JPH0146687B2 - - Google Patents
Info
- Publication number
- JPH0146687B2 JPH0146687B2 JP16913683A JP16913683A JPH0146687B2 JP H0146687 B2 JPH0146687 B2 JP H0146687B2 JP 16913683 A JP16913683 A JP 16913683A JP 16913683 A JP16913683 A JP 16913683A JP H0146687 B2 JPH0146687 B2 JP H0146687B2
- Authority
- JP
- Japan
- Prior art keywords
- medium
- condenser
- lng
- pressure
- liquid
- 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
- 239000007788 liquid Substances 0.000 claims description 21
- 238000010248 power generation Methods 0.000 claims description 8
- 238000000034 method Methods 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 6
- 230000005494 condensation Effects 0.000 description 3
- 238000009833 condensation Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000013535 sea water Substances 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- 230000001052 transient effect Effects 0.000 description 2
- 101100343586 Arabidopsis thaliana LNG2 gene Proteins 0.000 description 1
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 239000001294 propane Substances 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
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】
〔発明の利用分野〕
本発明はランキンサイクル方式のLNGの冷熱
発電設備に係り、ランキン媒体を待機時の常温か
ら運転時の低温まで冷却する場合の媒体循環ポン
プのキヤビテーシヨンを防止するに好適なLNG
冷熱発電設備の制御方法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 Rankine cycle type LNG cold-thermal power generation facility, and relates to cavitation of a medium circulation pump when cooling Rankine medium from room temperature during standby to low temperature during operation. LNG suitable for preventing
The present invention relates to a method of controlling cold power generation equipment.
従来のランキンサイクル方式のLNG冷熱発電
設備では、ランキン媒体としてフロン13B1、フ
ロン22、プロパン等の液化ガスを使用している。
これらの液化ガスは媒体凝縮器でLNGと熱交換
し、LNGを気化してみずからは凝縮する。凝縮
液は媒体循環ポンプで昇圧され、媒体蒸発器で気
化されてタービンを回転させ、再び媒体凝縮器に
リサイクルされている。ランキンサイクル系のタ
ービン排気側は、タービンでの動力回収を有効に
するためより低圧運転、たとえば大気圧近くの状
態で運転されるのが通常である。
Conventional Rankine cycle LNG cryogenic power generation equipment uses liquefied gases such as Freon 13B1, Freon 22, and propane as Rankine media.
These liquefied gases exchange heat with LNG in a medium condenser, vaporize the LNG, and condense themselves. The condensate is pressurized by a medium circulation pump, vaporized by a medium evaporator to rotate a turbine, and then recycled to a medium condenser. The turbine exhaust side of a Rankine cycle system is normally operated at a lower pressure, for example near atmospheric pressure, in order to effectively recover power in the turbine.
ランキン媒体の液化ガスは、通常運転前の待機
状態では常温（20℃）の飽和圧力を示しており、
約７〜13Kg／cm2Ｇ程度となつている。スタートア
ツプ時には、この期待状態から通常運転状態の０
〜１Kg／cm2Ｇまで減圧し、低温状態にすることに
なる。低圧運転は媒体凝縮器のLNG流量を定格
負荷の1/4〜1/2とし、タービンバイパス弁を徐閉
しながら冷却していく。減圧冷却運転の過渡状態
においては、媒体凝縮器内圧力が低くなつている
のに媒体循環ポンプに吸入される媒体の温度は媒
体凝縮器の滞留部分の時間遅れがあり、媒体凝縮
器内圧力の飽和温度より高くなる。したがつて、
ポンプの有効NPSHは小さくなる。 Liquefied gas as a Rankine medium exhibits a saturation pressure at room temperature (20°C) in the standby state before normal operation.
It is approximately 7 to 13 kg/cm 2 G. At startup, this expected state is changed to the normal operating state of 0.
The pressure will be reduced to ~1Kg/cm 2 G and the temperature will be reduced. In low-pressure operation, the LNG flow rate in the medium condenser is set to 1/4 to 1/2 of the rated load, and cooling is performed while gradually closing the turbine bypass valve. In the transient state of reduced pressure cooling operation, even though the pressure inside the medium condenser is low, the temperature of the medium sucked into the medium circulation pump is delayed due to the time delay in the retention part of the medium condenser, and the pressure inside the medium condenser is low. Higher than saturation temperature. Therefore,
The effective NPSH of the pump becomes smaller.
一般に有効NPSHは次式で示され、ポンプの
所要NPSHより大きくなければならない。 Generally, the effective NPSH is given by the following equation and must be greater than the required NPSH of the pump.
