TWI507643B - Regenerative air preheater design to reduce cold end fouling - Google Patents
Regenerative air preheater design to reduce cold end fouling Download PDFInfo
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- TWI507643B TWI507643B TW100120581A TW100120581A TWI507643B TW I507643 B TWI507643 B TW I507643B TW 100120581 A TW100120581 A TW 100120581A TW 100120581 A TW100120581 A TW 100120581A TW I507643 B TWI507643 B TW I507643B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
- F28D19/041—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier with axial flow through the intermediate heat-transfer medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/006—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus specially adapted for regenerative heat-exchange apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
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Description
本發明大致上係關於一種具有一化石燃料燃燒鍋爐及一再生型空氣預熱器之蒸氣產生系統。更具體而言,本發明係關於具有一化石燃料燃燒鍋爐及一在各種鍋爐操作位準期間展現經減少積垢之旋轉式再生型空氣預熱器之蒸氣產生系統。The present invention generally relates to a vapor generation system having a fossil fuel combustion boiler and a regenerative air preheater. More specifically, the present invention relates to a vapor generation system having a fossil fuel fired boiler and a rotary regenerative air preheater exhibiting reduced fouling during various boiler operating levels.
在鍋爐之燃燒過程中,燃料中之硫被氧化成SO2 。在燃燒過程之後,一些量之SO2 被進一步氧化成SO3 ,且一般約1%至2%之量級之SO2 將成為SO3 。氧化鐵、釩及其他金屬存在於合適的溫度範圍下可產生此氧化作用。選擇性催化還原(SCR)亦廣為人知係將該煙道氣中之一部分SO2 氧化成SO3 。催化劑配方(主要是催化劑中釩的量)影響氧化物之量,且氧化物比率為自0.5%至超過1.5%。更典型為約1%。因此,用新的SCR燃燒高硫煤之發電廠可觀察到SO3 之排放大量增加,此將產生可見之煙流、局部酸性地面位準問題及其他環境問題。During the combustion of the boiler, the sulfur in the fuel is oxidized to SO 2 . After the combustion process, some amount of SO 2 is further oxidized to SO 3 , and typically about 2% to 2% of SO 2 will become SO 3 . Iron oxide, vanadium and other metals are present at a suitable temperature range to produce this oxidation. Selective catalytic reduction (SCR) is also well known to oxidize a portion of the SO 2 in the flue gas to SO 3 . The catalyst formulation (primarily the amount of vanadium in the catalyst) affects the amount of oxide and the oxide ratio is from 0.5% to over 1.5%. More typically about 1%. As a result, a significant increase in SO 3 emissions can be observed in power plants that burn high-sulfur coal with new SCRs, which can result in visible smoke, local acid ground level problems, and other environmental issues.
旋轉式再生型熱交換器普通用於大型化石燃料燃燒鍋爐上,以將熱自熱的煙道氣轉移至提供至該鍋爐之一燃燒室之較冷輸入空氣。此類型之熱交換器一般被稱為空氣預熱器。使用空氣預熱器之目的在於增加化石燃料燃燒鍋爐之效率。基本上,旋轉式再生型空氣預熱器係由一大型圓柱體組成,該圓柱體封裝有複數個隔開之金屬片。該等片彼此分離,以允許熱的煙道氣流過每個板之平行於該圓柱體之軸之表面,從而加熱該等片。該等熱片被旋轉至較冷之輸入空氣流,以加熱該輸入空氣。該等煙道氣及輸入空氣通常在相對之方向上流經該空氣預熱器。整個圓柱體圍繞其軸而持續地旋轉,使得該熱氣及冷空氣流交替地流過相同之金屬片。Rotary regenerative heat exchangers are commonly used on large fossil fuel fired boilers to transfer hot self-heating flue gas to cooler input air provided to one of the boiler's combustion chambers. This type of heat exchanger is generally referred to as an air preheater. The purpose of using an air preheater is to increase the efficiency of a fossil fuel fired boiler. Basically, a rotary regenerative air preheater consists of a large cylinder encased with a plurality of spaced apart metal sheets. The sheets are separated from each other to allow a hot flue gas stream to pass over the surface of each of the plates parallel to the axis of the cylinder to heat the sheets. The hot sheets are rotated to a cooler input air stream to heat the input air. The flue gases and input air generally flow through the air preheater in opposite directions. The entire cylinder is continuously rotated about its axis such that the hot and cold air flows alternately through the same metal sheet.
化石燃料的燃燒之產物通常包含三氧化硫(SO3 )及水蒸氣(H2 O)二者,因此,當廢氣在該空氣預熱器內被冷卻至足夠之程度,則SO3 與水蒸氣組合且凝結成液體硫酸(H2 SO4 )。此發生於當表面(諸如一空氣預熱器之熱交換元件)之溫度低於硫酸之露點時。當灰粒及硫酸兩者沈積於該空氣預熱器中之金屬表面上時,其等黏結至該等金屬表面且造成被稱為積垢之現象。由於積垢會限制流經該空氣預熱器之空氣及氣體之量,因此會導致該空氣預熱器之效率降低。The product of the combustion of fossil fuels usually contains both sulfur trioxide (SO 3 ) and water vapor (H 2 O), so when the exhaust gas is cooled to a sufficient extent in the air preheater, SO 3 and water vapor Combined and condensed into liquid sulfuric acid (H 2 SO 4 ). This occurs when the temperature of the surface (such as the heat exchange element of an air preheater) is below the dew point of sulfuric acid. When both the ash particles and the sulphuric acid are deposited on the metal surface in the air preheater, they are bonded to the metal surfaces and cause a phenomenon called scale. Since fouling limits the amount of air and gas flowing through the air preheater, the efficiency of the air preheater is reduced.
