JPS6147965B2 - - Google Patents
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- Publication number
- JPS6147965B2 JPS6147965B2 JP52120860A JP12086077A JPS6147965B2 JP S6147965 B2 JPS6147965 B2 JP S6147965B2 JP 52120860 A JP52120860 A JP 52120860A JP 12086077 A JP12086077 A JP 12086077A JP S6147965 B2 JPS6147965 B2 JP S6147965B2
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- Prior art keywords
- heat medium
- intermediate heat
- heat
- medium
- tank
- Prior art date
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Description
【発明の詳細な説明】
本発明は廃熱利用発電プラントの改良に関する
ものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a power generation plant utilizing waste heat.
従来のこの種発電プラントでは中間熱体に水を
使用し、間接式熱交換器を用いて廃熱を水に回収
し、さらに水と熱媒体（低沸点媒体）との熱交換
を間接式交換器により行い、発生した蒸気により
タービンを駆動して発電を行つている。このよう
なプラントでは間接式熱交換器が大形となるた
め、発電プラントも巨大化する。 Conventional power generation plants of this type use water as an intermediate heating element, recover waste heat into water using an indirect heat exchanger, and then use indirect heat exchange to exchange heat between water and a heat medium (low boiling point medium). The generated steam drives a turbine to generate electricity. In such plants, the indirect heat exchangers are large, so the power generation plants are also large.
他の発電プラントの例では中間熱媒体を使用せ
ずに、低沸点媒体に廃熱を回収させて発電を行う
方法が採用されている。このようなプラントでは
低沸点媒体の分解温度が低いため、廃熱温度が高
温の場合には使用できないという欠点がある。 Other examples of power generation plants have adopted a method of generating electricity by recovering waste heat in a low boiling point medium without using an intermediate heat medium. Such a plant has the disadvantage that it cannot be used when the waste heat temperature is high because the decomposition temperature of the low boiling point medium is low.
本発明は上記の点にかんがみ間接式熱交換器に
比して小形、軽量の直接式熱交換器を用いしかも
廃熱温度が高くても熱媒体である低沸点媒体の熱
分解を生じる虞れのない、高効率の廃熱利用発電
プラントを提供することを目的とするもので、熱
媒体を作動流体とするタービンと、このタービン
に接続する凝縮器と、前記熱媒体と中間熱媒体と
を熱交換せしめる熱交換器と、上記中間熱媒体を
加熱する加熱器とを備えた廃熱利用発電プラント
において、前記熱交換器を直接式熱交換器とな
し、この熱交換器と中間熱媒体ポンプとの間にフ
ラツシユ蒸発を行う中間熱媒体タンクを設け、こ
の中間納媒体タンクで蒸発した熱体蒸気をタービ
ンの中圧段へ導入する管路を設け、かつ、前記の
凝縮器と中間熱媒体タンクとを、減圧弁を介して
連通して、上記中間熱媒体タンク内の圧力を制御
し得る構造としたことを特徴とする。 In consideration of the above points, the present invention uses a direct heat exchanger which is smaller and lighter than an indirect heat exchanger, and also eliminates the risk of thermal decomposition of the low boiling point medium which is the heat medium even if the waste heat temperature is high. The purpose is to provide a high-efficiency power generation plant using waste heat, which is free from heat transfer, and includes a turbine that uses a heat medium as a working fluid, a condenser connected to this turbine, and the heat medium and intermediate heat medium. In a waste heat power generation plant comprising a heat exchanger for exchanging heat and a heater for heating the intermediate heat medium, the heat exchanger is a direct heat exchanger, and the heat exchanger and the intermediate heat medium pump are provided. An intermediate heat medium tank for performing flash evaporation is provided between the condenser and the intermediate heat medium, and a pipe line is provided for introducing the hot steam evaporated in the intermediate storage tank to the intermediate pressure stage of the turbine. It is characterized by having a structure in which the pressure inside the intermediate heat medium tank can be controlled by communicating with the tank via a pressure reducing valve.
