JPH0231202B2 - - Google Patents
Info
- Publication number
- JPH0231202B2 JPH0231202B2 JP59043703A JP4370384A JPH0231202B2 JP H0231202 B2 JPH0231202 B2 JP H0231202B2 JP 59043703 A JP59043703 A JP 59043703A JP 4370384 A JP4370384 A JP 4370384A JP H0231202 B2 JPH0231202 B2 JP H0231202B2
- Authority
- JP
- Japan
- Prior art keywords
- hot water
- steam
- accumulator
- control valve
- amount
- 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
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 161
- 239000012530 fluid Substances 0.000 claims description 33
- 238000010248 power generation Methods 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 9
- 229920006395 saturated elastomer Polymers 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 239000002918 waste heat Substances 0.000 description 7
- 230000007423 decrease Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 210000000689 upper leg Anatomy 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K21/00—Steam engine plants not otherwise provided for
- F01K21/005—Steam engine plants not otherwise provided for using mixtures of liquid and steam or evaporation of a liquid by expansion
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
【発明の詳細な説明】
本発明は熱水発電プラント、特に蒸気熱水二相
流体輸送式の熱水発電プラントに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydrothermal power plant, particularly a steam-hot-water two-phase fluid transport type hydrothermal power plant.
第１図は従来の熱水発電プラントを示す図であ
る。図中１１は給水ポンプであり、その出口には
熱水発生器１２が接続されている。熱水発生器１
２の出口は温度調整弁１３を介してアキユムレー
タ１４の入口に接続されている。上記温度調整弁
１３は熱水発生器１２により排出される流体の排
熱量に応じて開度を制御するもので、前記熱水発
生器１２の出口側における液体の温度は温度検出
器１５で検出されている。前記アキユムレータ１
４の出口は熱水管１６により熱水タービン１７に
接続され、上記熱水管１６には熱水止め弁１８お
よび熱水加減弁１９が介挿されている。上記熱水
加減弁１９は前記アキユムレータ１４内の熱水レ
ベルが予じめ定められた設定値となるように制御
するもので、アキユムレータ１４内の熱水レベル
は液位検出器２０で検出されている。 FIG. 1 is a diagram showing a conventional hydrothermal power generation plant. In the figure, 11 is a water supply pump, and a hot water generator 12 is connected to its outlet. Hot water generator 1
The outlet of No. 2 is connected to the inlet of an accumulator 14 via a temperature control valve 13. The temperature control valve 13 controls the opening degree according to the amount of waste heat of the fluid discharged by the hot water generator 12, and the temperature of the liquid at the outlet side of the hot water generator 12 is detected by the temperature detector 15. has been done. Said accumulator 1
4 is connected to a hot water turbine 17 by a hot water pipe 16, and a hot water stop valve 18 and a hot water control valve 19 are inserted into the hot water pipe 16. The hot water control valve 19 controls the hot water level in the accumulator 14 to a predetermined set value, and the hot water level in the accumulator 14 is detected by the liquid level detector 20. There is.
前記熱水タービン１７から送出される液体は気
水分離器２１にて蒸気と熱水とに分離され、蒸気
はフラツシユ蒸気タービン入口蒸気止め弁２２お
よびインタセフト弁２３を介してフラツシユ蒸気
タービン２４へ送られ、熱水は多段フラツシヤ２
５へ送られる。多段フラツシヤ２５に供給された
熱水はフラツシヤ２５内の弁を通過するときに圧
力降下して一部が気化し、前記フラツシユ蒸気タ
ービン２４へ送られる。フラツシユ蒸気タービン
２４は前記熱水タービン１７と共に発電機２６を
駆動し、フラツシユ蒸気タービン２４を通過した
低温の蒸気は復水器２７へ送出される。上記復水
器２７にて冷却液化された水は復水ポンプ２８を
介して前記給水ポンプ１１に供給される。一方、
前記多段フラツシユ２５内の水はフラツシヤドレ
ンブースタポンプ２９および水位調節弁３０を介
して前記給水ポンプ１１に供給される。上記水位
調節弁３０は前記多段フラツシヤ２５内の水位を
制御するもので、多段フラツシヤ２５内の水位は
液位検出器３１で検出されている。 The liquid sent out from the hot water turbine 17 is separated into steam and hot water in a steam separator 21, and the steam is sent to the flash steam turbine 24 via the flash steam turbine inlet steam stop valve 22 and intertheft valve 23. The hot water is transferred to the multi-stage flusher 2.