高速度蒸氣噴流或空氣噴流被週期性地導向該等金屬表面,以在被稱為吹灰之過程中移除灰塵/酸沈積物。吹灰自該等金屬片移除一些而並非所有沈積物。High velocity vapor jets or air jets are periodically directed to the metal surfaces to remove dust/acid deposits during what is known as sootblowing. Soot blowing removes some but not all deposits from the metal sheets.
再生型空氣預熱器之冷端通常係處於低於該煙道氣中之H2 SO4 之露點,從而使得一部分H2 SO4 冷凝在該等熱交換元件之表面上。隨著所冷凝之灰塵及H2 SO4 聚集,其等造成在穿過該熱交換器100之流中建立一壓力降。由於來自燃料之燃燒之諸如灰塵及其他固態材料之固體亦聚集在該等熱交換元件上,該壓力降隨著時間經過將變得更大。若積垢已足夠嚴重,則金屬片之間之流動通道可能被堵塞。在此情形下,損失了熱轉移表面積且風扇可能無法移動必要量之燃燒空氣通過該空氣預熱器。The cold end of the regenerative air preheater is generally in line 2 SO below the dew point of the flue gas of H 4, so that a portion of the condensed H 2 SO 4 in such heat exchange surface of the element. As the condensed dust and H 2 SO 4 aggregate, it causes a pressure drop to build up in the flow through the heat exchanger 100. Since solids such as dust and other solid materials from the combustion of the fuel also accumulate on the heat exchange elements, the pressure drop will become greater over time. If the fouling is sufficiently severe, the flow path between the metal sheets may be blocked. In this case, the heat transfer surface area is lost and the fan may not be able to move the necessary amount of combustion air through the air preheater.
空氣預熱器之冷端由於較低氣體溫度之一本質而具有較高之氣體密度且因此較低之流速。一般而言,該冷端流速為熱端流速之僅約60%。較低之氣體流速亦導致更多之積垢。The cold end of the air preheater has a higher gas density and therefore a lower flow rate due to one of the lower gas temperatures. In general, the cold end flow rate is only about 60% of the hot end flow rate. Lower gas flow rates also result in more fouling.
亦存在其他增加積垢之因素,諸如低鍋爐負載。低鍋爐負載造成該速度降低至可能低至熱端最大持續額定(MCR)之25%。There are also other factors that increase fouling, such as low boiler loads. The low boiler load causes this speed to drop to as low as 25% of the hot end maximum continuous rating (MCR).
當前需要一種能夠在各種燃燒條件下抵抗積垢之空氣預熱器。There is a need for an air preheater that is resistant to fouling under a variety of combustion conditions.
簡而言之,本發明之一較佳形式為在各種鍋爐負載下更能抵抗「積垢(fouling)」之空氣預熱器。Briefly, one preferred form of the invention is an air preheater that is more resistant to "fouling" under various boiler loads.
本發明之一目的在於提供一種更能抵抗腐蝕之空氣預熱器。It is an object of the present invention to provide an air preheater that is more resistant to corrosion.
本發明之一目的在於提供一種可對於各種鍋爐負載調整之空氣預熱器。It is an object of the present invention to provide an air preheater that can be adjusted for various boiler loads.
本發明之一目的在於提供一種可在各種鍋爐負載下調整煙道氣速度之空氣預熱器。It is an object of the present invention to provide an air preheater that can adjust the flue gas velocity under various boiler loads.
自下文之圖及說明書中,本發明之其他目的及優點將可顯而易見。Other objects and advantages of the invention will be apparent from the description and drawings.
熟悉此項技術者可藉由參考附圖而更加理解本發明且本發明之多個目的及優點亦將顯而易見。The invention will be more fully understood and appreciated by the appended claims appended claims.
大多數蒸氣產生系統利用靜態或旋轉式再生型空氣預熱器來增加鍋爐效率。最常見的為旋轉式再生型空氣預熱器。此類型之空氣預熱器之特徵在於旋轉熱交換元件。本發明係關於裝配有任一類型之再生型空氣預熱器之鍋爐系統。為了促進論述,將結合一旋轉式再生型空氣預熱器來論述本發明之配置。Most steam generation systems utilize static or rotary regenerative air preheaters to increase boiler efficiency. The most common type is a rotary regenerative air preheater. This type of air preheater is characterized by a rotating heat exchange element. This invention relates to a boiler system equipped with any type of regenerative air preheater. To facilitate the discussion, the configuration of the present invention will be discussed in connection with a rotary regenerative air preheater.
參考諸圖式之圖1,顯示的係一習知之旋轉式可再生預熱器100。該空氣預熱器100具有一轉子112,其係可旋轉地安裝於一殼體114中。該轉子112係由自一轉子柱118延伸至該轉子112之外周邊之隔膜或隔板116而形成。隔板116於其間界定隔室120,該等隔室20係用於包含熱交換元件籃架總成122。Referring to Figure 1 of the drawings, a conventional rotary regenerative preheater 100 is shown. The air preheater 100 has a rotor 112 that is rotatably mounted in a housing 114. The rotor 112 is formed by a diaphragm or partition 116 extending from a rotor post 118 to a periphery of the rotor 112. The partition 116 defines a compartment 120 therebetween for securing the heat exchange element basket assembly 122.
