JPS6213490B2 - - Google Patents
Info
- Publication number
- JPS6213490B2 JPS6213490B2 JP6059085A JP6059085A JPS6213490B2 JP S6213490 B2 JPS6213490 B2 JP S6213490B2 JP 6059085 A JP6059085 A JP 6059085A JP 6059085 A JP6059085 A JP 6059085A JP S6213490 B2 JPS6213490 B2 JP S6213490B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- pump
- heat medium
- power generation
- 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
- 238000010248 power generation Methods 0.000 claims description 18
- 229920006395 saturated elastomer Polymers 0.000 claims 1
- 239000007788 liquid Substances 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000008016 vaporization Effects 0.000 description 4
- 238000009834 vaporization Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000003949 liquefied natural gas Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000011017 operating method Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 230000007704 transition Effects 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
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/02—Arrangements or modifications of condensate or air pumps
- F01K9/023—Control thereof
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、液化天然ガスなどの低温液化ガスの
保有する冷熱を利用して電気エネルギを取出す冷
熱発電設備に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to cold power generation equipment that extracts electrical energy by utilizing cold heat possessed by low-temperature liquefied gas such as liquefied natural gas.
冷熱発電設備の運転モードとしては、低温液化
ガスの気化のみを行う気化モードと発電を行う冷
熱発電モードとがあり、運転順序としては、ま
ず、気化モード運転に入つた後に冷熱発電モード
へ移行するのが一般的である。
There are two operating modes for cold power generation equipment: a vaporization mode that only vaporizes low-temperature liquefied gas, and a cold power generation mode that generates electricity.The operating order is that the system first enters the vaporization mode and then shifts to the cold power generation mode. is common.
従来の冷熱発電設備例を第１図により説明す
る。 An example of conventional cold power generation equipment will be explained with reference to FIG.
第１図は、従来の冷熱発電設備の系統図で、導
管１を経て凝縮器２に供給された気化熱媒体は、
導管３を経て供給される低温液化ガスと熱交換す
ることで冷却、液化される。又、低温液化ガス
は、その熱媒体により加熱、気化され、導管４を
経て、例えば、火力発電所ボイラ（図示省略）等
地の需要先へ送給される。一方、凝縮器で液化さ
れた液化熱媒体は、導管５，２１、弁２０、導管
２２，８、逆止弁９、導管１０を経て凝縮器２よ
りも低位置に設置された蒸発器１１に供給され、
ここで導管１２を経て供給される海水等の加熱源
で加熱、気化される。その後、この気化熱媒体
は、導管１３，２４、弁２３、導管２５，１を経
て凝縮器２に環流され、ここで再び冷却、液化さ
れる。気化モード運転では、このようなサイクル
を繰返しつつ運転が続行され、熱媒体の運転圧力
は、この場合、熱媒体の種類及び加熱源の温度に
よつても異なるが、一般的には数Kg／cm2Ｇとな
り、又、凝縮器２と蒸発器１１とは、ほぼ均圧状
態で運転される。 FIG. 1 is a system diagram of a conventional cold power generation facility, in which the vaporized heat medium supplied to the condenser 2 via the conduit 1 is
It is cooled and liquefied by exchanging heat with the low temperature liquefied gas supplied through the conduit 3. Furthermore, the low-temperature liquefied gas is heated and vaporized by the heat medium, and is sent through the conduit 4 to a local demand destination, such as a thermal power plant boiler (not shown). On the other hand, the liquefied heat medium liquefied in the condenser passes through conduits 5 and 21, valve 20, conduits 22 and 8, check valve 9, and conduit 10, and then enters evaporator 11 installed at a lower position than condenser 2. supplied,
Here, it is heated and vaporized by a heat source such as seawater supplied through the conduit 12. Thereafter, this vaporized heat medium is circulated through the conduits 13, 24, the valve 23, and the conduits 25, 1 to the condenser 2, where it is cooled and liquefied again. In vaporization mode operation, the operation continues while repeating such a cycle, and the operating pressure of the heating medium in this case varies depending on the type of heating medium and the temperature of the heating source, but is generally several kg/kg. cm 2 G, and the condenser 2 and evaporator 11 are operated in a substantially equal pressure state.
次に、冷熱発電モードへの移行方法について説
明する。 Next, a method of shifting to cold power generation mode will be explained.
