發(fā)布時(shí)間：2018-07-12 14:11

  本文選題：消音減壓閥 + 流固耦合　； 參考：《武漢工程大學(xué)》2014年碩士論文

【摘要】：鋼鐵行業(yè)在冶煉鋼鐵時(shí)產(chǎn)生的尾氣在通過TRT裝置發(fā)電后依然含有較高壓力的依然可以加以利用的成分，此時(shí)氣體的主要成分為煤氣。高壓煤氣在經(jīng)過一系列普通閥門組的調(diào)節(jié)下可變成低壓煤氣繼續(xù)供普通居民區(qū)日常燃用。然而用于調(diào)節(jié)氣壓的普通閥門組在啟閉的瞬間產(chǎn)生高達(dá)95-140分貝的污染噪聲。眾所周知，噪聲已經(jīng)成為對(duì)人們的心理和生理都有著嚴(yán)重危害的重要污染物，已成為繼大氣污染，水污染之后的第三大公害。在普通閥門組外建造密閉消聲室的方法雖然能達(dá)到將噪聲的危害控制在相關(guān)工業(yè)標(biāo)準(zhǔn)和規(guī)范所要求的噪聲范圍內(nèi)的目的，但卻耗費(fèi)了巨大的土地資源成本和建造成本。若是開發(fā)設(shè)計(jì)出一種兼有自由調(diào)節(jié)氣壓和降低噪聲功效的新型閥門—消音減壓閥，該新型消音減壓閥將會(huì)在節(jié)約資源、減排環(huán)保等方面有著廣闊的開發(fā)前景、巨大的使用價(jià)值和現(xiàn)實(shí)意義。 通過對(duì)相關(guān)聲學(xué)基礎(chǔ)理論進(jìn)行研究，發(fā)現(xiàn)消音減壓閥噪聲主要源自啟閉過程中產(chǎn)生的機(jī)械噪聲和氣動(dòng)噪聲，其中機(jī)械噪聲是閥門在啟閉時(shí)產(chǎn)生的，該噪聲主要是由于高速氣流對(duì)周圍固體結(jié)構(gòu)產(chǎn)生沖擊而使周圍腔體產(chǎn)生振動(dòng)而發(fā)出的；氣動(dòng)噪聲主要來自氣體流動(dòng)時(shí)自身湍流而產(chǎn)生的。依據(jù)中科院聲學(xué)研究所馬大猷教授所提出的微穿孔板消聲減噪的理論，結(jié)合某實(shí)際工程案例的相關(guān)參數(shù)和某公司申請(qǐng)的應(yīng)用型發(fā)明專利，提出一種新型消音減壓閥的結(jié)構(gòu)形式。 在對(duì)該工程問題進(jìn)行深入地了解和剖析后，發(fā)現(xiàn)消音減壓閥在該管道工藝中起到煤氣流量及壓力調(diào)節(jié)的作用，必須要解決管道氣流流量大，管道口徑大，右端管道的氣流流量要可調(diào)，切斷時(shí)且需要有密封作用，左端和右端的壓力差較大，極易產(chǎn)生噪聲等工作問題，其在負(fù)荷時(shí)工況為閥前壓力為210kPa,閥后壓力為19kPa,氣流量為300000m3/h，工作溫度為165-265℃。本文首先對(duì)消音減壓閥的結(jié)構(gòu)形式進(jìn)行設(shè)計(jì)，在進(jìn)行詳細(xì)設(shè)計(jì)后并繪出滿足管路系統(tǒng)要求的結(jié)構(gòu)示意圖和工程圖紙，其詳細(xì)設(shè)計(jì)尺寸分別為入口接管出口接管直徑為2020mm，厚度為18mm，微穿孔柱板內(nèi)徑為650mm，長(zhǎng)度為600mm，厚度為10mm，閥前腔體直徑為3000mm，長(zhǎng)度為500mm,閥后腔體直徑為4000mm，長(zhǎng)度為1200mm。然后通過采用有限元法對(duì)某一特定幾何尺寸下的消音減壓閥閥體結(jié)構(gòu)進(jìn)行結(jié)構(gòu)強(qiáng)度的有限元計(jì)算，獲得滿足結(jié)構(gòu)強(qiáng)度要求下合適的微穿孔柱板半徑，柱板長(zhǎng)度，柱板厚度，微穿孔柱板上微孔的孔徑，微穿孔排列形式等結(jié)構(gòu)方面的幾何尺寸。在此基礎(chǔ)之上，再對(duì)消音減壓閥進(jìn)行聲學(xué)性能模擬仿真，通過對(duì)比計(jì)算結(jié)果的聲壓級(jí)數(shù)值和實(shí)際的工業(yè)噪聲標(biāo)準(zhǔn)值，可得知：消音減壓閥在管路系統(tǒng)中產(chǎn)生的噪聲在相關(guān)工業(yè)標(biāo)準(zhǔn)所要求的范圍內(nèi)。 再者，采用有限元方法中的流固耦合方法對(duì)消音減壓閥進(jìn)行聲學(xué)有限元分析計(jì)算，獲得消音減壓閥的聲學(xué)性能。在此流程之上，在改變微穿孔柱板的半徑后，對(duì)該消音減壓閥再次進(jìn)行聲學(xué)有限元分析，并對(duì)該計(jì)算結(jié)果和前面所得到的后處理結(jié)果進(jìn)行對(duì)比，可得知改變微穿孔柱板的半徑對(duì)消音減壓閥的減噪有一定程度的影響，，增大微穿孔板的半徑可提高消音減壓閥的減噪效果。