在一典型之旋轉式再生型熱交換器100中,煙道氣流224及燃燒空氣入口流230自相對之端進入該轉子112中且在相對之方向上越過容納於該熱交換元件籃架總成122內之熱交換元件142。因此,冷空氣入口130及經冷卻煙道氣出口126係位於該熱交換器之一端,該端被稱為冷端144,且熱煙道氣入口124及經加熱空氣出口132係位於該空氣預熱器100之相對端,該端被稱為熱端146。區段板136延伸跨過該殼體114,鄰接該轉子112之上面及下面。區段板136將該空氣預熱器100分割成一空氣區段138及一煙道氣區段140。In a typical rotary regenerative heat exchanger 100, a flue gas stream 224 and a combustion air inlet stream 230 enter the rotor 112 from opposite ends and are disposed in opposite directions over the heat exchange element basket assembly. Heat exchange element 142 within 122. Thus, the cold air inlet 130 and the cooled flue gas outlet 126 are located at one end of the heat exchanger, the end being referred to as the cold end 144, and the hot flue gas inlet 124 and the heated air outlet 132 are located in the air pre- The opposite end of the heater 100, which is referred to as the hot end 146. Segment plate 136 extends across the housing 114 adjacent the upper and lower faces of the rotor 112. Segment plate 136 divides air preheater 100 into an air section 138 and a flue gas section 140.
圖1之箭頭指示穿過該轉子112之煙道氣流224及空氣流230之方向。通過該煙道氣入口124而進入之該煙道氣流224將熱轉移至安裝於定位在該煙道氣區段140中的該等隔室120中之熱交換元件籃架總成122中之熱交換元件142。經加熱之熱交換元件142接著被旋轉至該空氣預熱器100之空氣區段138。該等熱交換元件籃架總成122所儲存之熱接著被轉移至通過該空氣入口130而進入之空氣流230。冷煙道氣出口流226穿過煙道氣出口126而退出該預熱器100且該經加熱之空氣出口流232穿過空氣出口132而退出該預熱器100。The arrows of FIG. 1 indicate the direction of flue gas flow 224 and air flow 230 through the rotor 112. The flue gas stream 224 entering through the flue gas inlet 124 transfers heat to the heat in the heat exchange element basket assembly 122 mounted in the compartments 120 positioned in the flue gas section 140. Exchange element 142. The heated heat exchange element 142 is then rotated to the air section 138 of the air preheater 100. The heat stored by the heat exchange element basket assembly 122 is then transferred to the air stream 230 entering through the air inlet 130. The cold flue gas outlet stream 226 exits the preheater 100 through the flue gas outlet 126 and exits the preheater 100 through the heated air outlet stream 232.
如上所述,該空氣預熱器100之冷端144之額外酸積垢使得橫跨該空氣預熱器100建立一較大的壓力降。承載於該煙道氣中之顆粒物質亦隨著時間經過而聚集在該等熱交換元件142之表面上,且此等沈積物之存在會增加該空氣預熱器之壓力降。此顆粒物質趨向於主要在具有低流速之局部區域中聚集。As noted above, the additional acid build-up of the cold end 144 of the air preheater 100 creates a large pressure drop across the air preheater 100. The particulate matter carried in the flue gas also accumulates on the surface of the heat exchange elements 142 over time, and the presence of such deposits increases the pressure drop of the air preheater. This particulate matter tends to concentrate primarily in localized areas with low flow rates.
因此,積垢係歸因於兩個問題:(1)聚集飛灰及其他顆粒之酸之凝結;及(2)具有低流速之區域在低鍋爐負載下速度變得更低。Therefore, fouling is attributed to two problems: (1) condensation of acid that collects fly ash and other particles; and (2) areas with low flow rates become lower at low boiler loads.
已試圖用各種不同的方式克服各個問題。一種裝置用於僅部分阻擋該煙道氣入口。此裝置之效果令人失望。當時未有認識到且解決導致積垢之所有因素。Attempts have been made to overcome various problems in a variety of different ways. A device is used to only partially block the flue gas inlet. The effect of this device is disappointing. At that time, it did not recognize and solve all the factors that caused the scale.
本發明解決酸凝結問題及與速度相關之積垢問題。高速度顆粒流在類似於噴砂之一過程中會侵蝕固態材料。侵蝕 之速率與經增加至1乘冪以上之速度成比例。吾人的經驗是,飛灰侵蝕與經增大至3.4乘冪之流速成比例。The present invention addresses acid condensation problems and speed-related fouling problems. High velocity particle streams erode solid materials during one of the processes similar to sand blasting. erosion The rate is proportional to the rate of increase to more than one power. My experience is that fly ash erosion is proportional to the flow rate that increases to 3.4 volts.
因此,有益的是增加該氣體區段中之流速,以減少該等熱交換元件142上之沈積量。增加該空氣區段中之流速並不有利地輔助移除沈積物,因為該氣體區段中之顆粒物質很少或者不存在。然而,減少該氣體區段中之熱轉移表面之量的確有作用於升高該氣體區段中之氣體溫度,此導致酸凝結物較少且因此積垢較少。Therefore, it is beneficial to increase the flow rate in the gas section to reduce the amount of deposition on the heat exchange elements 142. Increasing the flow rate in the air section does not advantageously assist in the removal of deposits because there is little or no particulate matter in the gas section. However, reducing the amount of heat transfer surface in the gas section does have an effect on raising the temperature of the gas in the gas section, which results in less acid condensate and therefore less fouling.
進入該鍋爐中之空氣流係與該鍋爐之操作位準有關。因此,在其最大持續額定(MCR)之60%處運行之鍋爐較在MCR之90%處運行之相同鍋爐將需要且花費減少之燃燒空氣。因此,在60%MCR處運行之鍋爐較在90%MCR處運行之鍋爐排出之煙道氣少。通過相同截面而退出之具有大約相同密度之煙道氣之量越少,則其退出速度越低。The air flow entering the boiler is related to the operating level of the boiler. Therefore, a boiler operating at 60% of its maximum continuous rating (MCR) would require and consume less combustion air than the same boiler operating at 90% of the MCR. Therefore, boilers operating at 60% MCR have less flue gas than boilers operating at 90% MCR. The less the amount of flue gas having about the same density exiting through the same cross section, the lower the exit velocity.