以下本発明の実施例を図面を参照して説明す
る。 Embodiments of the present invention will be described below with reference to the drawings.
第１図において、１はタービン、２はタービン
１に直結された発電機、３はタービン１に接続さ
れたコンデンサ、４は直接式熱交換器、５は中間
熱媒体タンク、６は加熱器、７はコンデンサ３と
直接式熱交換器４とを連通する熱媒体液通路８に
設けられた熱媒体ポンプ、９は直接式熱交換器４
と中間媒体タンク５とを連通する中間熱媒体通路
１０に設けられた減圧弁、１１は中間熱媒体タン
ク５と加熱器６の熱交換管６ａとを連通する中間
熱媒体通路１２に設けられた中間熱媒体ポンプ、
１３は前記熱交換管６ａと直接式熱交換器４とを
連通する中間熱媒体通路、１４はタービン１と直
接式熱交換器４とを連通する熱媒体蒸気通路１５
に設けられた主弁、１６はタービン１と中間媒体
タンク５とを連通する減圧蒸気通路、１７はコン
デンサ３と中熱媒体タンク５とを連通す減圧用通
路、１８は上記減圧用通路１７に設けられた減圧
弁、１９は加熱器６に接続された加熱媒体通路で
ある。 In FIG. 1, 1 is a turbine, 2 is a generator directly connected to the turbine 1, 3 is a condenser connected to the turbine 1, 4 is a direct heat exchanger, 5 is an intermediate heat medium tank, 6 is a heater, 7 is a heat medium pump provided in a heat medium liquid passage 8 that communicates the condenser 3 and the direct heat exchanger 4; 9 is the direct heat exchanger 4;
A pressure reducing valve 11 is provided in an intermediate heat medium passage 10 that communicates between the intermediate heat medium tank 5 and the intermediate heat medium tank 5. intermediate heat medium pump,
13 is an intermediate heat medium passage that communicates the heat exchange tube 6a and the direct heat exchanger 4; 14 is a heat medium steam passage 15 that communicates the turbine 1 and the direct heat exchanger 4;
16 is a reduced pressure steam passage communicating with the turbine 1 and the intermediate medium tank 5; 17 is a pressure reducing passage communicating between the condenser 3 and the intermediate heat medium tank 5; 18 is a pressure reducing passage provided in the pressure reducing passage 17; The provided pressure reducing valve 19 is a heating medium passage connected to the heater 6.
次に上記構成からなる本実施例の作用について
説明する。 Next, the operation of this embodiment having the above configuration will be explained.
中間熱媒体タンク５内の中間熱媒体（例えばタ
ービン油または潤滑油）は中間熱媒体ポンプ（油
ポンプ）１１で加圧された後に通路１２を経て加
熱器６に供給される。この加熱器６において、加
熱媒体通路１９を経て供給された廃熱利用の加熱
媒体により加熱された中間熱媒体は、通路１３を
経て直接式熱交換器４に導入される。該交換器４
に導入された中間熱媒体は、熱媒体液通路８を経
て供給される熱媒体（低沸点媒体）と混合して熱
交換される。 The intermediate heat medium (for example, turbine oil or lubricating oil) in the intermediate heat medium tank 5 is pressurized by an intermediate heat medium pump (oil pump) 11 and then supplied to the heater 6 through a passage 12 . In this heater 6, an intermediate heat medium heated by a heating medium utilizing waste heat supplied through a heating medium passage 19 is introduced into a direct heat exchanger 4 through a passage 13. The exchanger 4
The intermediate heat medium introduced into the intermediate heat medium is mixed with the heat medium (low boiling point medium) supplied through the heat medium liquid passage 8 and heat exchanged therewith.
