200401863 玫、發明說明： 【發明所屬之技術領域】 本發明基本上是有關於發電廠而特別是使用燃氣輪機之 發電廠，而燃氣輪機是以碳氫氣如天然氣或丙烷來啟動。 【先前技術】 用來啟動此設備之該碳氫氣通常以液態形式進入而在使 用前被蒸發。傳統上蒸發的完成是靠燃燒某些燃料或靠吸 收其他熱源來加溫該流體。 燃氣輪機之性能是由一些因子所影響，其一是周圍空氣 壓力。空氣壓力受影響於海拔高度所，氣候造成之氣壓， 以及流經入口輸送管，濾網氣流之壓力損失等等。 燃氣輪機之性能亦受該入口空氣溫度所影響。燃氣輪機 典型上當周圍空氣溫度上升時會產生動力輸出之損失。燃 氣輪機性能可在當運作於ISO狀況之海平面及攝氏15度（華 氏59度）時定義為額定之100 %。即使溫度及性能間之真實關 係產生變化，當入口空氣溫度上升至約攝氏35度C(華氏95 度）時，動力輸出典型上下降ISO額定輸出之80%或85%。另 一方面，當入·口空氣溫度僅攝氏7度C(華氏45度）時，動力輸 出可上升ISO額定輸出之105%，其是一相較於高溫性能有 30%之提升。 當空調設備負荷最大時，電力（電流值）之需求通常在那些 高周圍空氣溫度。公元2000年六月九日第09/591,250號專利 描述一種儲存於一層狀槽中之熱交換流體如何在此設備中 用來冷卻該入口空氣。 83927 200401863 【發明内容】 本發明有效地吸取該冷卻液態碳氫燃料之冷用來冷卻該 被導入一燃氣輪機入口空氣。藉由減低燃燒些許為蒸發之 燃料或減低抵抗些許其他熱源之冷，以及藉由減低一獨立 冷卻源之需來，本發明能使一發電設備之運作更有效並更 經濟。 用來為發電設備燃料之該冷卻液態碳氫燃料是被蒸發於 一蒸發器中用於一熱交換流體。該熱交換流體可以是任一 種類之液體，包括水或一甲醇及水之溶液。在蒸發過程中 ，該熱交換流體被冷卻。一種連接該蒸發器下游侧及上游 侧之重覆循環回路可選擇性地用來重覆循環冷卻熱交換流 體回至該蒸發器作再冷卻。 些許該熱交換流體是週期性導入儲存於一儲存設備。最 好是該熱交換流體儲存成一層狀，該熱交換流體被導入該 儲存設備底層。當該流體需要用來蒸發該液態碳氫燃料， 會由該儲存設備頂層被抽出。 冷卻之熱交換流體被傳遞至連接該燃氣輪機之入口空氣 冷卻器。當冷卻熱交換流體可直接來自蒸發器，或來自該 儲存設備或來自兩者之結合。週期性的用來冷卻該入口空 氣之該熱交換流體可由該儲存設備中冷卻熱交換流體抽出 。在任何時刻，該入口空氣冷卻器冷卻該入口空氣至該燃 氣輪機，而改善該燃氣輪機之效率。 該熱交換流體當其冷卻該入口空氣時增溫。該增溫之熱交 換流體可回至該蒸發器用來蒸發額外之液態燃料。某些增溫 83927 200401863 之熱交換流體可週期性回收儲存。當該熱交換流體儲存成一 層狀，該增溫之熱交換流體會回至該儲存設備頂層，在該蒸 發器需要使用時會由該儲存設備頂層被抽出使用。 【實施方式】 該發電設備在圖1中說明包括一組蒸發器1 〇，一層狀槽形 式之儲存設備12，以及一對入口空氣冷卻器14相對應於一 對燃氣輪機1 6。該燃氣輪機16以一碳氫燃料運作，如天然 氣或丙燒。該燃料是以冷卻，液態以供使用，如液態天然 氣（LNG)或液態石油氣（LPG)。 在其提供該蹲氣輪機1 6使用前，該液態碳氫燃料必須由 液態被蒸發至氣態。該圖示蒸發器10可用來蒸發一冷卻燃 料。蒸發的完成是以置入液態燃料與較高溫之熱交換流體 進行熱接觸未達成，該蒸發器可以是一垂直殼狀及管狀之 熱交換器用來處理流量1 200 m3/hr之熱交換流體。其他種類 及尺寸之熱交換器亦可被使用而其蒸發器之數量可改變。 有多種液體可用為熱交換流體。而在某些狀況時，水可 使用。某些時候，該熱交換流體可以是一包含水及一甲醇 及水之溶液，如一含30%(重量）甲醇及70%(重量）水之溶液 。其他可能是包含一或多個氯化鈉，氯化鈣，醋酸鉀，蟻 酸鉀，硝酸鉀，硝酸鈉，亞硝酸鈉，乙烯乙二醇，丙烯乙 二醇，氨水，或無水氨。當某些時候最好是用單一熱交換 流體於整個系統中，而在其他狀況時最好是用多種熱交換 流體於整個系統之各不同之部分。 在本發明的實例中，該冷卻液態燃料在約-160°C (-260°F ) 83927 200401863 經由液態補給管線20進入該蒸發器1 0。在該蒸發器中，該 冷卻液態燃料被置於用來與相對高溫之熱交換流體作熱接 觸而其是經由高溫流體補給管線22補給。在此狀況，該熱 交換流體於該高溫流體補給管線中之溫度約為20 °C (70 °F ) 。該高溫熱交換流體與該液態燃料之熱接觸使在該熱交換 流體冷卻時蒸發冷卻液態燃料成為氣態燃料。該氣態燃料 經由氣態管線24進入該蒸發器，藉此被導入該燃氣輪機1 6 。該冷卻之熱交換流體經由低狀態補給管線26進入該蒸發 器。在此，該氣態燃料之溫度約為10°C(50°F)，而該冷卻之 熱交換流體之溫度約為〇°C (30°F )。 中間狀態流體管線28可被用來導引冷卻之熱交換流體至 該層狀槽1 2或該入口空氣冷卻器1 4。在某些實例中，該冷 卻之熱交換流體之溫度會較所需溫度高。如此，可能必需 提供一個次要冷卻器來冷卻該熱交換流體使其溫度低於只 靠單次通過該蒸發器10之溫度。一個作再冷卻該熱交換流 體可用之方法是用一個重覆循環之回路如下所示。 該所示之重覆循環之回路包括一蒸發幫浦30及重覆循環 管線32可選择性地用來重覆循環冷卻該熱交換流體回至該 蒸發器之上游側作再冷卻。 在本發明的實例中，該重覆循環管線32包括一分離管線 用於每一蒸發器1 0。每一管線提供一重覆循環閥門44用來 控制至其相對蒸發器之熱交換流體之流動。重覆循環之某 些冷卻熱交換流體回流至該蒸發器作二次冷卻會使在低狀 態補給管線2 6中之冷卻熱交換流體之溫度降低。 83927 200401863 該入口空氣冷卻器14用來利用該冷卻熱交換流體來冷卻 該燃氣輪機1 6使用之入口空氣。舉例來說該空氣冷卻器可 以是鮪片管式熱交換器。該冷卻熱交換流體可以由中間狀 態流體管線28提供。一預備空氣冷卻器（未顯示）可用來該燃 氣輪機入口空氣之冷卻。 在本發明的實例中，周圍空氣經由導管46進入該入口空 氣冷卻器1 6。在某些狀況，該周圍空氣之溫度可能為3 5 °C (95 °F)或更高。這些空氣冷卻器中，該周圍空氣被置於用來 與由中間狀態流體管線28提供之相對的冷卻熱交換流體作 熱接觸。一於該中間狀態流體管線28之空氣冷卻閥門50控 制熱交換流體之流動。該空氣冷卻閥門之型式及位置是可 以變動的。 在該入口空氣冷卻器14中，由該導管46提供之高溫周圍 空氣及由中間狀態流體管線28提供之該冷卻熱交換流體之 熱接觸在加溫熱交換流體中冷卻入口空氣。最好是於一溫 度為5°C(4 5°F)或更低，該冷卻之入口空氣用來經由燃氣輪 機入口 52進入該燃氣輪機16。使用溫度為5°C (45°F )之入口 空氣，而不使用溫度為35°C (95°F)之入口空氣，可增加燃氣 輪機動力輸出30%或更多。 該加溫之熱交換流體經由該回流管線54進入該入口空氣 冷卻器1 4。