同時,當該鍋爐在60%MCR處相對於90%MCR處運行時,其產生退出溫度較低之煙道氣。因此,鍋爐操作位準影響進入該鍋爐之輸入空氣速度、退出該鍋爐之排出煙道氣流速及退出煙道氣之溫度。At the same time, when the boiler is operated at 60% MCR relative to 90% MCR, it produces a flue gas that exits the lower temperature. Therefore, the boiler operating level affects the input air velocity entering the boiler, the exit flue gas flow rate exiting the boiler, and the temperature exiting the flue gas.
參考圖2,本發明包含緊鄰該空氣預熱器100入口處之擋板總成152、162。此等係經附接得盡可能鄰近,以最小化該擋板總成152、162與該空氣預熱器100之間之洩漏。在減小之鍋爐負載條件期間,可使用一控制器158來部分閉合擋板總成152、162。此有效地減小流動面積且因此增加流速。Referring to Figure 2, the present invention includes baffle assemblies 152, 162 adjacent the inlet of the air preheater 100. These are attached as close as possible to minimize leakage between the baffle assemblies 152, 162 and the air preheater 100. A controller 158 can be used to partially close the baffle assemblies 152, 162 during reduced boiler load conditions. This effectively reduces the flow area and thus increases the flow rate.
藉由限制進入該空氣預熱器之煙道氣入口124及空氣入口130二者中之流,用於熱轉移之有效面積較小將導致較少熱交換。此造成該等金屬表面之更大一部分具有高於硫酸露點之溫度,從而減少該等金屬表面之積垢。同時,該氣體區段中之流率增大,其促進任何聚集沈積物之侵蝕。By limiting the flow into both the flue gas inlet 124 and the air inlet 130 of the air preheater, a smaller effective area for heat transfer will result in less heat exchange. This causes a greater portion of the metal surface to have a temperature above the dew point of the sulfuric acid, thereby reducing fouling of the metal surfaces. At the same time, the flow rate in the gas section increases, which promotes erosion of any aggregated deposits.
此外,若流入該空氣預熱器中之冷空氣係藉由另一熱交換器而加熱以保持金屬溫度高於該酸露點,則阻擋該空氣預熱器100之空氣側及煙道氣側兩者之流、需要來自其他熱交換器之熱量將減少。此將節約總體能量,因為阻擋該空氣側上之金屬表面之一部分需要之能量較加熱該冷空氣至一充分程度所需要之能量之量係小至可以忽略。In addition, if the cold air flowing into the air preheater is heated by another heat exchanger to keep the metal temperature higher than the acid dew point, the air side and the flue gas side of the air preheater 100 are blocked. The flow of heat from the other heat exchangers will be reduced. This will save overall energy because the amount of energy required to block a portion of the metal surface on the air side is less than negligible than the amount of energy required to heat the cold air to a sufficient extent.
圖2係具有根據本發明之再生型空氣預熱器配置之蒸氣產生系統之示意圖。該系統包含定位於熱煙道氣入口124內側之一煙道擋板總成152,其係盡可能鄰近該等元件籃架總成122之面。一煙道氣導管154將該鍋爐148連接至該空氣預熱器100。該煙道氣擋板總成152之擋板(圖3中之156)係可在減少之負載條件下閉合,以有效地減小該煙道氣入口124之流動面積。此增加流過該等熱交換元件142之煙道氣之速度。此亦減少用於將熱自該煙道氣轉移之有效表面積。2 is a schematic illustration of a vapor generation system having a regenerative air preheater configuration in accordance with the present invention. The system includes a flue baffle assembly 152 positioned inside the hot flue gas inlet 124 as close as possible to the face of the component basket assembly 122. A flue gas duct 154 connects the boiler 148 to the air preheater 100. The baffle of the flue gas baffle assembly 152 (156 of Figure 3) can be closed under reduced load conditions to effectively reduce the flow area of the flue gas inlet 124. This increases the velocity of the flue gas flowing through the heat exchange elements 142. This also reduces the effective surface area used to transfer heat from the flue gas.
該系統亦包含定位於該預熱器冷空氣入口130處之一空氣擋板總成162,其盡可能鄰近該籃架總成122中之元件之面,以盡可能最小化空氣洩漏。空氣擋板總成162係可在鍋爐148之減少之負載條件下部分閉合,以有效地 減小該空氣入口130之流動面積且因此減小用於將熱轉移至流動進入該空氣預熱器100中之空氣之有效表面積。此意即該預熱器100之冷端(圖1之144)之冷卻減少。The system also includes an air baffle assembly 162 positioned at the preheater cold air inlet 130 as close as possible to the face of the components in the basket assembly 122 to minimize air leakage. The air baffle assembly 162 can be partially closed under reduced load conditions of the boiler 148 to effectively The flow area of the air inlet 130 is reduced and thus the effective surface area for transferring heat to the air flowing into the air preheater 100 is reduced. This means that the cooling of the cold end of the preheater 100 (144 of Figure 1) is reduced.
歸因於該煙道氣區段(圖1之140)之增加之流速,則承載於煙道氣中之飛灰侵蝕該空氣預熱器100中之熱交換元件142之表面上之沈積物。侵蝕速率係與經提升至針對侵蝕劑特定之乘冪的速度成比例。對於飛灰,此乘冪為3.4。The fly ash carried in the flue gas erodes the deposit on the surface of the heat exchange element 142 in the air preheater 100 due to the increased flow rate of the flue gas section (140 of Figure 1). The rate of erosion is proportional to the speed that is raised to the specific power of the etchant. For fly ash, this power is 3.4.