Sent to 5. When the hot water supplied to the multi-stage flasher 25 passes through a valve in the flasher 25, the pressure drops and a portion of the hot water is vaporized and sent to the flash steam turbine 24. The flash steam turbine 24 drives a generator 26 together with the hot water turbine 17 , and the low-temperature steam that has passed through the flash steam turbine 24 is sent to a condenser 27 . The water cooled and liquefied in the condenser 27 is supplied to the water supply pump 11 via the condensate pump 28. on the other hand,
Water in the multi-stage flush 25 is supplied to the water supply pump 11 via a flush drain booster pump 29 and a water level control valve 30. The water level control valve 30 controls the water level within the multi-stage flasher 25, and the water level within the multi-stage flasher 25 is detected by a liquid level detector 31.
一般に熱水発電プラントは排熱の温度が中、低
温の場合において、上記排熱を経済的に回収する
のに適している。また上記排熱の温度が高温の場
合には、熱水条件を高めることにより理論的には
効率がよくなる。 In general, hydrothermal power plants are suitable for economically recovering waste heat when the temperature of the waste heat is medium to low. Furthermore, when the temperature of the exhaust heat is high, efficiency can theoretically be improved by increasing the hot water conditions.
しかし、上記熱水条件をむやみに高めると、材
料費が高くつき、また段階効率や翼車の耐エロジ
ヨン性を考慮した熱水タービンの設計が難しくな
る。 However, unnecessarily increasing the above-mentioned hot water conditions increases material costs and makes it difficult to design a hot water turbine that takes stage efficiency and impeller erosion resistance into consideration.
そこでこれらの欠点を補う手段として蒸気熱水
二相流体輸送式の発電プランが先に提案されてい
る（特願昭52−148116号）。これは、排熱の温度
が高い場合に、熱水の圧力は上げず、熱水の一部
を蒸気させて熱水と蒸気との二相流体とすること
により、さらに高位のエネルギーとして回収する
もものである。 Therefore, as a means of compensating for these drawbacks, a steam-hot-water two-phase fluid transport type power generation plan was previously proposed (Japanese Patent Application No. 148,116/1982). When the temperature of the exhaust heat is high, the pressure of the hot water is not increased, and some of the hot water is steamed to form a two-phase fluid of hot water and steam, which is recovered as higher energy. It's a thigh.
しかるにこの種の発電プラントには次のような
問題があつた。すなわち、流体が飽和二相流体で
あるため温度は一定である。したがつて第１図に
示すような従来の熱水発電プラントのように、ア
キユムレータ１４の入口側に温度調節弁１３を設
け、排熱量に応じて流量を制御するものには使用
できない。 However, this type of power plant had the following problems. That is, since the fluid is a saturated two-phase fluid, the temperature is constant. Therefore, it cannot be used in a conventional hydrothermal power generation plant as shown in FIG. 1, in which the temperature control valve 13 is provided on the inlet side of the accumulator 14 and the flow rate is controlled according to the amount of exhaust heat.
本発明の目的は、蒸気熱水二相流体輸送式の発
電方式を利用した熱水発電プラントに対し、より
広範囲な排熱量の安定した制御を行なえる熱水発
電プラントを提供することになる。 An object of the present invention is to provide a hydrothermal power plant that can stably control the amount of exhaust heat over a wider range, compared to a hydrothermal power plant that uses a steam-hot-water two-phase fluid transport type power generation system.