直接式熱交換器４内で中間媒体により加熱され
た熱体は蒸気となり、この蒸気は通路１５および
主弁１４を経てタービン１に導入されて仕事を
し、発電機２を駆動する。タービン１から吐出さ
れた熱媒体はコンデンサ３に導入され凝縮、冷却
されて液体となり、この液体は熱媒体ポンプ７に
より加圧されて直接式熱交換器４に供給されて循
環する。 The heat body heated by the intermediate medium in the direct heat exchanger 4 becomes steam, and this steam is introduced into the turbine 1 through the passage 15 and the main valve 14 to perform work and drive the generator 2. The heat medium discharged from the turbine 1 is introduced into the condenser 3, condensed and cooled to become a liquid, and this liquid is pressurized by the heat medium pump 7 and supplied to the direct heat exchanger 4 for circulation.
一方、直接式熱交換器４から吐出された中間熱
媒体は熱媒体を溶解しているが、通路１０および
減圧弁９を経て中間媒体タンク５に導入され、こ
のタンク５内でフラツシユ蒸発して熱媒体溶解度
が減少し、溶解していた熱媒体の１部を分離す
る。このため該中間熱媒体が中間熱媒体ポンプ１
１により通路１２を経て熱交換管６ａを流通する
際に、加熱器６における熱媒体蒸気発生量が減少
する。 On the other hand, the intermediate heat medium discharged from the direct heat exchanger 4 has dissolved heat medium, but is introduced into the intermediate medium tank 5 through the passage 10 and the pressure reducing valve 9, and is flash-evaporated in the tank 5. The solubility of the heating medium decreases and a portion of the heating medium that was dissolved is separated. Therefore, the intermediate heat medium is the intermediate heat medium pump 1.
1, the amount of heat medium vapor generated in the heater 6 decreases when it flows through the heat exchange tube 6a via the passage 12.
上記の中間熱媒体としてタービン油を使用し、
熱媒体として親和力の強い低沸点媒体であるＲ
（Refrigenrant）―11、Ｒ―113を使用した場合、
中間熱媒体温度と熱媒体溶液解度の関係を図示す
ると第２図のとおりであつて、本図は中間熱媒体
の圧力をパラメータとして示してある。 Using turbine oil as the above intermediate heat medium,
R is a low boiling point medium with strong affinity as a heat medium.
(Refrigenrant)-11, when using R-113,
The relationship between the intermediate heat medium temperature and the solubility of the heat medium solution is illustrated in FIG. 2, and this figure shows the pressure of the intermediate heat medium as a parameter.
直接式熱交換器４の出口における中間熱媒体の
圧量力がP2、温度がT2のとき（点ａ）、熱媒体の
溶解度はn2である。前記圧力P2、温度T2の中間
熱媒体は中間熱媒体タンク５に導入されて圧力P1
に減圧され、フラツシユ蒸発により降温してT1
となり、（点ｂ）溶解度はn1に低下する。そして
ポンプ１１により加圧された昇圧、昇温し、圧力
P3、温度T3となつて（点ｄ）加熱器６に供給さ
れる。このとき熱媒体の溶解可能な限度（溶解
度）はn3であるが、中間熱媒体ポンプ１１と加熱
器６との間では熱媒体の供給がないため点ｂにお
ける熱媒体溶解度n1がそのまま保たれている。中
間熱媒体は加熱器６で温度T4まで加熱され、か
つ熱交換管６ａによる圧力損失のため圧力がP2に
低下する（点ｅ）ので、溶解度はn4となる。この
ため（n1―n4）の熱媒体は加熱器６内で蒸気とな
つて蒸発する。この蒸気が、もし、過多であると
熱交換管６ａの表面に乾燥する部分を生じ、局部
的に過熱して熱媒体を分解させる恐れがある。 When the pressure force of the intermediate heating medium at the outlet of the direct heat exchanger 4 is P 2 and the temperature is T 2 (point a), the solubility of the heating medium is n 2 . The intermediate heat medium at the pressure P 2 and temperature T 2 is introduced into the intermediate heat medium tank 5 and has a pressure P 1 .
The pressure is reduced to T 1 , and the temperature decreases due to flash evaporation.
(Point b) The solubility decreases to n 1 . Then, the pressure is increased by the pump 11, the temperature is increased, and the pressure is increased.