在本發明的實例中，該加溫之熱交換流體在該 回流管線中興溫度可以約為20°C (70°F)。該回流管線之一支 線導回該南溫流體補給管線2 2。另一支線導回該層狀槽1 2 之頂部。一槽閥門5 6位於該回流管線之該支線控制被導入 83927 -10- 200401863 該層狀槽12之加溫熱交換流體之流量。該槽閥門之刑、 位置是可以變動的。 之式及 不需立即用來冷卻入口空氣之冷卻熱交換 认，礼隨可被細 一冷卻補給管線6 0導至该層狀槽1 2。該冷卻从一 、 調、、、&官缘與誇 層狀槽1 2底邵連通，在此該熱交換流體被儲产、〜 、^ 卞万；一層狀彡 狀態。在莱些狀況中，如一例所示，其可以於访、、 ^ /、 17 1該槽4女 一約為50,000立方公尺至1 00,000立方公尺 > 办曰 曰有 沉中，該槽應與外部隔離並包含頂部及底部配i /心另大 設計用來加強儲存之熱交換流體之熱層化。 ’、、先特別 冷卻，高密度是儲存於該槽1 2底部而古、、四 、 回，皿，低密度是雜 存於該槽1 2頂邵，而造成層狀儲存。杏、、w _ 缉 田酿度低於4。(：（39 為必需時’使用流體而不用靜態水可以菩 ） 疋’、詈的，因 態水之溫度/密度關係使其難於低於這些、、W产 ^ ^ 之狀態。 …、准持1狀 一位於該冷卻補給管線60之儲存閥門62可用 h丨、、入％ 一為4u ^ 水可時 當提 及多少冷卻之熱交換流體被導入該層狀槽〗2。通常 供該燃氣輪機16之入口空氣值或需求為低時，Α 1心 、 q丨一 丁 ~却〈熱交 換流體被送入儲存。傳送冷卻之熱交換流體至該層狀样^ 產生一冷卻之熱交換流體之貯存而其當該冷卻液態燃料之 蒸發無法提供足夠冷卻來冷卻該入口空氣至需要等級時可 被抽出使用。 當需要時，高溫熱交換流體可被從該層狀槽1 2頂部經由 該回泥管線5 4被抽出。如需要，可使用〆幫浦。該鬲溫熱交 換流> 體可被導入蒸發器1 〇用來冷卻，在被冷卻之後再回 充至 83927 -11 - 200401863 該層狀槽12底部。 冷卻之熱交換流體之貯存可由該層狀槽1 2底部經由該入 口空氣冷卻器14經由一附加補給管線64導引由該槽底部至 該中間狀態流體管線28。一位於該附加補給管線64之次要 閥門66可用來控制何時及多少冷卻之熱交換流體由該層狀 槽12被抽出。一次要幫浦68最好是安排於該附加補給管線 上以提供所需壓力使冷卻之熱交換流體由儲存被抽出。該 次要閩門及次要幫浦之型式及位置是可以變動的。 此詳細敘述已在此提供以為例子，並不為本發明之限制 。本發明之全_如下所申請。 【圖式簡單說明】 本發明可按附圖而能更清楚的被瞭解，圖中： 圖1是依據本發明一實例之發電設備之概要圖。 【圖式代表符號說明】 10 蒸 發 器 12 層 狀槽 形 式 之 儲存設備 14 一 對 入 口 空 氣 冷卻器 16 一 對 燃 氣 輪 機 20 液 態 補 給 管 線 22 溫 流 ft 補 給 管線 24 氣 態 管 線 26 低狀 態 補 給 管 線 83927 -12-200401863 Description of the invention: [Technical field to which the invention belongs] The present invention basically relates to a power plant, particularly a power plant using a gas turbine, and the gas turbine is started with carbon hydrogen such as natural gas or propane. [Prior art] The carbon and hydrogen used to start the device usually enter in liquid form and are evaporated before use. Traditionally, evaporation is accomplished by burning certain fuels or by absorbing other heat sources to warm the fluid. The performance of a gas turbine is affected by several factors. One is the ambient air pressure. Air pressure is affected by altitude, air pressure caused by climate, and pressure loss of air flow through inlet ducts, filters, etc. The performance of the gas turbine is also affected by the inlet air temperature. Gas turbines typically lose power output when the ambient air temperature rises. Gas turbine performance can be defined as 100% of rated when operating at ISO-level sea level and 15 degrees Celsius (59 degrees Fahrenheit). Even if the true relationship between temperature and performance changes, when the inlet air temperature rises to about 35 ° C (95 ° F), the power output typically decreases by 80% or 85% of the ISO rated output. On the other hand, when the inlet and outlet air temperature is only 7 ° C (45 ° F), the power output can increase by 105% of the ISO rated output, which is a 30% improvement over high-temperature performance. When the air conditioning equipment is at its maximum load, the demand for electricity (current value) is usually those with high ambient air temperature. Patent No. 09 / 591,250 of June 9, 2000 describes how a heat exchange