另外,由於用於自該等煙道氣提取熱之表面積減小,則穿過該空氣預熱器而到達該冷端之煙道氣係較熱且因此該冷端中之板之一較大百分率係保持於高於H2 SO4 露點。此導致較少的H2 SO4 凝結在該等熱交換元件(圖1之142)。Additionally, since the surface area used to extract heat from the flue gases is reduced, the flue gas passing through the air preheater to the cold end is hotter and thus one of the plates in the cold end is larger The percentage is maintained above the H 2 SO 4 dew point. This results in less H 2 SO 4 condensing on the heat exchange elements (142 of Figure 1).
控制器158(較佳為具有預程式控制邏輯之可程式邏輯控制器(PLC))監測該鍋爐148之負載且控制該等擋板總成152、162中之擋板葉片之致動。A controller 158, preferably a programmable logic controller (PLC) having pre-program control logic, monitors the load of the boiler 148 and controls actuation of the baffle blades in the baffle assemblies 152,162.
在一較佳實施例中,該控制器158接收來自發電廠分佈式控制系統(DCS)160之一信號。該DCS 160可基於所監測之參數而決定該鍋爐148之操作負載,且係可經程式化而將指示該鍋爐負載之一信號發送至該控制器158。在接收到該信號之後,該控制器158將計算該鍋爐負載且據此致動該等擋板總成152、162。In a preferred embodiment, the controller 158 receives a signal from a power plant distributed control system (DCS) 160. The DCS 160 can determine the operational load of the boiler 148 based on the monitored parameters and can be programmed to send a signal indicative of the boiler load to the controller 158. Upon receiving the signal, the controller 158 will calculate the boiler load and actuate the baffle assemblies 152, 162 accordingly.
現在交替地參考圖1及圖2,可監測該空氣預熱器內之多個位置處之溫度。若該煙道氣區段140內之任何結構(之溫度)下跌至低於該煙道氣內之各種酸之露點,則液體酸凝結在此等結構上。液體酸聚集且固持飛灰加速該空氣預熱 器之積垢之飛塵。通常,該煙道氣出口126具有該煙道氣區段140之最低溫度且最傾向於酸凝結。因此,該控制器158將接收溫度讀數且決定是否較之增加煙道氣流率時應更閉合煙道氣入口,從而減小該交換元件142之曝露至該等煙道氣之表面積。增加之煙道氣速度及減小之熱交換器表面積之組合減小自該等煙道氣取得之熱量,從而升高退出該空氣預熱器100之煙道氣流226之溫度。Referring now alternately to Figures 1 and 2, the temperature at a plurality of locations within the air preheater can be monitored. If any structure (temperature) within the flue gas section 140 falls below the dew point of the various acids in the flue gas, the liquid acid condenses on the structures. The liquid acid accumulates and holds the fly ash to accelerate the air preheating The dust of the scale of the device. Typically, the flue gas outlet 126 has the lowest temperature of the flue gas section 140 and is most prone to acid condensation. Accordingly, the controller 158 will receive the temperature reading and determine if the flue gas inlet should be closed more than the flue gas flow rate, thereby reducing the surface area of the exchange element 142 that is exposed to the flue gases. The combination of increased flue gas velocity and reduced heat exchanger surface area reduces the heat taken from the flue gases, thereby increasing the temperature of the flue gas stream 226 exiting the air preheater 100.
類似地,當該空氣擋板總成162更閉合該空氣入口130時,該入口空氣流230之速度增加。在更閉合該空氣入口130亦減小該等熱交換元件142之曝露至該空氣入口流230之表面積。此導致由該空氣入口流230吸收之熱減少,再次造成煙道氣流226退出該空氣預熱器時具有較高之溫度。Similarly, as the air baffle assembly 162 more closely closes the air inlet 130, the velocity of the inlet air flow 230 increases. Further closing the air inlet 130 also reduces the surface area of the heat exchange elements 142 exposed to the air inlet stream 230. This results in a reduction in the heat absorbed by the air inlet stream 230, again causing the flue gas stream 226 to have a higher temperature exiting the air preheater.
穿過該空氣預熱器100之煙道氣之速度增大傾向於以基於該速度增大至3.4乘冪之一速率來侵蝕該空氣預熱器中所聚集之沈積物。該控制器可操作該煙道氣擋板152及該空氣擋板162,以最大化對聚集物之侵蝕,然而,該等擋板總成可能無法閉合至允許退出之煙道氣超過一最大可允許溫度之程度。此溫度可能係基於下游設備可安全地容忍之最大溫度加上希望之安全裕度而預決定。The increase in velocity of the flue gas passing through the air preheater 100 tends to erode deposits accumulated in the air preheater at a rate that increases to a power of 3.4 based on the speed. The controller can operate the flue gas baffle 152 and the air baffle 162 to maximize erosion of the aggregates, however, the baffle assemblies may not be closed until the flue gas allowed to exit exceeds a maximum The degree of temperature allowed. This temperature may be predetermined based on the maximum temperature that the downstream equipment can safely tolerate plus the desired safety margin.
參考圖3至圖6,該空氣擋板總成162包含一框架182及定位於該框架182內之多個擋板156。較佳的是,該等擋板156係經分組為一些擋板面板163、164。除了關聯之擋板156,每個阻擋面板163、164包含一致動器166及一驅動器 168,其將該致動器166連接至該等擋板156之各者。Referring to FIGS. 3-6, the air baffle assembly 162 includes a frame 182 and a plurality of baffles 156 positioned within the frame 182. Preferably, the baffles 156 are grouped into a plurality of baffle panels 163, 164. In addition to the associated baffle 156, each of the blocking panels 163, 164 includes an actuator 166 and a driver 168, which connects the actuator 166 to each of the baffles 156.