上記の目的を達成するために、本発明の熱水発
電プラントは、給水ポンプと、給水ポンプから送
出される液体が供給され、熱水または熱水と蒸気
からなる二相流体を発生する熱水・蒸気発生器
と、熱水・蒸気発生器から発生される二相流体を
加圧状態で蓄えるアキユムレータと、アキユムレ
ータに蓄えられた二相流体のうち、蒸気が蒸気入
口から供給されかつ熱水が熱水入口から供給され
る熱水タービンと、給水ポンプの出口側に設けら
れ、熱水・蒸気発生器から発生される二相流体の
温度が設定値以上となるように熱水・蒸気発生器
への液体供給量を制御する給水制御弁と、アキユ
ムレータの蒸気出口側に設けられ、当該アキユム
レータ内の圧力が設定値となるように熱水タービ
ンへの蒸気流出量を制御する蒸気加減弁と、アキ
ユムレータの熱水出口側に設けられ、当該アキユ
ムレータ内の熱水レベルが設定値となるように熱
水タービンへの熱水流出量を制御する熱水加減弁
とを具備して構成している。 In order to achieve the above object, the hot water power generation plant of the present invention includes a water supply pump and a hot water supply system that is supplied with a liquid sent from the water supply pump and generates hot water or a two-phase fluid consisting of hot water and steam.・Steam generator, hot water, and an accumulator that stores the two-phase fluid generated from the steam generator in a pressurized state; The hot water turbine is supplied from the hot water inlet, and the hot water/steam generator is installed at the outlet side of the water supply pump so that the temperature of the two-phase fluid generated from the hot water/steam generator is higher than the set value. a water supply control valve that controls the amount of liquid supplied to the hot water turbine; a steam control valve that is provided on the steam outlet side of the accumulator and controls the amount of steam flowing out to the hot water turbine so that the pressure in the accumulator becomes a set value; The hot water regulating valve is provided on the hot water outlet side of the accumulator and controls the amount of hot water flowing into the hot water turbine so that the hot water level in the accumulator becomes a set value.
従つて、本発明の熱水発電プラントにおいて
は、給水制御弁により、熱水・蒸気発生器から発
生される二相流体の温度が設定値以上となるよう
に制御され、また蒸気加減弁により、アキユムレ
ータ内の圧力が設定値となるように制御されると
共に、熱水加減弁により、アキユムレータ内の熱
水レベルが設定値となるように制御されることに
より、排熱量に応じた量の流体を熱水タービンに
導入することができる。これにより、広範囲な排
熱量の制御を安定に行なうことが可能となる。 Therefore, in the hot water power generation plant of the present invention, the water supply control valve controls the temperature of the two-phase fluid generated from the hot water/steam generator to be equal to or higher than a set value, and the steam control valve The pressure in the accumulator is controlled to be the set value, and the hot water level in the accumulator is controlled by the hot water control valve to be the set value, so that the amount of fluid corresponding to the amount of exhaust heat is controlled. Can be introduced into hot water turbines. This makes it possible to stably control the amount of exhaust heat over a wide range.
第２図は本発明の一実施例を示す熱水発電プラ
ントの系統図である。なお第１図と同一部分には
同一符号を付し説明は省略する。給水ポンプ１１
の出口には給水制御弁４１を介して熱水・蒸気発
生器４２が接続され、熱水・蒸気発生器４２の出
口側における流体の温度は温度検出器１５にて検
出されている。上記給水制御弁４１は熱水・蒸気
発生器４２の出口における流体の温度が予め定め
られた設定値Ａ以上となるように制御するもので
ある。すなわち第３図に示すように熱水・蒸気発
生器４２の出口側における流体の温度が設定値Ａ
未満のときは上記給水制御弁４１は閉方向に動
き、流体の温度が設定値Ａ以上のときは全開状態
となる。 FIG. 2 is a system diagram of a hydrothermal power generation plant showing an embodiment of the present invention. Note that the same parts as in FIG. 1 are given the same reference numerals, and explanations thereof will be omitted. Water supply pump 11
A hot water/steam generator 42 is connected to the outlet of the hot water/steam generator 42 via a water supply control valve 41, and the temperature of the fluid at the outlet side of the hot water/steam generator 42 is detected by a temperature detector 15. The water supply control valve 41 controls the temperature of the fluid at the outlet of the hot water/steam generator 42 to be equal to or higher than a predetermined set value A. That is, as shown in FIG. 3, the temperature of the fluid at the outlet side of the hot water/steam generator 42 is at the set value A.
When the temperature is less than the set value A, the water supply control valve 41 moves in the closing direction, and when the temperature of the fluid is equal to or higher than the set value A, the water supply control valve 41 is fully opened.