fluid stored in a layered tank can be used in this device to cool the inlet air. 83927 200401863 [Summary of the Invention] The present invention effectively absorbs the cold of the cooled liquid hydrocarbon fuel to cool the air introduced into a gas turbine inlet. By reducing the burning of slightly evaporated fuel or reducing the cold resistance of some other heat sources, and by reducing the need for an independent cooling source, the present invention enables a power plant to operate more efficiently and economically. The cooled liquid hydrocarbon fuel used to fuel power generation equipment is evaporated in an evaporator for a heat exchange fluid. The heat exchange fluid may be any kind of liquid, including water or a solution of methanol and water. During the evaporation process, the heat exchange fluid is cooled. A repeating circulation circuit connecting the downstream and upstream sides of the evaporator can be selectively used to repeat the circulating cooling heat exchange fluid back to the evaporator for re-cooling. Some of the heat exchange fluid is periodically introduced into a storage device. Preferably, the heat exchange fluid is stored in a layer, and the heat exchange fluid is introduced into the bottom layer of the storage device. When the fluid is needed to evaporate the liquid hydrocarbon fuel, it is pumped from the top layer of the storage device. The cooled heat exchange fluid is transferred to an inlet air cooler connected to the gas turbine. When cooling the heat exchange fluid can come directly from the evaporator, or from the storage device or from a combination of the two. The heat exchange fluid periodically used to cool the inlet air may be extracted by the cooling heat exchange fluid in the storage device. At any time, the inlet air cooler cools the inlet air to the gas turbine and improves the efficiency of the gas turbine. The heat exchange fluid warms as it cools the inlet air. The warmed heat exchange fluid can be returned to the evaporator to evaporate additional liquid fuel. Some heat exchange fluids that warm up 83927 200401863 can be recovered and stored periodically. When the heat exchange fluid is stored in a layer, the warmed heat exchange fluid will return to the top layer of the storage device, and the vaporizer will be withdrawn from the top layer of the storage device when it is needed. [Embodiment] The power generation equipment illustrated in FIG. 1 includes a group of evaporators 10, a storage device 12 in the form of a single-layer trough, and a pair of inlet air coolers 14 corresponding to a pair of gas turbines 16. The gas turbine 16 operates on a hydrocarbon fuel, such as natural gas or propylene. The fuel is available in a cooled, liquid state, such as liquid natural gas (LNG) or liquid petroleum gas (LPG). The liquid hydrocarbon fuel must be evaporated from a liquid state to a gas state before it is used by the squatting turbine 16. The illustrated evaporator 