在改變微穿孔主板的長(zhǎng)度后，對(duì)該消音減壓閥再次進(jìn)行聲學(xué)有限元分析，并對(duì)該結(jié)果和前面所得到的后處理結(jié)果進(jìn)行對(duì)比，可得知改變微穿孔柱板的長(zhǎng)度對(duì)消音減壓閥的減噪有一定程度的影響，增長(zhǎng)微穿孔板的長(zhǎng)度可提高消音減壓閥的減噪效果。 最后并將得到的聲學(xué)性能結(jié)果與實(shí)際多閥門組結(jié)合密閉消聲室的噪聲結(jié)果進(jìn)行對(duì)比。結(jié)果表明：消音減壓閥在管路系統(tǒng)中調(diào)節(jié)流體壓力和降低噪聲方面有著更多明顯的優(yōu)勢(shì)。通過改變結(jié)構(gòu)的形式，主要采用改變微穿孔柱板的長(zhǎng)度，半徑，微孔孔徑，微孔排列方式等手段來改變結(jié)構(gòu)的方式，分析不同結(jié)構(gòu)形式下的消音減壓閥的聲學(xué)性能，以選用合適的幾何結(jié)構(gòu)的尺寸以達(dá)到減噪優(yōu)化的目的。已獲得的關(guān)于消音減壓閥機(jī)械性能、聲學(xué)性能方面的數(shù)據(jù)和相關(guān)結(jié)論，為進(jìn)一步開發(fā)和設(shè)計(jì)消音減壓閥提供一些有益的建議。
[Abstract]:The tail gas produced in iron and steel industry in the smelting of steel still contains high pressure components that still can be used after the TRT unit. The main component of the gas is gas. High pressure gas can be turned into low pressure gas for daily use in ordinary residential area under the regulation of a series of ordinary valve groups. The ordinary valve group that regulates the pressure produces the pollution noise of up to 95-140 decibels at the moment of opening and closing. It is well known that noise has become an important pollutant that has serious harm to people's psychology and physiology. It has become the third public hazard following air pollution and water pollution. The method of building a closed chamber outside the ordinary valve group is a method of construction. It can achieve the purpose of controlling the harm of noise in the range of noise required by the related industrial standards and specifications, but it consumes huge cost of land resources and construction costs. If a new type of valve, a new type of valve, which has the functions of free adjustment and noise reduction, is developed and designed, the new silencing pressure relief valve will be developed. It has broad development prospects, huge use value and practical significance in saving resources, reducing emissions and environmental protection.