冷熱発電モードにあつては、膨張タービン（以
下タービンと略）１７を駆動するために、タービ
ン１７の入口圧力よりも出口圧力の方が当然低
く、例えば蒸発器１１の圧力が数Kg／cm2Ｇである
のに対し凝縮器２の圧力はほぼ大気圧と低いため
凝縮器２での熱媒体を蒸発器１１に供給するため
に熱媒体を昇圧するポンプ７を運転する必要があ
る。その運転手順は、一般的に先ず弁２０を閉止
し、その結果、凝縮器２内の熱媒液の液面が上昇
し、これが所定の液面位迄上昇したことを液面計
２６で確認した時点でポンプ７を起動する。次
に、弁２３を徐閉することにより凝縮器２の内圧
を徐々に低下せしめ、所定圧力まで低下したこと
を圧力計27にて確認した時点で弁１５を開きター
ビン１７を起動すると共に弁２３を閉止する。こ
の結果、蒸発器１１からの高圧の気化熱媒体は導
管１３，１４、弁１５、導管１６を経てタービン
１７に供給されタービン１７は回転を開始する。
この気化熱媒体はタービン１７を回転させること
によりその保有するエネルギを機械エネルギに変
換し、更に、発電機１８により電気エネルギに変
換して取出され、利用される。タービン１７にて
仕事をした結果、温度、圧力共に低下した気化熱
媒体は導管１９，１を経て凝縮器１に環流され、
このサイクルを繰り返しつつ冷熱発電運転が継続
される。尚、ポンプ７は液化ガス用ポンプである
ため常に所定のNPSH即ち過冷却の状態で運転す
る必要がある。すなわち、過冷却の状態で運転し
ないとポンプ１７内にて多量の気泡が発生しキヤ
ビテーシヨンを起し圧送運転不能となる。 In the cold power generation mode, in order to drive the expansion turbine (hereinafter referred to as turbine) 17, the outlet pressure of the turbine 17 is naturally lower than the inlet pressure, for example, the pressure of the evaporator 11 is several kg/cm 2 In contrast, the pressure in the condenser 2 is low, approximately atmospheric pressure, so in order to supply the heat medium in the condenser 2 to the evaporator 11, it is necessary to operate the pump 7 that boosts the pressure of the heat medium. Generally, the operating procedure is to first close the valve 20, and as a result, the level of the heat transfer liquid in the condenser 2 rises, and it is confirmed by the level gauge 26 that this has risen to a predetermined level. At that point, pump 7 is started. Next, the internal pressure of the condenser 2 is gradually lowered by gradually closing the valve 23, and when it is confirmed by the pressure gauge 27 that the pressure has decreased to a predetermined pressure, the valve 15 is opened and the turbine 17 is started, and the valve 23 is gradually closed. Close. As a result, the high pressure vaporized heat medium from the evaporator 11 is supplied to the turbine 17 via the conduits 13, 14, the valve 15, and the conduit 16, and the turbine 17 starts rotating.
The energy of this vaporized heat medium is converted into mechanical energy by rotating the turbine 17, and further converted into electrical energy by the generator 18, which is extracted and utilized. As a result of the work done in the turbine 17, the vaporized heat medium whose temperature and pressure have decreased is returned to the condenser 1 through the conduits 19 and 1.
The cold power generation operation continues while repeating this cycle. Incidentally, since the pump 7 is a pump for liquefied gas, it must always be operated in a predetermined NPSH, that is, supercooled state. That is, if the pump 17 is not operated in a supercooled state, a large amount of bubbles will be generated within the pump 17, causing cavitation and making pumping operation impossible.
また、この種のポンプの軸受部の潤滑は処理流
体そのものを用いているため、極端な場合は軸受
焼損などの重大事故につながる惧れがある。 Furthermore, since the processing fluid itself is used to lubricate the bearings of this type of pump, in extreme cases, there is a risk of serious accidents such as bearing burnout.
このような冷熱発電設備では、ポンプのトラブ
ルを避けるべく、タービンをバイパスした導管の
途中に設けられた弁２３をゆつくり操作している
が、それでも圧力降下速度が許容範囲を超えてポ
ンプ７がキヤビテーシヨンを起しトリツプする起
動失敗が生じる可能性を残している。 In such cold power generation equipment, in order to avoid problems with the pump, the valve 23 installed in the middle of the conduit that bypasses the turbine is operated slowly, but the pressure drop rate still exceeds the allowable range and the pump 7 This leaves open the possibility of startup failure due to cavitation and tripping.