前記熱水・蒸気発生器４２の出口は二相流体輸
送管４３を介してアキユムレータ４４の入口に接
続されている。上記アキユムレータ４４は上部に
蒸気出口４４ａ、下部に熱水出口４４ｂを有する
ものである。また図中４５は熱水タービンで、こ
の熱水タービン４５には蒸気入口４５ａおよび熱
水入口４５ｂが設けられている。そしてアキユム
レータ４４の蒸気出口４４ａと熱水タービン４５
の蒸気入口４５ａとの間は主蒸気管４６で接続さ
れ、この主蒸気管４６には主蒸気止め弁４７およ
び蒸気加減弁４８が介挿されている。また前記ア
キユムレータ４４の熱水出口４４ｂと熱水タービ
ン４５の熱水入口４５ｂとの間は熱水管１６で接
続され、この熱水管１６には熱水止め弁１８およ
び熱水加減弁１９が介挿されている。またアキユ
ムレータ４４の蒸気出口４４ａ側圧力は圧力検出
器４９で検出され、アキユムレータ４４内の熱水
レベルは液位検出器２０で検出されている。 The outlet of the hot water/steam generator 42 is connected to the inlet of an accumulator 44 via a two-phase fluid transport pipe 43. The accumulator 44 has a steam outlet 44a at the top and a hot water outlet 44b at the bottom. Further, in the figure, 45 is a hot water turbine, and this hot water turbine 45 is provided with a steam inlet 45a and a hot water inlet 45b. The steam outlet 44a of the accumulator 44 and the hot water turbine 45
A main steam pipe 46 is connected to the steam inlet 45a, and a main steam stop valve 47 and a steam control valve 48 are inserted into the main steam pipe 46. A hot water pipe 16 is connected between the hot water outlet 44b of the accumulator 44 and the hot water inlet 45b of the hot water turbine 45, and a hot water stop valve 18 and a hot water control valve 19 are inserted in the hot water pipe 16. has been done. Further, the pressure on the steam outlet 44a side of the accumulator 44 is detected by a pressure detector 49, and the hot water level in the accumulator 44 is detected by a liquid level detector 20.
前記蒸気加減弁４８は前記アキユムレータ４５
内の圧力が予め定められた設定値Ｂとなるように
制御するものである。すなわち、第４図に示すよ
うに、アキユムレータ４４内の圧力が上がれば蒸
気加減弁４８は開方向へ動き、アキユムレータ４
４内の圧力が下がれば閉方向へ動く。 The steam control valve 48 is connected to the accumulator 45.
The internal pressure is controlled to a predetermined set value B. That is, as shown in FIG. 4, when the pressure inside the accumulator 44 increases, the steam control valve 48 moves in the opening direction, and the accumulator 4
When the pressure inside 4 decreases, it moves in the closing direction.
また前記熱水加減弁１９は前記アキユムレータ
４４内の熱水レベルを予め定められた設定値Ｃと
なるように制御するものである。すなわち、第５
図に示すようにアキユムレータ４４内の熱水レベ
ルが上がれば熱水加減弁１９は開方向へ動き、ア
キユムレータ４４内の熱水レベルが下がれば閉方
向へ動く。 The hot water adjustment valve 19 controls the hot water level in the accumulator 44 to a predetermined set value C. That is, the fifth
As shown in the figure, when the hot water level in the accumulator 44 rises, the hot water regulating valve 19 moves in the opening direction, and when the hot water level in the accumulator 44 falls, it moves in the closing direction.
熱水タービン４５以降の系統は第１図の従来の
プラトンと同様である。 The system after the hot water turbine 45 is the same as the conventional Plato shown in FIG.
このように構成された本装置において、アキユ
ムレータ４４内の圧力設定値Ｂを41〔Kg／cm2abs〕
と設定した場合については例示する。上記設定値
Ｂに対する飽和温度は250.6℃である。また熱
水・蒸気発生器４２の出口における流体の温度設
定値Ａは上記飽和温度よりも僅かに低目、たとえ
ば248℃と設定する。 In this device configured in this way, the pressure setting value B in the accumulator 44 is set to 41 [Kg/cm 2 abs].