Through the study of the related acoustic theory, it is found that the noise of the noise reduction valve mainly originates from the mechanical noise and aerodynamic noise produced during the opening and closing, in which the mechanical noise is produced when the valve is opened and closed, and the noise is mainly caused by the vibration of the surrounding cavity caused by the impact of the high-speed airflow on the surrounding solid structure. According to the theory of the micro perforated plate noise reduction and noise reduction proposed by Professor DAA DAA of the Academy of acoustics of the Academy of Sciences, a new structure form of a new type of noise reduction pressure relief valve is proposed in accordance with the relevant parameters of a practical engineering case and the application type invention patent applied by a company.
After thorough understanding and analysis of the project, it is found that the silencing pressure relief valve plays the role of regulating gas flow and pressure in the pipeline. It is necessary to solve the large flow flow of the pipe, the large diameter of the pipe, the air flow of the right end pipe, and the sealing effect when cut off, and the pressure difference between the left end and the right end is large. It is very easy to produce noise and other working problems. The pressure of the valve before the valve is 210kPa, the pressure after the valve is 19kPa, the gas flow is 300000m3/h, and the working temperature is 165-265. This paper first designs the structure form of the depressing pressure relief valve, and then the detailed design and the engineering drawings are drawn after the detailed design and the full full line system. The diameter of the inlet nozzle is 2020mm, the thickness is 18mm, the inner diameter of the micro perforated cylinder is 650mm, the length is 600mm, the thickness is 10mm, the diameter of the front cavity of the valve is 3000mm, the length is 500mm, the diameter of the cavity is 4000mm, the length is 1200mm. then through the finite element method, the silencing of a certain geometric size is passed. The structure strength of the pressure relief valve body is calculated by the finite element method, and the geometrical size of the suitable microperforated column plate radius, the length of the cylinder plate, the thickness of the column plate, the pore size of microperforated microporous plate and the microperforation arrangement are obtained to satisfy the structural strength. On this basis, the acoustic performance of the silencer pressure relief valve is simulated. By comparing the sound pressure level values of the calculated results and the actual industrial noise standard values, it is known that the noise produced by the silencing pressure relief valve in the pipeline system is within the range required by the related industrial standards.
Furthermore, the acoustical performance of the muffling pressure relief valve is obtained by the finite element method of the fluid solid coupling in the finite element method to obtain the acoustic performance of the muffling relief valve. On this flow, the acoustic finite element analysis of the muffled pressure relief valve is carried out again after the change of the radius of the microperforated Cylinder plate. The results are compared. It is found that the radius of the microperforated cylinder can affect the noise reduction of the muffling pressure relief valve to a certain extent. Increasing the radius of the microperforated plate can improve the noise reduction effect of the muffling pressure relief valve. After changing the length of the microperforated main board, the acoustic finite element analysis is carried out again for the muffled pressure relief valve, and the results and the front are also analyzed. The results are compared. It is found that the length of the microperforated cylinder can affect the noise reduction of the muffling pressure relief valve to a certain extent. The increase of the length of the microperforated plate can improve the noise reduction effect of the muffling relief valve.
The results show that the noise reduction valve has more obvious advantages in regulating the fluid pressure and reducing the noise in the pipeline system. By changing the structure, the length of the microperforated cylindrical plate is mainly changed. Diameter, pore size, micropore arrangement and other means to change the structure, analyze the acoustic performance of the muffling pressure relief valve under different structural forms, in order to choose the appropriate geometric structure to achieve the purpose of reducing the noise. It provides some useful suggestions for developing and designing noise reducing valves.
【學(xué)位授予單位】：武漢工程大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2014
【分類號(hào)】：X757;TB535

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