本発明の目的は、ポンプのトラブルを生じさせ
ないと冷熱発電設備を提供することである。
An object of the present invention is to provide a cold power generation facility that does not cause pump troubles.
本発明は、タービンをバイパスするバイパス通
路の途中に操作用の弁と並列に自動調節弁を設
け、さらに昇圧用のポンプ入側における液体熱媒
体の圧力をその飽和圧力よりも高圧力に維持する
ようにその自動調節弁を自動調節する圧力調節計
を設けたことを特徴とする。
The present invention provides an automatic control valve in parallel with the operating valve in the middle of a bypass passage that bypasses the turbine, and further maintains the pressure of the liquid heat medium at the inlet side of the pump for boosting the pressure at a higher pressure than its saturation pressure. The present invention is characterized in that a pressure regulator is provided to automatically adjust the automatic control valve.
以下、本発明を具体的実施例に基づき詳細に説
明する。
Hereinafter, the present invention will be explained in detail based on specific examples.
第２図は、本発明の一実施例における冷熱発電
設備の系統図である。なお、第２図において、第
１図と同一機器等は同一符号を付している。第２
図において、２８は圧力調節計であり、ポンプ７
の入側における液体熱媒体の圧力を検出し、この
圧力を飽和圧力よりも高圧力である設定圧力にす
るための調節信号を出力する。２９は温度検出器
であり、ポンプ７の入側の液化熱媒体の温度を検
出する。この温度検出器２９の出力は演算器３０
に入力される。演算器３０は、入力された温度を
基に該温度における液化熱媒体の飽和圧力を求
め、これよりも高圧力となる。圧力設定値を圧力
調節計２８に出力する。３１は自動調節弁であ
り、圧力調節計２８の出力する調節信号によつて
自動調節される。この調節弁３１は、弁１５と膨
張タービン１７とをバイパスする通路の途中に設
けられた弁２３に並列に設置されている。３２と
３３は導管である。 FIG. 2 is a system diagram of a cold power generation facility in one embodiment of the present invention. In FIG. 2, the same equipment as in FIG. 1 is given the same reference numeral. Second
In the figure, 28 is a pressure regulator, and the pump 7
Detects the pressure of the liquid heat medium on the inlet side of the system, and outputs an adjustment signal to bring this pressure to a set pressure higher than the saturation pressure. A temperature detector 29 detects the temperature of the liquefied heat medium on the inlet side of the pump 7. The output of this temperature detector 29 is
is input. Based on the input temperature, the computing unit 30 determines the saturation pressure of the liquefied heat medium at the input temperature, and the pressure is higher than this. The pressure set value is output to the pressure regulator 28. Reference numeral 31 denotes an automatic control valve, which is automatically adjusted in accordance with a control signal output from the pressure regulator 28. This control valve 31 is installed in parallel with the valve 23 provided in the middle of a passage that bypasses the valve 15 and the expansion turbine 17. 32 and 33 are conduits.
このような構成において、気化モード運転から
冷熱発電モード運転への移行は次のように行なわ
れる。まず、弁２０を閉止する。この結果、凝縮
器２内の液化熱媒体の液面が上昇し、所定の液面
位まで上昇した時点でポンプ７を起動する。この
起動により、ポンプ７には液化熱媒体が吸入され
るが、この吸入側（入側）の液化熱媒体の温度は
温度検出器２９で検出される。同様に、液化熱媒
体の圧力も圧力調節計２８で検出される。演算器
３０は、温度検出器２９の出力を入力して、液化
熱媒体のその温度に対する飽和圧力を求め、これ
よりも高い圧力を圧力調節計２８の設定圧力とし
て出力する。圧力調節計２８は、その設定圧力と
検出した実際の圧力とを比較し、実際の圧力が設
定圧力より高い場合には自動調節弁３１を閉方向
に、逆に低い場合には自動調節弁３１を開方向に
作動させる。例えば、弁２３を急閉した結果、ポ
ンプ７吸入側の圧力が圧力調節計２８の設定値よ
りも低くならんとした時は自動調節弁３１が自動
的に開くのでポンプ７吸入側は圧力調節計２８の
設定値、即ち過冷却状態を維持する。そして、圧
力低下により熱媒体の温度が低下したなら自動的
に圧力調節計２８の設定値を下げるので、この動
作を繰り返しつつ圧力は低下の一途をたどる。そ
して凝縮器２の内圧が所定の圧力、例えば、0.5
Kg／cm2Ｇ迄低下したことが圧力計２７で確認され
た時点で弁１５を開きタービン１７を起動する。
この結果、蒸発器１１からの気化熱媒体は導管１
３，１４、弁１５、導管１６を経てタービン１７