An example is shown below. The saturation temperature for the above set value B is 250.6°C. Further, the temperature setting value A of the fluid at the outlet of the hot water/steam generator 42 is set to be slightly lower than the saturation temperature, for example, 248°C.
今、排熱量が少なくて流体の温度が248℃より
も低い場合は、給水制御弁４１が閉方向へ動き給
水量が減少する。そうすると流体は248℃より少
し低い温度まで加熱される。そこで蒸気加減弁４
８および熱水加減弁１９の調整を行なう。つまり
上記状態においては、蒸気加減弁４８は全閉さ
れ、アキユムレータ４４内の圧力は流体の飽和圧
力すなわち流体温度の設定値248℃の飽和圧力
39.2〔Kg／cm2abs〕以下に保たれる。そして熱水・
蒸気発生器４２にて発生した熱水量に応じて熱水
加減弁１９が開閉し、熱水を熱水タービン４５に
導入する。これは従来の熱水発電プラントと基本
的には同様である。 Now, if the amount of exhaust heat is small and the temperature of the fluid is lower than 248° C., the water supply control valve 41 moves in the closing direction and the amount of water supply decreases. The fluid is then heated to a temperature slightly below 248°C. Therefore, steam control valve 4
8 and the hot water control valve 19 are adjusted. In other words, in the above state, the steam control valve 48 is fully closed, and the pressure inside the accumulator 44 is the saturation pressure of the fluid, that is, the saturation pressure of the fluid temperature set value of 248°C.
Maintained below 39.2 [Kg/cm 2 abs]. And hot water
The hot water control valve 19 opens and closes according to the amount of hot water generated by the steam generator 42, and hot water is introduced into the hot water turbine 45. This is basically the same as a conventional hydrothermal power plant.
次に流体温度が設定値である248℃に達すると、
給水制御弁４１は全開となり、最大給水量が流れ
る。 Next, when the fluid temperature reaches the set value of 248℃,
The water supply control valve 41 is fully opened and the maximum amount of water flows.
さらに流体温度が上昇し排熱量が多くなると、
熱水・蒸気発生器４２から蒸気が発生し始める。
この蒸気の発生量は前記排熱量にしたがつて増大
し、仮にこのままでいくとすると、結局は給水量
全体が蒸発する状態となる。この状態は飽和蒸気
プラントの場合と同様であるが、このときの排熱
量は以下のように設計点をはかるに越えているの
で、給水量全体が蒸発する状態に陥る可能性はな
い。 Furthermore, as the fluid temperature rises and the amount of waste heat increases,
Steam begins to be generated from the hot water/steam generator 42.
The amount of steam generated increases in accordance with the amount of exhaust heat, and if this continues as it is, the entire amount of water supplied will eventually evaporate. This condition is similar to that of a saturated steam plant, but since the amount of waste heat at this time far exceeds the design point as shown below, there is no possibility that the entire amount of water supply will evaporate.
すなわち第６図は排熱量Ｈ〔Kcal／Ｈ〕と熱水
発生量Gw〔Kg／Ｈ〕および蒸気発生量Gs〔Kg／Ｈ〕
との関係を示す図である。上記排熱量Ｈと熱水発
生量Gw、蒸気発生量Gsの関係は
Ｈ＝Gs（h2−h0）Gw（h1−h0）
Ｇ＝Gs＋Gw
Ｇ：給水量〔Kg／Ｈ〕
h0：給水エンタルピ〔Kcal／Kg〕
h1：飽和熱水エンタルピ〔Kacl／Kg〕
h2：乾き飽和蒸気エンタルピ〔Kcal／Kg〕
となる。ここで飽和圧力39.2〔Kg／cm2aba〕、流体
温度は250.6℃の乾き飽和蒸気エンタルピh2は
668.9〔Kcal／Kg〕、で飽和圧力４２〔Kg／cm2
abs〕、給水温度80℃の給水エンタルピh0は80.8
〔Kcal／Kg〕である。 In other words, Figure 6 shows the amount of waste heat H [Kcal/H], the amount of hot water generated G w [Kg/H], and the amount of steam generated G s [Kg/H]
FIG. The relationship between the above exhaust heat amount H, hot water generation amount G w , and steam generation amount G s is H = G s (h2 − h0) G w (h1 − h0) G = G s + G w G: Water supply amount [Kg/H ] h0: Water supply enthalpy [Kcal/Kg] h1: Saturated hot water enthalpy [Kacl/Kg] h2: Dry saturated steam enthalpy [Kcal/Kg]. Here, the saturation pressure is 39.2 [Kg/cm 2 aba], the fluid temperature is 250.6°C, and the dry saturated steam enthalpy h2 is
668.9 [Kcal/Kg], saturation pressure 42 [Kg/cm 2
abs], the feed water enthalpy h0 at a feed water temperature of 80℃ is 80.8
[Kcal/Kg].
