、２１……管路、２
２……封水管、２３……封水調節弁、２４……軸
封部、２５……差圧検出器、２６……差圧信号、
２７……演算器、２８，２９……関数発生器、３
０……演算器、３１……発電量信号、３２……比
例積分演算器、３３……流体継手、３４……負荷
メモリー、３５……発電量信号、３６……演算
器、３７……電力、３８……開閉器、PS……シス
テムヘツド曲線、HC，HB，HT，NT1〜7，NB1〜7…
…揚程曲線、L0，T1，LS，Lo，La，Lb……発電
量、PB……封水圧力、ΔP0，ΔP1，ΔPo，ΔPS…
…差圧、NTa，NTb……復水昇圧ポンプ回転数。
Figure 1 is a system diagram showing a conventional condensate booster system, Figure 2 is a diagram showing the pressure of a conventional condensate booster and the power generation amount of the plant, and Figure 3 explains the sealing pressure of the water pump. Figure 4 is a diagram showing the throttle of the deaerator water level control valve in the prior art, Figure 5
The figure is a system diagram of one embodiment of the condensate booster of the present invention, Figure 6 is a chart showing the pressure of the condensate booster and the power generation amount of the plant in the above embodiment, and Figures 7 and 8 are the above FIG. 9 is a diagram showing the functions of the control device of the embodiment, FIG. 9 is a diagram showing the throttle of the deaerator water level control valve, FIGS. 10 and 11 are system diagrams of the embodiments different from the above, and FIG. FIG. 13 is a chart illustrating the amount of pressure increase of the water seal boost pump in the above embodiment, and is also a chart showing the throttle of the deaerator water level control valve. 1... Pipe line, 2... Steam turbine, 3... Generator, 4... Condenser, 5... Condensate pump, 6... Electric motor, 7... Condensate desalination device, 8... Condensate Water boost pump, 9... Electric motor, 10... Piping, 11... Condensate flow rate detector, 12... Deaerator water level control valve, 13...
... Low pressure feed water heater, 14 ... Deaerator, 15 ... Deaerator water level detector, 16 ... Water supply flow rate detector, 17
... Controller, 18 ... Communication pipe, 19 ... Water supply boost pump, 20 ... Water supply pump, 21 ... Pipe line, 2
2... Water sealing pipe, 23... Water sealing adjustment valve, 24... Shaft sealing section, 25... Differential pressure detector, 26... Differential pressure signal,
27... Arithmetic unit, 28, 29... Function generator, 3
0...Calculator, 31...Power generation signal, 32...Proportional integral calculator, 33...Fluid coupling, 34...Load memory, 35...Power generation signal, 36...Calculator, 37...Electric power , 38... Switch, P S ... System head curve, H C , H B , H T , N T1~7 , N B1~7 ...
...Lift curve, L 0 , T 1 , L S , L o , L a , L b ... Power generation, P B ... Seal water pressure, ΔP 0 , ΔP 1 , ΔP o , ΔP S ...
...Differential pressure, N Ta , N Tb ... Condensate boost pump rotation speed.
Claims (1)
ンと、上記復水器内の復水を加圧して前記蒸気発
生装置に還流させる可変回転速度形の復水加圧ポ
ンプと、上記復水加圧ポンプの下流に接続されて
軸封水部を備えた給水ポンプと、前記復水加圧ポ
ンプの下流側から分岐されて上記軸封水部に連通
する封水管路とを設けた汽力発電プラントにおい
て、前記復水加圧ポンプ下流側復水管に接続され
た調節弁の流出、入口間の差圧を予め設定された
値に等しからしめるように、前記復水加圧ポンプ
の回転速度を制御する手段を設けたことを特徴と
する復水昇圧装置。 ２ 前記の制御手段は、発電量及び発電量に比例
する特性値の少なくとも何れかについて予め定め
た値と、当該発電プラント操業中の発電量実測値
及び発電量に比例する特性値の実測値の少なくと
も何れか一方とを比較して前記復水加圧ポンプの
運転を制御するものであることを特徴とする特許
請求の範囲第１項に記載の復水昇圧装置。 ３ 前記の封水管路は、その途中に封水を加圧す
る手段を設けたものであることを特徴とする特許
請求の範囲第１項に記載の復水昇圧装置。[Scope of Claims] 1. A steam generator, a steam turbine equipped with a condenser, and a variable rotation speed type condensate pressurizer that pressurizes condensate in the condenser and returns it to the steam generator. a pump, a water supply pump connected downstream of the condensate pressure pump and provided with a shaft water sealing section, and a water sealing pipe branched from the downstream side of the condensate pressure pump and communicating with the shaft water sealing section. In a steam power generation plant equipped with a condensate pressure pump, the condensate pressure pump is controlled such that the differential pressure between the outlet and inlet of the control valve connected to the condensate pipe on the downstream side of the condensate pressurizing pump is equalized to a preset value. A condensate pressure boosting device characterized by being provided with means for controlling the rotational speed of a pressure pump. 2. The control means is configured to control a predetermined value for at least one of the amount of power generation and a characteristic value proportional to the amount of power generation, and the actual value of the amount of power generated during operation of the power plant and the actual value of the characteristic value proportional to the amount of power generation. 2. The condensate pressurizing device according to claim 1, wherein the condensate pressurizing pump is controlled by comparing at least one of the two condensate pressurizing pumps. 3. The condensate pressure boosting device according to claim 1, wherein the water sealing pipe is provided with means for pressurizing the water sealing water in the middle thereof.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20099183A JPS6093206A (en) | 1983-10-28 | 1983-10-28 | Condensate booster |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20099183A JPS6093206A (en) | 1983-10-28 | 1983-10-28 | Condensate booster |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6093206A JPS6093206A (en) | 1985-05-25 |
| JPH0454122B2 true JPH0454122B2 (en) | 1992-08-28 |
Family
ID=16433685
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20099183A Granted JPS6093206A (en) | 1983-10-28 | 1983-10-28 | Condensate booster |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6093206A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5424711B2 (en) * | 2009-05-20 | 2014-02-26 | 株式会社東芝 | Steam turbine power generation system |
-
1983
- 1983-10-28 JP JP20099183A patent/JPS6093206A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6093206A (en) | 1985-05-25 |
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