如圖3所示,該空氣擋板總成162可將該煙道氣入口(圖2之124)分割成若干區段。該等擋板區段163、164之擋板156係經定位而控制煙道氣入口124內之流。該煙道氣入口124之另一區段174係保持開啟而不具有擋板總成或擋板。As shown in FIG. 3, the air baffle assembly 162 can divide the flue gas inlet (124 of FIG. 2) into segments. The baffles 156 of the baffle sections 163, 164 are positioned to control the flow within the flue gas inlet 124. The other section 174 of the flue gas inlet 124 remains open without a baffle assembly or baffle.
煙道氣擋板總成152與上述之空氣擋板總成162具有相同之部件且以相同之方式操作。因此,當應用至該煙道氣入口而非空氣入口時,上文之描述同樣適用於煙道氣擋板總成152。The flue gas baffle assembly 152 has the same components as the air baffle assembly 162 described above and operates in the same manner. Thus, the above description applies equally to the flue gas baffle assembly 152 when applied to the flue gas inlet rather than the air inlet.
該控制器158操作該等擋板區段163、164之致動器166,以部分限制該煙道氣入口(圖2中之124)之特定區域中之流。The controller 158 operates the actuators 166 of the baffle sections 163, 164 to partially limit the flow in a particular region of the flue gas inlet (124 in Figure 2).
應理解,根據本發明之再生型空氣預熱器100可包含如圖3至圖6中之更多或更少擋板總成152、162。此外,該煙道氣入口124之較小或較大部分係經保持不具有擋板總成,以控制穿過該煙道氣入口124之流。It should be understood that the regenerative air preheater 100 in accordance with the present invention may include more or fewer baffle assemblies 152, 162 as in Figures 3-6. In addition, the smaller or larger portion of the flue gas inlet 124 remains without the baffle assembly to control flow through the flue gas inlet 124.
圖6係圖5之一部分之放大圖。其顯示擋板156係可圍繞一軸176而在一「開啟」位置與「閉合」位置之間旋轉。一平坦桿密封件178係經安裝至每個擋板156之兩側。桿密封件178覆蓋且接觸桿密封件178之鄰接擋板之一部分,以阻止煙道氣在該等擋板之間流動。該擋板之最為鄰近該框架182之桿密封件178接觸該框架182之一部分,以阻止煙道氣在該框架182與該擋板156之間流動。Figure 6 is an enlarged view of a portion of Figure 5. The display baffle 156 is rotatable about an axis 176 between an "open" position and a "closed" position. A flat rod seal 178 is mounted to both sides of each baffle 156. A rod seal 178 covers and contacts a portion of the rod seal 178 adjacent the baffle to prevent flue gas from flowing between the baffles. A rod seal 178 of the baffle that is closest to the frame 182 contacts a portion of the frame 182 to prevent flue gas from flowing between the frame 182 and the baffle 156.
現參考圖3,對於垂直流空氣預熱器,控制器(圖2之 158)係經程式化而週期性地開啟一「經閉合」擋板面板163之擋板156,同時閉合一「開啟」擋板總成164之該等擋板156,同時維持大體恆定流動區域。此操作允許該「經閉合」擋板總成164之擋板158流出可能聚集於該等擋板156之頂部上之任何灰塵沈積物。Referring now to Figure 3, for a vertical flow air preheater, the controller (Figure 2 158) Periodically opening a baffle 156 of a "closed" baffle panel 163 while simultaneously closing the baffles 156 of an "open" baffle assembly 164 while maintaining a substantially constant flow area. This operation allows the baffle 158 of the "closed" baffle assembly 164 to flow out of any dust deposits that may collect on top of the baffles 156.
現參考圖2,限制該煙道氣入口124之流動區域增加該煙道氣流之速度,從而造成承載於該煙道氣中之飛灰侵蝕冷端沈積物。然而,對於熱轉移,速度較高且面積較少將產生高於正常煙道氣出口溫度之溫度。即,閉合煙道氣入口之若干部分有效地阻止煙道氣流經所安裝之熱交換元件(圖1之142)之若干部分,從而減小有效的熱轉移面積且增高離開空氣預熱器100之煙道氣溫度。Referring now to Figure 2, limiting the flow region of the flue gas inlet 124 increases the velocity of the flue gas stream, thereby causing fly ash carried in the flue gas to erode cold end deposits. However, for heat transfer, higher speeds and smaller areas will result in temperatures above the normal flue gas outlet temperature. That is, portions of the closed flue gas inlet effectively block flue gas flow through portions of the installed heat exchange element (142 of Figure 1), thereby reducing the effective heat transfer area and increasing the exit of the air preheater 100. Flue gas temperature.
此外,在100%功率下之一較大壓力降對於較高壓力之空氣及煙道氣風扇188需要較高的成本且運轉此等較大風扇188之較大馬達之操作成本較高。除了最差之煤炭之外,發電廠資料測量系統並不顯示出在滿負載超過8小時之時間內,吹灰循環之間存在壓力降。所觀察到之積垢係已經在有些較熱上游表面上形成、由該煙道氣流所推動且承載的來自「爆裂(popcorn)」之大顆粒或爐渣而形成之熱端積垢,或可為位於低速度及低紊流區域中之酸積垢及/或顆粒積垢之冷端積垢。In addition, a large pressure drop at 100% power requires higher cost for higher pressure air and flue gas fans 188 and higher operating costs for larger motors operating such larger fans 188. In addition to the worst coal, the power plant data measurement system does not show a pressure drop between the soot blowing cycles over a full load of more than 8 hours. The observed fouling is hot end fouling that has formed on some of the hotter upstream surfaces, is propelled by the flue gas stream and carries large particles or slag from "popcorn", or may be Cold-end fouling of acid deposits and/or particulate deposits in low velocity and low turbulence areas.