今、最大給水量を100〔Ｔ／Ｈ〕、給水温度を80
℃とすると、排熱量Ｈが０〔Kcal／Ｈ〕では熱水
発生量Gwは０〔Ｔ／Ｈ〕となる。また排熱量Ｈが
1.76×107〔Kcal／Ｈ〕（第６図中Ｄ）においては、
流体温度248℃の熱水発生量Gwは100〔Ｔ／Ｈ〕、
すなわち、
100×103〔Kg／Ｈ〕×（257.0−80.0）
〔Kcal／Kg〕＝1.76×107〔Kcal／Ｈ〕
となり、排熱量Ｈが5.88×107〔Kcal／Ｈ〕（第６
図中Ｅ）においては、飽和圧力４１〔Kg／cm2
abs〕の飽和蒸気発生量Gwは100〔Ｔ／Ｈ〕、すな
わち、
100×103〔Kg／Ｈ〕×（668.9×80.9）
〔Kcal／Kg〕＝5.88×107〔kcal／Ｈ〕
となり、排熱量Ｈが1.76×107〔Kcal／Ｈ〕と5.88
×107〔Kcal／Ｈ〕との間（第６図中Ｄ−Ｅ）で
は250.6℃の飽和熱水と41〔Kg／cm2abs〕の飽和蒸
気が合わせて100〔Ｔ／Ｈ〕発生することになる。 Now, the maximum water supply amount is 100 [T/H] and the water supply temperature is 80.
℃, when the amount of waste heat H is 0 [Kcal/H], the amount of generated hot water G w is 0 [T/H]. Also, the amount of exhaust heat H is
At 1.76×10 7 [Kcal/H] (D in Figure 6),
The amount of hot water generated Gw at a fluid temperature of 248℃ is 100 [T/H],
In other words, 100×10 3 [Kg/H]×(257.0−80.0) [Kcal/Kg]=1.76×10 7 [Kcal/H], and the amount of exhaust heat H is 5.88×10 7 [Kcal/H] (6th
At E) in the figure, the saturation pressure is 41 [Kg/cm 2
The saturated steam generation amount G w of [abs] is 100 [T/H], that is, 100 × 10 3 [Kg/H] × (668.9 × 80.9) [Kcal/Kg] = 5.88 × 10 7 [kcal/H]. , the amount of exhaust heat H is 1.76×10 7 [Kcal/H] and 5.88
×10 7 [Kcal/H] (D-E in Figure 6), a total of 100 [T/H] of saturated hot water of 250.6℃ and saturated steam of 41 [Kg/cm 2 abs] are generated. It turns out.
ここで、通常は蒸気発生量Gsを15％程度に設
定する。すなわち、第６図においては2.4×107
〔Kcal／Ｈ〕（第６図中Ｆ）付近となる。したが
つて給水量全体が蒸発する状態になることはない
のである。 Here, the steam generation amount Gs is usually set to about 15%. That is, in Figure 6, 2.4×10 7
It will be around [Kcal/H] (F in Figure 6). Therefore, the entire water supply does not evaporate.