P 3 and temperature T 3 (point d) and is supplied to the heater 6. At this time, the meltable limit (solubility) of the heat medium is n 3 , but since there is no supply of heat medium between the intermediate heat medium pump 11 and the heater 6, the heat medium solubility n 1 at point b remains unchanged. It's dripping. The intermediate heat medium is heated to a temperature T4 by the heater 6, and the pressure decreases to P2 due to the pressure loss due to the heat exchange tube 6a (point e), so the solubility becomes n4 . Therefore, the heat medium (n 1 -n 4 ) turns into steam and evaporates within the heater 6. If this steam is excessive, it may cause dry areas on the surface of the heat exchange tube 6a, causing local overheating and decomposing the heat medium.
ところが本実施例では前述したように熱媒体を
溶解する中間熱媒体を直接式熱交換器４から中間
熱媒体タンク５に導入してフラツシユ蒸発させ、
ここで熱媒体溶解度を低下させるので、加熱器６
における熱媒体蒸気発生量を減少させることがで
き、該加熱器６における熱媒体の分解を防止する
ことができる。 However, in this embodiment, as described above, the intermediate heat medium that dissolves the heat medium is introduced from the direct heat exchanger 4 into the intermediate heat medium tank 5, and flash-evaporated.
Here, the solubility of the heat medium is reduced, so the heater 6
The amount of heat medium vapor generated in the heater 6 can be reduced, and decomposition of the heat medium in the heater 6 can be prevented.
上述の作用、効果を第２図について再度、順を
追つて眺めると、前記中間熱媒体は直接式熱交換
器４の出口においてａ状態すなわち圧力P2、温度
T2であるが中間熱媒体タンク５でフラツシユ蒸
発させることによりｂ状態、すなわち圧力P1、温
度T1となる。このように温度および圧力が低下
するため溶解度もn2からn1に低下し、（n2―n1）に
相当する熱媒体が中間熱媒体タンク５において蒸
気として分離される。したがつて加熱器６におけ
る蒸気発生量は（n1―n4）に相当する。このよう
に、中間熱媒体タンク５におけるフラツシユ蒸発
をしない場合に比して蒸発発生量が大幅に減少す
る。前記フラツシユ蒸発で発生した蒸気は直接式
熱交換器４および加熱器６で発生する蒸気に比べ
て低圧であるから、中間熱媒体タンク５を減圧蒸
気通路１６を介してタービン１の中圧段へ接続す
ると仕事をさせることもでき、これによつつてプ
ラント全体の熱効率が著しく向上する。この場
合、中間熱媒体タンク５内の圧力を減圧弁１８で
調節し、蒸気通路１６内の蒸気流量を制御する。
これにより、起動操作時、停止操作時などのよう
に、プラントが定常状態でない場合においても、
溶液解度制御が容易となる。 If we look at the above-mentioned functions and effects in order again with reference to FIG .
T2 , but by flash evaporation in the intermediate heat medium tank 5, it becomes state b, that is, pressure P1 and temperature T1 . As the temperature and pressure decrease in this way, the solubility also decreases from n 2 to n 1 , and the heat medium corresponding to (n 2 −n 1 ) is separated as vapor in the intermediate heat medium tank 5. Therefore, the amount of steam generated in the heater 6 corresponds to (n 1 −n 4 ). In this way, the amount of evaporation generated is significantly reduced compared to the case where flash evaporation in the intermediate heat medium tank 5 is not performed. Since the steam generated by the flash evaporation has a lower pressure than the steam generated in the direct heat exchanger 4 and the heater 6, the intermediate heat medium tank 5 is transferred to the intermediate pressure stage of the turbine 1 via the reduced pressure steam passage 16. When connected, they can also perform work, thereby significantly increasing the thermal efficiency of the entire plant. In this case, the pressure in the intermediate heat medium tank 5 is adjusted by the pressure reducing valve 18, and the steam flow rate in the steam passage 16 is controlled.
As a result, even when the plant is not in a steady state, such as during startup or shutdown operations,
Solution solubility control becomes easy.