有効NPSH＝HPT＋Ｈ−HLOSS−HPV
＞所要NPSH
HPT：容器内圧力（液柱ｍ）
Ｈ：液の水頭（液柱ｍ）
HLOSS：流路の圧力損失（液中ｍ）
HPV：ポンプ入口部の液の飽和蒸気圧力（液柱
ｍ）
有効NPSHが小さくなると媒体循環ポンプの
所要NPSHを逆転し、ポンプのキヤビテーシヨ
ンを発生し、さらにはポンプの破損につながる。
有効NPSHを当初から大きくしようとすると媒
体凝縮器を高い位置に設置する必要があり、架
構、据付費用が多大となる。Effective NPSH=H PT +H-H LOSS -H PV > Required NPSH H PT : Pressure inside the container (liquid column m) H: Liquid water head (liquid column m) H LOSS : Pressure loss in flow path (liquid column m) H PV : Saturated vapor pressure of the liquid at the pump inlet (liquid column m) If the effective NPSH becomes small, the required NPSH of the medium circulation pump will be reversed, causing cavitation of the pump and even damage to the pump.
If you try to increase the effective NPSH from the beginning, it will be necessary to install the medium condenser in a high position, which will increase the cost of the structure and installation.
本発明の目的は、ランキンサイクル方式の
LNG冷熱発電設備の起動時における減圧操作運
転において、媒体循環ポンプのキヤビテーシヨン
防止を図り、減圧操作運転時間を短くし、プラン
トの起動完了時間を短くする制御方法を提供する
ことにある。
The purpose of the present invention is to use the Rankine cycle method.
The object of the present invention is to provide a control method that prevents cavitation of a medium circulation pump during depressurization operation at the time of startup of an LNG cryogenic power generation facility, shortens the depressurization operation time, and shortens the time required to complete the start-up of the plant.
凝縮器は一般的に熱交換特性として凝縮ゾーン
と過冷却ゾーンに分かれ、各ゾーンの総括伝熱係
数は第１図の如くなる。当然のことながら、凝縮
器としては最大熱交換量を得るため、凝縮ゾーン
の伝熱係数で設計し、伝熱管群には液が浸らない
ようにして下部に凝縮液留部を設けるのが通常で
ある。プラントの起動時の減圧操作運転時は負荷
が全交換熱量の1/4〜1/2であるため、伝熱面積に
余裕がある。したがつて、本発明は伝熱管群の一
部を液に浸すことにより過冷却ゾーンを設け、凝
縮した飽和液を過冷却させるようにしたものであ
る。
A condenser is generally divided into a condensation zone and a subcooling zone in terms of heat exchange characteristics, and the overall heat transfer coefficient of each zone is as shown in FIG. Naturally, in order to obtain the maximum amount of heat exchange as a condenser, it is usually designed based on the heat transfer coefficient of the condensation zone, and a condensate reservoir is provided at the bottom so that the heat exchanger tube group is not soaked with liquid. It is. During depressurization operation at plant start-up, the load is 1/4 to 1/2 of the total heat exchanged, so there is plenty of heat transfer area. Therefore, in the present invention, a subcooling zone is provided by immersing a part of the heat transfer tube group in liquid, and the condensed saturated liquid is supercooled.
本発明の一実施例を第２図により説明する。１
は媒体凝縮器で、LNG２の冷熱により媒体が凝
縮して凝縮液４となる。LNG２は媒体凝縮器１
で熱交換し気化してNGガス３となり、燃料とし
て使用される。凝縮液４は媒体循環ポンプ５で昇
圧され、媒体蒸発器６に供給される。媒体蒸発器
６では海水７により凝縮液４が気化され、通常は
膨張タービン８に供給される。そして、膨張ター
ビン８で電力が回収され、膨張して低圧となつた
ガスは再び媒体凝縮器１にリサイクルされる。
An embodiment of the present invention will be described with reference to FIG. 1
is a medium condenser, in which the medium is condensed by the cold heat of LNG 2 and becomes condensed liquid 4. LNG2 is medium condenser 1
It exchanges heat and vaporizes to become NG gas 3, which is used as fuel. The condensate 4 is pressurized by a medium circulation pump 5 and supplied to a medium evaporator 6. In the medium evaporator 6 , the condensate 4 is vaporized by seawater 7 and is normally supplied to an expansion turbine 8 . Electric power is then recovered by the expansion turbine 8, and the expanded and low-pressure gas is recycled to the medium condenser 1 again.
起動時は、媒体凝縮器１の器内圧力は凝縮液４
が常温であるため、約７〜13Kg／cm2Ｇを示してい
る。媒体凝縮器１の器内圧力を通常運転圧力の０
〜１Kg／cm2Ｇまで減圧する場合、LNG２を一定
の低負荷で流しておき、媒体をタービンバイパス
弁９を使用して循環させながらタービンバイパス
弁９を除閉する。タービンバイパス弁９は通常運
転中は全閉であり、膨張タービン８の保護制御装
置として圧力調節装置１０を備えている。１１は
媒体凝縮器１の液位調節装置で、通常運転中は媒
体凝縮器１の伝熱管群に凝縮液４が浸つて熱交換
性能が落ちないように低液位で制御している。し
かし、起動時の減圧操作運転時には液位を媒体凝
縮器１の伝熱管群に浸るように高液位で制御し、
それにより凝縮液４を過冷却して液体循環ポンプ
５のキヤビテーシヨン発生を防止する。 At startup, the internal pressure of the medium condenser 1 is the condensate 4.