10 can be used to evaporate a cooling fuel. The completion of evaporation is not achieved by placing liquid fuel in thermal contact with a higher-temperature heat exchange fluid. The evaporator can be a vertical shell-shaped and tubular heat exchanger for processing heat exchange fluid with a flow rate of 1 200 m3 / hr. Other types and sizes of heat exchangers can also be used and the number of evaporators can be changed. A variety of liquids can be used as the heat exchange fluid. In some cases, water can be used. In some cases, the heat exchange fluid may be a solution containing water and a methanol and water, such as a solution containing 30% by weight of methanol and 70% by weight of water. Others may include one or more of sodium chloride, calcium chloride, potassium acetate, potassium formate, potassium nitrate, sodium nitrate, sodium nitrite, ethylene glycol, propylene glycol, ammonia, or anhydrous ammonia. In some cases it is best to use a single heat exchange fluid throughout the system, while in other situations it is better to use multiple heat exchange fluids in different parts of the overall system. In the example of the present invention, the cooled liquid fuel enters the evaporator 10 via a liquid supply line 20 at about -160 ° C (-260 ° F) 83927 200401863. In the evaporator, the cooled liquid fuel is placed in thermal contact with a relatively high temperature heat exchange fluid and is replenished via a high temperature fluid supply line 22. In this case, the temperature of the heat exchange fluid in the high temperature fluid supply line is about 20 ° C (70 ° F). The thermal contact of the high temperature heat exchange fluid with the liquid fuel causes the liquid fuel to evaporate to cool the gaseous fuel when the heat exchange fluid is cooled. The gaseous fuel enters the evaporator via a gaseous line 24, thereby being introduced into the gas turbine 16. The cooled heat exchange fluid enters the evaporator via the low-state makeup line 26. Here, the temperature of the gaseous fuel is about 10 ° C (50 ° F), and the temperature of the cooled heat exchange fluid is about 0 ° C (30 ° F). The intermediate state fluid line 28 may be used to direct the cooled heat exchange fluid to the laminar tank 12 or the inlet air cooler 14. In some instances, the temperature of the cooled heat exchange fluid will be higher than the desired temperature. As such, it may be necessary to provide a secondary cooler to cool the heat-exchange fluid to a temperature below that of the evaporator 10 by a single pass. A useful method for recooling the heat exchange fluid is to use a repeating circuit as shown below. The illustrated repeat cycle circuit includes an evaporation pump 30 and a repeat cycle line 32 that can be selectively used to repeatedly cycle the heat exchange fluid back to the upstream side of the evaporator for recooling. In the example of the present invention, the repeating circulation line 32 includes a separation line for each evaporator 10. Each line is provided with a repeat cycle valve 44 for controlling the flow of heat exchange fluid to its opposite evaporator. Certain cooling and heat exchange fluids which are repeatedly circulated back to the evaporator for secondary cooling will reduce the temperature of the cooling heat exchange fluid in the low-state supply line 26. 