に供給され、タービン１７は回転を開始する。 In such a configuration, the transition from vaporization mode operation to cold power generation mode operation is performed as follows. First, valve 20 is closed. As a result, the liquid level of the liquefied heat medium in the condenser 2 rises, and when the liquid level rises to a predetermined level, the pump 7 is started. As a result of this activation, the liquefied heat medium is sucked into the pump 7, and the temperature of the liquefied heat medium on the suction side (inlet side) is detected by the temperature detector 29. Similarly, the pressure of the liquefied heat medium is also detected by the pressure regulator 28. The computing unit 30 inputs the output of the temperature detector 29, determines the saturation pressure of the liquefied heat medium at that temperature, and outputs a pressure higher than this as the set pressure of the pressure regulator 28. The pressure regulator 28 compares the set pressure with the detected actual pressure, and if the actual pressure is higher than the set pressure, the automatic regulating valve 31 is closed, and if the actual pressure is lower, the automatic regulating valve 31 is closed. Operate in the opening direction. For example, if the pressure on the suction side of the pump 7 does not become lower than the set value of the pressure regulator 28 as a result of suddenly closing the valve 23, the automatic control valve 31 will automatically open, so the suction side of the pump 7 will be connected to the pressure regulator. The set value of 28, that is, the supercooled state is maintained. Then, when the temperature of the heat medium decreases due to a decrease in pressure, the set value of the pressure regulator 28 is automatically lowered, so as this operation is repeated, the pressure continues to decrease. Then, the internal pressure of the condenser 2 is set to a predetermined pressure, for example, 0.5
When the pressure gauge 27 confirms that the pressure has decreased to Kg/cm 2 G, the valve 15 is opened and the turbine 17 is started.
As a result, the vaporized heat medium from the evaporator 11 is transferred to the conduit 1
3, 14, valve 15, conduit 16 to turbine 17
The turbine 17 starts rotating.
本実施例のような冷熱発電設備では、ポンプの
吸入部の状態を如何なる場合でも自動的に過冷却
状態に維持できるので、ポンプのキヤビテーシヨ
ンの発生が防止でき、これに伴なうポンプ停止に
よる起動失敗や、ポンプ軸受の焼損事故を充分に
防止できるのみならず、起動時間が必要最小限に
短縮できるため起動効率が良く経済的となる。 In the cold thermal power generation equipment like this example, the state of the pump suction part can be automatically maintained in a supercooled state under any circumstances, so it is possible to prevent the occurrence of pump cavitation, and it is possible to prevent the pump from starting due to the pump stoppage due to this. Not only can failures and burnout accidents of the pump bearings be sufficiently prevented, but the startup time can be shortened to the necessary minimum, resulting in high startup efficiency and economy.
以上説明したように本発明によれば、ポンプ入
側の圧力をその飽和圧力以上に保つことができる
ので、ポンプのトラブルを生じさせることがなく
なる。
As described above, according to the present invention, the pressure on the inlet side of the pump can be maintained at a level higher than its saturation pressure, thereby eliminating problems with the pump.
第１図は、従来の冷熱発電設備の系統図、第２
図は本発明の一実施例を示す冷熱発電設備の系統
図である。
１，３から６，８，１０，１２から１４，１
６，１９，２１，２２，２４，２５，３２，３３
……導管、２……凝縮器、７……ポンプ、９……
逆止弁、１１……蒸発器、１５，２０，２３……
弁、１７……タービン、１８……発電機、２６…
…液面計、２７……圧力計、２８……圧力調節
計、２９……温度検出器、３０……演算器、３１
……自動調節弁。
Figure 1 is a system diagram of conventional cold power generation equipment;
The figure is a system diagram of a cold power generation facility showing an embodiment of the present invention. 1,3 to 6,8,10,12 to 14,1
6, 19, 21, 22, 24, 25, 32, 33
... Conduit, 2 ... Condenser, 7 ... Pump, 9 ...
Check valve, 11... Evaporator, 15, 20, 23...
Valve, 17... Turbine, 18... Generator, 26...
...Liquid level gauge, 27...Pressure gauge, 28...Pressure regulator, 29...Temperature detector, 30...Calculator, 31
...Automatic control valve.