Since it is at room temperature, it shows about 7 to 13 kg/cm 2 G. The internal pressure of medium condenser 1 is set to 0, which is the normal operating pressure.
When reducing the pressure to ~1 Kg/cm 2 G, the LNG 2 is allowed to flow at a constant low load, and the turbine bypass valve 9 is opened and closed while the medium is circulated using the turbine bypass valve 9. The turbine bypass valve 9 is fully closed during normal operation, and is provided with a pressure regulator 10 as a protection control device for the expansion turbine 8. Reference numeral 11 denotes a liquid level adjustment device for the medium condenser 1, which controls the liquid level at a low level during normal operation so that the condensed liquid 4 does not soak into the heat exchanger tube group of the medium condenser 1 and the heat exchange performance deteriorates. However, during the decompression operation at startup, the liquid level is controlled at a high level so that it soaks into the heat transfer tube group of the medium condenser 1.
This supercools the condensate 4 and prevents cavitation in the liquid circulation pump 5.
本発明によれば、ランキンサイクル方式の
LNG冷熱発電設備の起動時において、媒体凝縮
器の余つている伝熱面積を利用して液位の制御を
行なうことにより凝縮液を過冷却し、減圧過渡時
のポンプのキヤビテーシヨンを防止することがで
きる。また、ポンプのキヤビテーシヨンを防止す
ることにより減圧速度を増すことができ、起動時
間を短縮することができる。
According to the present invention, the Rankine cycle method
When starting up LNG cryogenic power generation equipment, the remaining heat transfer area of the medium condenser is used to control the liquid level, thereby supercooling the condensed liquid and preventing cavitation of the pump during transient depressurization. can. Furthermore, by preventing cavitation of the pump, the decompression speed can be increased and the start-up time can be shortened.
第１図は凝縮器の凝縮ゾーンと過冷却ゾーンの
総括伝熱係数の負荷による比較を示した説明図、
第２図はランキンサイクル方式LNG冷熱発電設
備の概略系統を示した説明図である。
１……媒体凝縮器、２……LNG（液）、３……
NGガス、４……凝縮液、５……媒体循環ポン
プ、６……媒体蒸発器、７……海水、８……ター
ビン、９……タービンバイパス弁、１０……圧力
調節装置、１１……液位調節装置。
Figure 1 is an explanatory diagram showing a comparison of the overall heat transfer coefficients of the condensation zone and supercooling zone of the condenser depending on the load.
FIG. 2 is an explanatory diagram showing a schematic system of a Rankine cycle LNG cryogenic power generation facility. 1...Medium condenser, 2...LNG (liquid), 3...
NG gas, 4... Condensate, 5... Medium circulation pump, 6... Medium evaporator, 7... Seawater, 8... Turbine, 9... Turbine bypass valve, 10... Pressure regulator, 11... Liquid level adjustment device.
Claims (1)
器と、膨張タービンよりなるランキンサイクル方
式のLNG冷熱発電設備において、媒体凝縮器に
凝縮液の液位調節装置を設置し、運転起動時の液
位を高液位に制御するようにしたことを特徴とす
るLNG冷熱発電設備の制御方法。1. In a Rankine cycle type LNG cryothermal power generation facility consisting of a medium condenser, a medium circulation pump, a medium evaporator, and an expansion turbine, a condensate level adjustment device is installed in the medium condenser, and the liquid level at the start of operation is A method for controlling an LNG cryogenic power generation facility, characterized in that the liquid level is controlled to a high liquid level.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16913683A JPS6062610A (en) | 1983-09-16 | 1983-09-16 | Control method of lng cold heat power generating plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16913683A JPS6062610A (en) | 1983-09-16 | 1983-09-16 | Control method of lng cold heat power generating plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6062610A JPS6062610A (en) | 1985-04-10 |
| JPH0146687B2 true JPH0146687B2 (en) | 1989-10-11 |
Family
ID=15880948
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16913683A Granted JPS6062610A (en) | 1983-09-16 | 1983-09-16 | Control method of lng cold heat power generating plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6062610A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103277153B (en) * | 2013-05-08 | 2015-02-11 | 南京溧马新能源科技有限公司 | Organic Rankine cycle heat engine device based on multiple expansion machines |
| CN104454055A (en) * | 2014-10-22 | 2015-03-25 | 烟台荏原空调设备有限公司 | Dual-working-medium circulation power generation system with cooling function |
-
1983
- 1983-09-16 JP JP16913683A patent/JPS6062610A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6062610A (en) | 1985-04-10 |
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