前記中間熱媒体タンク５内の中間熱媒体はその
液面近傍では温度が高いが、該タンク５の底部で
の温度が低い。 The temperature of the intermediate heat medium in the intermediate heat medium tank 5 is high near the liquid level, but the temperature at the bottom of the tank 5 is low.
今、仮りにタンク５の底部における中間熱媒体
が静止して平衡している状態を想定すると、圧力
P1、温度T1に相当する溶解度n1であることにな
る。しかし、実際には対流によつて、液面付近の
中間熱媒体（T1よりも高温、従つて、n1よりも
低溶解度）が流動してくる。このため、タンク底
部の中間熱媒体は、溶解度n1に飽和していない状
態となつており、蒸気が発生しにくい。従つて前
記ポンプ１１におけるキヤビテーシヨンの発生を
軽減することができる。 Now, assuming that the intermediate heat medium at the bottom of tank 5 is stationary and in equilibrium, the pressure
The solubility n 1 corresponds to P 1 and temperature T 1 . However, in reality, the intermediate heat medium near the liquid surface (higher temperature than T 1 , therefore, lower solubility than n 1 ) flows due to convection. Therefore, the intermediate heat medium at the bottom of the tank is not saturated with solubility n 1 , and steam is hardly generated. Therefore, the occurrence of cavitation in the pump 11 can be reduced.
第３図は他の実施例を示したもので、中間熱媒
体タンク５と中間熱媒体ポンプ１１との間に冷却
器２０を設け、中間熱媒体と熱媒体とを熱交換さ
せて冷却するようにした点が上記実施例（第１
図）と異なる。その他構造は第１図と同一である
から説明を省略する。なお第３図に示す符号のう
ち第１図に示す符号と同一のものは同一部分を示
すものとする。 FIG. 3 shows another embodiment, in which a cooler 20 is provided between the intermediate heat medium tank 5 and the intermediate heat medium pump 11, and the intermediate heat medium and the heat medium are cooled by heat exchange. The points made in the above embodiment (first
Figure) is different. The rest of the structure is the same as that in FIG. 1, so the explanation will be omitted. Note that among the symbols shown in FIG. 3, the same symbols as those shown in FIG. 1 indicate the same parts.
この実施例によれば中間熱媒体ポンプ１１の入
口温度を第２図のT1よりもさらに低く設定する
ことができる。 According to this embodiment, the inlet temperature of the intermediate heat medium pump 11 can be set even lower than T 1 in FIG. 2.
第２図に示した圧力カーブP1について見ると、
温度T1のとき熱媒体溶液解度n1である。 Looking at the pressure curve P 1 shown in Figure 2,
When the temperature is T 1 , the solubility of the heat medium solution is n 1 .
従つて、温度がT1よりも低下すると、このカ
ーブP1が左上がりに傾斜しているので溶解度がn1
よりも増加する。 Therefore, when the temperature drops below T 1 , this curve P 1 slopes upward to the left, so the solubility decreases to n 1
increases more than
従つて、濃度n1の熱媒体を溶解した中間熱媒体
は温度T1以下（圧力P1）では不飽和であり、蒸気
を発生せしめにくい。このため、中間熱媒体がポ
ンプ１１の吸入口付近で撹拌されても蒸気を発生
しないから、キヤビテーシヨンの発生する恐れは
なく安全性を向上させることができる。 Therefore, the intermediate heat medium obtained by dissolving the heat medium of concentration n 1 is unsaturated at a temperature below T 1 (pressure P 1 ) and is difficult to generate steam. Therefore, even if the intermediate heat medium is stirred near the suction port of the pump 11, no steam is generated, so there is no risk of cavitation occurring, and safety can be improved.
以上説明したように、本発明によれば中間熱媒
体と熱媒体の熱交換を直接式熱交換器で行うこと
によりプラントをコンパクト化すると共に、中間
熱媒体に溶解する熱媒体の熱分解を防止し、か
つ、プラント全体の熱効果を向上させることがで
きる。 As explained above, according to the present invention, the heat exchange between the intermediate heat medium and the heat medium is performed using a direct heat exchanger, thereby making the plant more compact and preventing thermal decomposition of the heat medium dissolved in the intermediate heat medium. Moreover, the thermal effect of the entire plant can be improved.