Claims (1)
する凝縮器と、液化熱媒体を昇圧するポンプと、
蒸発器と、第１の弁と、該蒸発器で気化された気
化熱媒体の供給を受け駆動する膨張タービンと、
前記凝縮器とを順次直列に接続した熱サイクルを
有し、前記ポンプをバイパスする通路の途中に第
２の弁と、前記第１の弁と前記膨張タービンとを
バイパスする通路の途中に第３の弁と、前記膨張
タービンにより駆動される発電機とを備えた冷熱
発電設備において、前記第３の弁と並列に第４の
弁を設けると共に前記ポンプの入側における液化
熱媒体の圧力を飽和圧力よりも高圧力に維持する
ように該第４の弁を自動調節する圧力調節計を設
けたことを特徴とする冷熱発電設備。1. A condenser that liquefies the vaporized heat medium using the cold heat of the low-temperature liquefied gas, and a pump that increases the pressure of the liquefied heat medium.
an evaporator, a first valve, and an expansion turbine driven by receiving the vaporized heat medium vaporized by the evaporator;
a heat cycle in which the condenser and the expansion turbine are sequentially connected in series, a second valve in the middle of a passage that bypasses the pump, and a third valve in the middle of a passage that bypasses the first valve and the expansion turbine. In the cryogenic power generation equipment including a valve and a generator driven by the expansion turbine, a fourth valve is provided in parallel with the third valve, and the pressure of the liquefied heat medium on the inlet side of the pump is saturated. 1. A cryogenic power generation facility characterized by being provided with a pressure regulator that automatically adjusts the fourth valve so as to maintain the pressure at a higher pressure than the pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6059085A JPS60222511A (en) | 1985-03-27 | 1985-03-27 | Thermal power generating equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6059085A JPS60222511A (en) | 1985-03-27 | 1985-03-27 | Thermal power generating equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60222511A JPS60222511A (en) | 1985-11-07 |
| JPS6213490B2 true JPS6213490B2 (en) | 1987-03-26 |
Family
ID=13146601
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6059085A Granted JPS60222511A (en) | 1985-03-27 | 1985-03-27 | Thermal power generating equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60222511A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017072054A (en) * | 2015-10-07 | 2017-04-13 | いすゞ自動車株式会社 | Power generation device and method for controlling power generation device |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012021757A2 (en) | 2010-08-11 | 2012-02-16 | Cummins Intellectual Property, Inc. | Split radiator design for heat rejection optimization for a waste heat recovery system |
| CN103180554B (en) * | 2010-08-13 | 2016-01-20 | 康明斯知识产权公司 | Rankine Cycle Condenser Pressure Control Using Transducer Bypass Valve |
| US8826662B2 (en) | 2010-12-23 | 2014-09-09 | Cummins Intellectual Property, Inc. | Rankine cycle system and method |
| DE112011104516B4 (en) | 2010-12-23 | 2017-01-19 | Cummins Intellectual Property, Inc. | System and method for regulating EGR cooling using a Rankine cycle |
| DE102012000100A1 (en) | 2011-01-06 | 2012-07-12 | Cummins Intellectual Property, Inc. | Rankine cycle-HEAT USE SYSTEM |
| WO2012096958A1 (en) | 2011-01-10 | 2012-07-19 | Cummins Intellectual Property, Inc. | Rankine cycle waste heat recovery system |
| US8919328B2 (en) | 2011-01-20 | 2014-12-30 | Cummins Intellectual Property, Inc. | Rankine cycle waste heat recovery system and method with improved EGR temperature control |
| US8893495B2 (en) | 2012-07-16 | 2014-11-25 | Cummins Intellectual Property, Inc. | Reversible waste heat recovery system and method |
| US9140209B2 (en) | 2012-11-16 | 2015-09-22 | Cummins Inc. | Rankine cycle waste heat recovery system |
| US9845711B2 (en) | 2013-05-24 | 2017-12-19 | Cummins Inc. | Waste heat recovery system |
| FR3020090B1 (en) * | 2014-04-16 | 2019-04-12 | IFP Energies Nouvelles | DEVICE FOR CONTROLLING A CLOSED CIRCUIT OPERATING ACCORDING TO A RANKINE CYCLE AND METHOD USING SUCH A DEVICE |
-
1985
- 1985-03-27 JP JP6059085A patent/JPS60222511A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017072054A (en) * | 2015-10-07 | 2017-04-13 | いすゞ自動車株式会社 | Power generation device and method for controlling power generation device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60222511A (en) | 1985-11-07 |
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