然而,在低負載條件下,該氣體出口溫度始終低於針對該MCR設計點之氣體出口溫度。此係歸因於兩個因素。在較小之鍋爐負載條件下,進入該空氣預熱器100中之煙道氣之溫度低於在設計點下之溫度。該空氣預熱器100亦更有效,此係因為煙道氣速度亦較低且因此所得之熱轉移係數之減小較退出該表面積之流之減少具有較小之效果,因此在該煙道氣溫度中產生更大之減小。通常,發生於低負載下之較低溫度足夠低而導致硫酸之凝結。一些發電廠使用蒸氣加熱來增高入口空氣溫度,且因此退出氣體溫度及元件板溫度,以避免使酸冷凝。然而,由於速度降低之灰塵聚集不會藉由此程序而緩解。However, under low load conditions, the gas outlet temperature is always below the gas outlet temperature for the MCR design point. This is due to two factors. Under smaller boiler load conditions, the temperature of the flue gas entering the air preheater 100 is lower than the temperature at the design point. The air preheater 100 is also more efficient because the flue gas velocity is also lower and thus the resulting thermal transfer coefficient has a smaller effect than the flow exiting the surface area, so the temperature in the flue is A greater reduction in degrees. Generally, lower temperatures occurring at low loads are sufficiently low to cause condensation of sulfuric acid. Some power plants use steam heating to increase the inlet air temperature and therefore exit the gas temperature and component plate temperature to avoid condensation of the acid. However, dust accumulation due to reduced speed is not alleviated by this procedure.
表1對比在百分之三十(30%)之負載條件、百分之七十(70%)負載條件及MRC期間本發明相對於習知之空氣預熱器之煙道氣速度。根據本發明之擋板總成152、162係用於實施該煙道氣入口流動面積之百分之五十(50%)之減少,以產生該煙道氣流之速度中的明顯增加。如在表中可見,將煙道氣之入口速度增加一倍使得該煙道氣之出口速度增加一倍,且平均煙道氣出口速度成比例地增加至3.4乘冪。使用本發明,可在70%之功率及MCR為3.54之情形下達成將平均煙道氣出口速度之比率到達3.4乘冪,而使用習知之空氣預熱器,該比率為0.32。在30%之功率位準下,本發明之比率為0.43,相較之下,習知之空氣預熱器為0.04。在30%負載情形下,閉合額外之擋板56將提供更高之冷端速度及更好之清潔效果(速度至3.4乘冪)。此實例之條件並不一定為最佳條件,而是僅闡明本發明之原理。Table 1 compares the flue gas velocities of the present invention relative to conventional air preheaters during thirty (30%) load conditions, seventy percent (70%) load conditions, and MRC. The baffle assemblies 152, 162 in accordance with the present invention are used to effect a fifty percent (50%) reduction in the flow area of the flue gas inlet to produce a significant increase in the velocity of the flue gas stream. As can be seen in the table, doubling the inlet velocity of the flue gas doubles the exit velocity of the flue gas and increases the average flue gas exit velocity proportionally to 3.4. Using the present invention, the ratio of the average flue gas exit velocity can be reached to 3.4 volts with 70% power and an MCR of 3.54, using a conventional air preheater, which is 0.32. At a power level of 30%, the ratio of the present invention is 0.43, compared to 0.04 for a conventional air preheater. At 30% load, closing the additional baffle 56 will provide a higher cold end speed and better cleaning (speed to 3.4 volts). The conditions of this example are not necessarily the best conditions, but merely illustrate the principles of the invention.
在替代實施例中,該等擋板係可由齒輪驅動器、帶驅動器、鏈條機構、螺線管或其他已知之致動器機構而致動。此等均屬於本發明之範疇。In alternative embodiments, the baffles can be actuated by a gear drive, a belt drive, a chain mechanism, a solenoid, or other known actuator mechanism. These are all within the scope of the invention.
雖然已經顯示且描述了較佳實施例,可在不脫離本發明之精神及範疇對本發明做出各種修改及替代。據此,應理解,本發明係藉由闡明且非限制之方式而描述。While the preferred embodiment has been shown and described, various modifications and Accordingly, the invention is to be considered as illustrative and not restrictive.
100...空氣預熱器100. . . Air preheater
112...轉子112. . . Rotor
114...殼體114. . . case
116...隔板或隔膜116. . . Partition or diaphragm
118...轉子柱118. . . Rotor column
120...隔室120. . . Compartment
122...熱交換元件籃架總成122. . . Heat exchange component basket assembly
124...熱煙道氣入口124. . . Hot flue gas inlet
126...經加熱空氣出口126. . . Heated air outlet
130...空氣入口130. . . Air inlet
132...空氣出口132. . . Air outlet
136...區段板136. . . Section board
138...空氣區段138. . . Air section
140...煙道氣區段140. . . Flue gas section
142...熱交換元件142. . . Heat exchange element
144...冷端144. . . Cold end
146...熱端146. . . Hot end
148...鍋爐148. . . boiler
152...擋板總成152. . . Baffle assembly
154...煙道氣導管154. . . Flue gas duct
156...擋板156. . . Baffle
158...控制器158. . . Controller
160...發電廠分佈式控制系統160. . . Power plant distributed control system
162...擋板總成162. . . Baffle assembly
163...擋板面板163. . . Baffle panel
164...擋板面板164. . . Baffle panel
166...致動器166. . . Actuator
168...驅動器168. . . driver
174...煙道氣入口124之一部分174. . . Part of the flue gas inlet 124
178...桿密封件178. . . Rod seal
179...桿密封件179. . . Rod seal
182...框架182. . . frame
188...風扇188. . . fan
224...煙道氣流224. . . Flue gas flow
226...煙道氣流226. . . Flue gas flow
230...空氣入口流230. . . Air inlet flow
232...經加熱空氣出口流232. . . Heated air outlet flow
圖1係習知之旋轉式再生型空氣預熱器之部分透視、截面圖;Figure 1 is a partial perspective, cross-sectional view of a conventional rotary regenerative air preheater;
圖2係具有根據本發明之再生型空氣預熱器配置之蒸氣產生系統之示意圖;Figure 2 is a schematic illustration of a vapor generation system having a regenerative air preheater configuration in accordance with the present invention;
圖3係圖2之擋板歧管之側視立體圖;Figure 3 is a side perspective view of the baffle manifold of Figure 2;
圖4係圖3之擋板歧管之俯視平面圖;Figure 4 is a top plan view of the baffle manifold of Figure 3;
圖5係沿圖3之線V-V而截取之截面圖;及Figure 5 is a cross-sectional view taken along line V-V of Figure 3;
圖6係圖5之區域VI之放大圖。Figure 6 is an enlarged view of a region VI of Figure 5.