このように本実施例によれば、排熱量の変化に
応じて発生する蒸気と熱水の量が変化し、この変
化はアキユムレータ４４内の圧力と熱水レベルの
変化に反映される。したがつて蒸気加減弁４８と
熱水加減弁１９によりアキユムレータ４４内の圧
力と熱水レベルとを制御することによつて、蒸気
と熱水の流量を排熱量に応じて制御し、熱水ター
ビンに導入することができる。 As described above, according to this embodiment, the amount of steam and hot water generated changes in accordance with the change in the amount of exhaust heat, and this change is reflected in the change in the pressure and hot water level within the accumulator 44. Therefore, by controlling the pressure and hot water level in the accumulator 44 using the steam control valve 48 and the hot water control valve 19, the flow rates of steam and hot water are controlled according to the amount of exhaust heat, and the hot water turbine can be introduced into
以上説明したように本発明によれば、給水制御
弁により、熱水・蒸気発生器から発生される二相
流体の温度が設定値以上となるように制御し、ま
た蒸気加減弁により、アキユムレータ内の圧力が
設定値となるように制御すると共に、熱水加減弁
により、アキユムレータ内の熱水レベルが設定値
となるように制御するようにしたので、排熱量に
応じた量の流体を熱水タービンに導入することが
でき、もつて広範囲な排熱量の制御を安定に行な
うことが可能な熱水発電プラントが提供できる。 As explained above, according to the present invention, the water supply control valve controls the temperature of the two-phase fluid generated from the hot water/steam generator to be equal to or higher than the set value, and the steam control valve controls the temperature of the two-phase fluid inside the accumulator. The pressure in the accumulator is controlled to be the set value, and the hot water level in the accumulator is controlled to be the set value using the hot water control valve. It is possible to provide a hydrothermal power generation plant that can be introduced into a turbine and can stably control the amount of exhaust heat over a wide range.
第１図は従来の熱水発電プラント系統図、第２
図は本発明の一実施例における熱水発電プラント
の系統図、第３図〜第６図は同実施例の作用を示
すもので、第３図は給水制御弁の開度と流体温度
との関係を示す図、第４図は蒸気加減弁の開度と
アキユムレータ内圧力との関係を示す図、第５図
は熱水加減弁の開度とアキユムレータ内熱水レベ
ルとの関係を示す図、第６図は排熱量と熱水およ
び蒸気の発生量との関係を示す図である。
１１……給水ポンプ、１６……熱水管、１９…
…熱水制御弁、４１……給水制御弁、４２……熱
水・蒸気発生器、４４……アキユムレータ、４５
……熱水タービン、４６……主蒸気管、４８……
蒸気制御弁。
Figure 1 is a conventional hydrothermal power generation plant system diagram;
The figure is a system diagram of a hot water power generation plant according to an embodiment of the present invention. Figures 3 to 6 show the operation of the same embodiment. Figure 3 shows the relationship between the opening degree of the water supply control valve and the fluid temperature. Figure 4 is a diagram showing the relationship between the opening degree of the steam control valve and the pressure inside the accumulator, and Figure 5 is a diagram showing the relationship between the opening degree of the hot water control valve and the hot water level in the accumulator. FIG. 6 is a diagram showing the relationship between the amount of exhaust heat and the amount of hot water and steam generated. 11...Water pump, 16...Hot water pipe, 19...
... Hot water control valve, 41 ... Water supply control valve, 42 ... Hot water/steam generator, 44 ... Accumulator, 45
...Hot water turbine, 46...Main steam pipe, 48...
Steam control valve.