第１図は本発明の廃熱利用発電プラントの一実
施例を示す系統図、第２図は中間熱媒体温度と熱
媒体溶解度の関係を示す線図、第３図は本発明に
係る他の実施例を示す系統図である。
１……タービン、３……凝縮器、４……直接式
熱交換器、５……中間熱媒体タンク、６……加熱
器、１１……中間熱媒体ポンプ、２０……中間熱
媒体冷却器。
Fig. 1 is a system diagram showing one embodiment of the waste heat power generation plant of the present invention, Fig. 2 is a line diagram showing the relationship between intermediate heat medium temperature and heat medium solubility, and Fig. 3 is a system diagram showing an example of the waste heat power generation plant of the present invention. It is a system diagram showing an example. 1... Turbine, 3... Condenser, 4... Direct heat exchanger, 5... Intermediate heat medium tank, 6... Heater, 11... Intermediate heat medium pump, 20... Intermediate heat medium cooler .
Claims (1)
ービンに接続する凝縮器と、前記熱媒体と中間熱
媒体とを熱交換せしめる熱交換器と、上記中間熱
媒体を加熱する加熱器とを備えた廃熱利用発電プ
ラントにおいて、前記熱交換器を直接式熱交換器
となし、この熱交換器と中間熱媒体ポンプとの間
にフラツシユ蒸発を行う中間熱媒体タンクを設
け、この中間熱媒体タンクで蒸発した熱媒体蒸気
をタービンの中圧段へ導入する管路を設け、か
つ、前記の凝縮器と中間熱媒体タンクとを、減圧
弁を介して連通して、上記中間熱媒体タンク内の
圧力を制御し得る構造としたことを特徴とする廃
熱利用発電プラント。1. Equipped with a turbine that uses a heat medium as a working fluid, a condenser connected to the turbine, a heat exchanger that exchanges heat between the heat medium and the intermediate heat medium, and a heater that heats the intermediate heat medium. In a power generation plant using waste heat, the heat exchanger is a direct heat exchanger, an intermediate heat medium tank for flash evaporation is provided between the heat exchanger and the intermediate heat medium pump, and the intermediate heat medium tank is used to perform flash evaporation. A pipe line is provided for introducing the evaporated heat medium vapor into the intermediate pressure stage of the turbine, and the condenser and the intermediate heat medium tank are communicated via a pressure reducing valve, so that the pressure in the intermediate heat medium tank is A waste heat power generation plant characterized by having a structure that allows control of.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12086077A JPS5455256A (en) | 1977-10-11 | 1977-10-11 | Waste-heat utilizing power plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12086077A JPS5455256A (en) | 1977-10-11 | 1977-10-11 | Waste-heat utilizing power plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5455256A JPS5455256A (en) | 1979-05-02 |
| JPS6147965B2 true JPS6147965B2 (en) | 1986-10-22 |
Family
ID=14796732
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12086077A Granted JPS5455256A (en) | 1977-10-11 | 1977-10-11 | Waste-heat utilizing power plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5455256A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02131726A (en) * | 1988-11-11 | 1990-05-21 | Tokyo Electric Co Ltd | vacuum cleaner |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5865917A (en) * | 1981-10-15 | 1983-04-19 | Takuma Sogo Kenkyusho:Kk | Power generating device of exhaust heat recovery in diesel engine |
| EP4208628B1 (en) * | 2020-09-04 | 2026-03-25 | Technion Research & Development Foundation Limited | Heat engine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52118146A (en) * | 1976-03-30 | 1977-10-04 | Toshiba Corp | Power plant uses low boiling point medium to working fluid |
-
1977
- 1977-10-11 JP JP12086077A patent/JPS5455256A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02131726A (en) * | 1988-11-11 | 1990-05-21 | Tokyo Electric Co Ltd | vacuum cleaner |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5455256A (en) | 1979-05-02 |
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