152...擋板總成152. . . Baffle assembly
156...擋板156. . . Baffle
162...擋板總成162. . . Baffle assembly
163...擋板面板163. . . Baffle panel
164...擋板面板164. . . Baffle panel
166...致動器166. . . Actuator
168...驅動器168. . . driver
182...框架182. . . frame
Claims (15)
Applications Claiming Priority (1)
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US12/814,812 US20110303135A1 (en) | 2010-06-14 | 2010-06-14 | Regenerative air preheater design to reduce cold end fouling |
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TW201207327A TW201207327A (en) | 2012-02-16 |
TWI507643B true TWI507643B (en) | 2015-11-11 |
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TW100120581A TWI507643B (en) | 2010-06-14 | 2011-06-13 | Regenerative air preheater design to reduce cold end fouling |
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US (1) | US20110303135A1 (en) |
EP (1) | EP2395310A3 (en) |
JP (1) | JP5408629B2 (en) |
CN (1) | CN102287847A (en) |
AU (1) | AU2011202815A1 (en) |
CA (1) | CA2742488A1 (en) |
MX (1) | MX2011006066A (en) |
TW (1) | TWI507643B (en) |
ZA (1) | ZA201104265B (en) |
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US9034081B2 (en) * | 2011-11-22 | 2015-05-19 | Fluor Technologies Corporation | Down-flow direct contact cooler |
CN102777926B (en) * | 2012-08-10 | 2015-05-20 | 山东泓奥电力科技有限公司 | Intelligent rotary air heater on basis of comprehensive temperature control at cold end of air preheater |
US10267517B2 (en) * | 2016-07-08 | 2019-04-23 | Arvos Ljungstrom Llc | Method and system for improving boiler effectiveness |
US11396002B2 (en) * | 2017-03-28 | 2022-07-26 | Uop Llc | Detecting and correcting problems in liquid lifting in heat exchangers |
CN107191963B (en) * | 2017-07-10 | 2023-07-25 | 东方电气集团东方锅炉股份有限公司 | Rotary air preheater and method for preventing ammonium bisulfate from being blocked by rotary air preheater |
CN107477608A (en) * | 2017-09-25 | 2017-12-15 | 长沙天瑞能源科技有限公司 | Air preheater hot blast automatic block clearing anti-blocking system |
CN107965788A (en) * | 2017-11-13 | 2018-04-27 | 湖南大唐节能科技有限公司 | Double heat source air preheaters block controlling device |
CN108167858A (en) * | 2018-01-22 | 2018-06-15 | 江苏港丰锅炉工程有限公司 | A kind of rotary regenerative air preheater system for preventing cold end dust stratification |
CN108870433A (en) * | 2018-06-12 | 2018-11-23 | 大唐东北电力试验研究院有限公司 | A kind of rotary regenerative air preheater calor innatus hearsay passs anti-block apparatus |
CN108826350A (en) * | 2018-06-12 | 2018-11-16 | 大唐东北电力试验研究院有限公司 | Anti-block apparatus is recycled based on the hot Secondary Air for using boiler using brown coal rotary regenerative air heater |
CN108692331B (en) * | 2018-08-07 | 2024-01-26 | 上海敖征实业有限公司 | Air preheater |
CN111306566A (en) * | 2020-02-20 | 2020-06-19 | 华电电力科学研究院有限公司 | Separation type air preheating system and method for preventing ABS (anti-lock brake System) of air preheater from being blocked |
CN112577064B (en) * | 2020-11-11 | 2023-04-28 | 湖南华电常德发电有限公司 | Air preheater anti-blocking structure with hot air introduced in sections and working method thereof |
CN113654074A (en) * | 2021-08-27 | 2021-11-16 | 西安热工研究院有限公司 | Flue gas bin-bypass heat regeneration energy-saving system based on air preheater heat transfer deviation |
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Also Published As
Publication number | Publication date |
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JP2012002499A (en) | 2012-01-05 |
EP2395310A3 (en) | 2013-11-06 |
US20110303135A1 (en) | 2011-12-15 |
TW201207327A (en) | 2012-02-16 |
AU2011202815A1 (en) | 2012-01-12 |
CN102287847A (en) | 2011-12-21 |
MX2011006066A (en) | 2011-12-14 |
ZA201104265B (en) | 2012-12-27 |
CA2742488A1 (en) | 2011-12-14 |
EP2395310A2 (en) | 2011-12-14 |
JP5408629B2 (en) | 2014-02-05 |
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