83927 200401863 The inlet air cooler 14 is used to cool the inlet air used by the gas turbine 16 using the cooling heat exchange fluid. The air cooler may be, for example, a finned tube heat exchanger. The cooling heat exchange fluid may be provided by an intermediate state fluid line 28. A preliminary air cooler (not shown) can be used to cool the air at the gas turbine inlet. In the example of the invention, ambient air enters the inlet air cooler 16 via a duct 46. In some conditions, the temperature of the surrounding air may be 3 5 ° C (95 ° F) or higher. In these air coolers, the ambient air is placed in thermal contact with the opposite cooling heat exchange fluid provided by the intermediate state fluid line 28. An air cooling valve 50 in the intermediate state fluid line 28 controls the flow of the heat exchange fluid. The type and position of the air cooling valve can be changed. In the inlet air cooler 14, the thermal contact between the high-temperature ambient air provided by the duct 46 and the cooling heat exchange fluid provided by the intermediate state fluid line 28 cools the inlet air in the warming heat exchange fluid. Preferably at a temperature of 5 ° C (45 ° F) or lower, the cooled inlet air is used to enter the gas turbine 16 through the gas turbine inlet 52. Using inlet air at a temperature of 5 ° C (45 ° F) instead of using inlet air at a temperature of 35 ° C (95 ° F) can increase the power output of a gas turbine by 30% or more. The warmed heat exchange fluid enters the inlet air cooler 14 through the return line 54. In the example of the present invention, the temperature of the heated heat exchange fluid in the return line may be about 20 ° C (70 ° F). One branch of the return line leads back to the south temperature fluid supply line 22. The other branch leads back to the top of the layered groove 12. A branch valve 56 is located in the branch line of the return line to control the flow of the heated heat exchange fluid introduced into the layered tank 12 83927 -10- 200401863. The position and position of the slot valve can be changed. This type and cooling heat exchange does not need to be used immediately to cool the inlet air. It can be guided to the layered tank 12 by a cooling supply line 60. The cooling is connected to the bottom layer of the layered groove 12 from the center of the channel, and the heat exchange fluid is stored and produced in a layered state. In some cases, as shown in an example, it can be visited, ^ /, 17 1 The slot 4 female one is about 50,000 cubic meters to 1 00,000 cubic meters > There is Shen Zhong, the slot It should be isolated from the outside and include top and bottom cores and a large core designed to enhance the thermal stratification of the stored heat exchange fluid. First, it is specially cooled, high density is stored in the bottom of the tank 12 and ancient, four, and back, and low density is stored in the top of the tank 12, resulting in layered storage. The apricot, w _ field fermenting degree is lower than 4. (: (39 is necessary if you can use a fluid without static water) 必需 ', 詈, because of the temperature / density relationship of the state water, it is difficult to lower than these, W, ^ ^.…, Quasi-hold The storage valve 62 located in the cooling supply line 60 can be used. The amount is 4u. When water is available, how much cooling heat exchange fluid is referred to the layered tank. 2. It is usually provided for the gas turbine 16 When the inlet air value or demand is low, Α 1 center, q 丨 一 丁 ~ but the heat exchange fluid is sent to storage. The cooled heat exchange fluid is transferred to the layered sample ^ Generates a cooled heat exchange fluid for storage And when the evaporation of the cooled liquid fuel does not provide sufficient cooling to cool the inlet air to the required level, it can be drawn out for use. When needed, high temperature heat exchange fluid can be passed from the top of the layered tank 12 through the return mud Pipeline 5 4 is drawn out. If necessary, the pump can be used. The temperature-heat exchange stream can be introduced into the evaporator 10 for cooling, and after being cooled, it can be recharged to 83927 -11-200401863. Bottom of the trough 12. Cooling heat transfer Fluid storage can be guided from the bottom of the layered tank 12 through the inlet air cooler 14 via an additional supply line 64 from the bottom of the tank to the intermediate state fluid line 28. A secondary valve 66 located on the additional supply line 64 It can be used to control when and how much cooled heat exchange fluid is withdrawn from the layered tank 12. The primary pump 68 is preferably arranged on the additional supply line to provide the required pressure to allow the cooled heat exchange fluid to be withdrawn from storage. The type and position of the secondary Minmen and the secondary pumps can be changed. This detailed description has been provided here as an example and is not a limitation of the present invention. The full scope of the present invention is as follows. [Schematic Brief description] The present invention can be understood more clearly according to the drawings. Figure 1 is a schematic diagram of a power generating device according to an example of the present invention. [Description of Representative Symbols of the Drawings] 10 Evaporator 12 Layered groove Storage equipment 14 a pair of inlet air coolers 16 a pair of gas turbines 20 liquid supply lines 22 warm flow ft supply lines 24 gaseous lines 26 Low status supply line 83927 -12-