Claims (1)
れ、熱水または熱水と蒸気からなる二相流体を発
生する熱水・蒸気発生器と、 前記熱水・蒸気発生器から発生される二相流体
を加圧状態で蓄えるアキユムレータと、 前記アキユムレータに蓄えられた二相流体のう
ち、蒸気が蒸気入口から供給されかつ熱水が熱水
入口から供給される熱水タービンと、 前記給水ポンプの出口側に設けられ、前記熱
水・蒸気発生器から発生される二相流体の温度が
設定値以上となるように前記熱水・蒸気発生器へ
の液体供給量を制御する給水制御弁と、 前記アキユムレータの蒸気出口側に設けられ、
当該アキユムレータ内の圧力が設定値となるよう
に前記熱水タービンへの蒸気流出量を制御する蒸
気加減弁と、 前記アキユムレータの熱水出口側に設けられ、
当該アキユムレータ内の熱水レベルが設定値とな
るように前記熱水タービンへの熱水流出量を制御
する熱水加減弁と、 を具備して成ることを特徴とする熱水発電プラン
ト。[Scope of Claims] 1. A water supply pump; A hot water/steam generator that is supplied with the liquid sent from the water supply pump and generates hot water or a two-phase fluid consisting of hot water and steam; an accumulator that stores two-phase fluid generated from a steam generator in a pressurized state; and of the two-phase fluid stored in the accumulator, steam is supplied from the steam inlet and hot water is supplied from the hot water inlet. a water turbine, and an amount of liquid supplied to the hot water/steam generator such that the temperature of the two-phase fluid generated from the hot water/steam generator is a set value or higher, and is provided on the outlet side of the water supply pump. a water supply control valve for controlling the water supply, and a water supply control valve provided on the steam outlet side of the accumulator;
a steam control valve that controls the amount of steam flowing out to the hot water turbine so that the pressure in the accumulator reaches a set value; and a steam control valve provided on the hot water outlet side of the accumulator,
A hot water power generation plant comprising: a hot water adjustment valve that controls the amount of hot water flowing into the hot water turbine so that the hot water level in the accumulator becomes a set value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4370384A JPS60187704A (en) | 1984-03-07 | 1984-03-07 | Hot water power generation plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4370384A JPS60187704A (en) | 1984-03-07 | 1984-03-07 | Hot water power generation plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60187704A JPS60187704A (en) | 1985-09-25 |
| JPH0231202B2 true JPH0231202B2 (en) | 1990-07-12 |
Family
ID=12671173
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4370384A Granted JPS60187704A (en) | 1984-03-07 | 1984-03-07 | Hot water power generation plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60187704A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103899370B (en) * | 2014-04-29 | 2015-12-09 | 苟仲武 | A kind of Novel steam power circulating device and method of work |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS562414A (en) * | 1979-06-21 | 1981-01-12 | Mitsubishi Heavy Ind Ltd | Variable pressure driving system for hot water turbine |
| JPS5732003A (en) * | 1980-08-04 | 1982-02-20 | Mitsubishi Heavy Ind Ltd | Motive power plant |
-
1984
- 1984-03-07 JP JP4370384A patent/JPS60187704A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS562414A (en) * | 1979-06-21 | 1981-01-12 | Mitsubishi Heavy Ind Ltd | Variable pressure driving system for hot water turbine |
| JPS5732003A (en) * | 1980-08-04 | 1982-02-20 | Mitsubishi Heavy Ind Ltd | Motive power plant |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60187704A (en) | 1985-09-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4693086A (en) | Steam turbine plant having a turbine bypass system | |
| EP0093724A4 (en) | Sliding pressure flash tank. | |
| US5836162A (en) | Feedwater heater drain recycle system | |
| JP4393593B2 (en) | Heating method and apparatus for valve device | |
| JPH0231202B2 (en) | ||
| JPH09112801A (en) | Pressured fluidized bed boiler generating system | |
| JP2737884B2 (en) | Steam turbine generator | |
| JPS6125887B2 (en) | ||
| JPS5814909A (en) | Degassing apparatus | |
| JPH0842802A (en) | Device for controlling generating quantity of intermediate/low pressure steam in exhaust gas boiler | |
| JP2531801B2 (en) | Exhaust heat recovery heat exchanger controller | |
| JP3010086B2 (en) | Cogeneration power plant | |
| JPH01308A (en) | How to operate a combined cycle power plant | |
| JPS5572615A (en) | Power generating plant | |
| JPS6239661B2 (en) | ||
| JPS60206912A (en) | Flush preventive method for condensate in rankin cycle system | |
| JPH10197687A (en) | Complex reactor power generation equipment | |
| JPH0223929Y2 (en) | ||
| JPH0423161B2 (en) | ||
| JP2523493B2 (en) | Turbin bypass system | |
| JPS6155603B2 (en) | ||
| JPS624602B2 (en) | ||
| JP3276247B2 (en) | Boiler / turbine condensate and water supply equipment | |
| JPS5489145A (en) | Steam turbine device combined with water manufacuring plant | |
| JP2002129911A (en) | Auxiliary steam attemperator and its operating method |