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Yatay silindirik LPG tankının 4 standarda göre tasarımı

Compare of 4 standards in pressure vessel design

  1. Tez No: 19309
  2. Yazar: ROHAT BAYSAL
  3. Danışmanlar: PROF. SELAHADDİN ANIK
  4. Tez Türü: Yüksek Lisans
  5. Konular: Makine Mühendisliği, Mechanical Engineering
  6. Anahtar Kelimeler: Belirtilmemiş.
  7. Yıl: 1991
  8. Dil: Türkçe
  9. Üniversite: İstanbul Teknik Üniversitesi
  10. Enstitü: Fen Bilimleri Enstitüsü
  11. Ana Bilim Dalı: Belirtilmemiş.
  12. Bilim Dalı: Belirtilmemiş.
  13. Sayfa Sayısı: 148

Özet

ÖZET Endüstrinin değişik alanlarında kullanılan basınçlı kapların tasarımında, değişik tasarım kuralları uygulanmak tadır. Bu kurallar arasındaki temel fark, kullanılan mal zeme için öngörülen tasarım gerilmelerinden doğmaktadır. Tasarımı bir ülkede yapılıp, bir başka ülkede imâl edilen ve diğer bir ülkede de montajı yapılan bir basınçlı kabın, hangi tasarım kurallarına göre kabul edileceği sorunlar çı karmaktadır, yurdumuzda en yaygın şekilde kullanılan 5 ta sarım kuralı TSE, Türk Loydu, AD Merkblatter, ASME Sec. VIII- Div.l ve ASME Sec. VIII-Div. 2, olduğundan çalışmada bu tasa rım kurallarına yer verilmiş, sözkonusu standartlar Basic dilinde yazılmış bir bilgisayar programı ile incelenmiş ve aralarındaki temel farklar grafikler halinde verilmiştir. -vı-

Özet (Çeviri)

SUMMARY COMPARE OF 4 STANDARDS IN PRESSURE VESSEL DESIGN It's applied different design rules for pressure ves sels used in various sectors of industry. The main differen ce among these rules comes from the differences in design streses of the material used in vessel. A pressure vessel designed in a country and manufactured in another country and maunted in a country apart from those causes problems so that it is not known which design rules will be accepted. If there was only one design code, this kind of a problem wouldn't occur. Today in industrious countries like USA, Canada, U.S.S.R., Germany, England etc., 19 different design codes are being applied. In this thesis four design ru|es (standards) which are widely known (ASME Sec. VII I-Div.1, ASME Sec.VIII-Div. 2, AD Merkblatter, Turkish Loyd) were examined by a computer program written ıh Basic and main differences among these rules were demonstrated by graphics. Also design princip les for each standards were explained in due order. The design rules are only valid for horizontal, cylindrical and welded vessels. The essential datas of pessure vessel design are operation pressure and operation temperature. Calculations mentioned in AD Merkblatter codes can not be used at temperatures less than -10 C since materials shift sharply under this temperature. The use of general construction steel (St 33, St 34, St 37, 2, St 42, St 52) is limited to 300°C and the multiplication of vessel diameter (mm) and p design pressure (bar) should not exceed 20000. Boiler plates HI, HII, HIII can be used up to 450°C without any pressure limits for stainless steels although operation temperatures can reach 4 50 C and some types even 550°C depending on the type of the stainless steel, 400°C should not be exceeded. Although the wall thickness calcu lations are based on the yield point at design temperature in AD Merkblatter ahd T.L. codes, ASME codes gives directly the permitted strength values instead of yield point valu es. Yield point and permitted strength values vary due to design tempetarutes. ASME (2) codes cnsist of more strict rules than ASME (1). So the calculated wall thickness according to ASME (2) is less than the wall thickness value calculated according to ASME (1). -vii-PRESSURE VESSELS DESIGN ACCORDING TO AD MERKBLATTER: The essential data of pressure vessel design are operation pressure and temperature. Design pressure and temperature are usualy chosen equal or a little bit higher than the operation values. Wall thickness calculations should be based on the yield point at design temperature. Variation of the yield points with temperature are given in the content of the thesis. Cost iron and steels should only be used under spe cial precautions in causes where they have specific advan tages compared with other materials. Required wall thickness for cylindrical shell is given as, s= ^^ +C1+C2 20.-fUp The variables of this equation are as follows, s S Da P K V CI Required wall thickness Safety factor Outher diamenter of vessel Design pressure Material strength value at operation temperature Velded joint weakening facton Allowance to compansete for wall thickness tolarances The equations for dished ends is as follows, DaP$ s = An KV 40-- - 0 is used to balance the weakening due to nozzles on the dished ends and is given in tables. Apart from this, same special precautions should be taken in vessel design, because of this weakening. These precaution which can be summarized as increasing shell thickness locally or totally, increasing the nozzle thick ness and using reinforcement plates, are given further in the thesis. -Vlll-The values of the safety factors are given in tab les according to the type of the material. AD Merkblatter codes also strictly define the test conditions of pressure vessels i.e safety factors, test li quid test pressure, and all other test coditions are detai led. PRESSURE VESSEL DESİGN ACCORDING TO ASME CODES: ASME Codes are not different from AD Merkblatter in defining essential data, such as operation temperature and pressure, design pressure and temperature. However ASME gives required wall thickness for cylindrical shells as, t= - (According to ASME Sec.VIII/ 100.SE-0,6P Div.l) PR t= - (According to ASME Sec.VIII/ 100.S-0,5P Div.2) and for torispheric dished end as, PLM (According to ASME Sec.VIII/ 200.S.E-0,2P Div.l) t= L.e A (According to ASME Sec.VIII/ Div.2) where, P : Design Pressure S : Permitted strenght value E : Welding performance factor R : Internal radius t : Required wall thickness L : Outside radius of dish If -|p>16-|- then, M= -|-( 3+ -|- ) else M is determined from table, 2 2 2 2 A=a1 + a2x+a-x +(b1+b2x+b3îi ) y+ (c^+c^ + ^x }y x=r/2R where r=inside knuckle redius y=ln P/S Corrosion allowance are also mentioned in this secti on and application range, chemical resistance and thermal expansion characteristics of materials are indicated in tables. -IX-Supporting details of horizontal pressure vessels and vessel manholes are pointed out and standardized di mensions are given also. A horizontal vessel on saddle support acts as a beam with the following deviations. 1) The loading conditions are different for a full or partially filled vessel. 2) The stresses in the vessel vary according to the angle included by the saddles. 3) The load due to the weight of the vessel is combi ned with other loads. LOADINGS: 1) Reaction of the saddles. It's a recommended prac tice to design the vessel for at least a full waterload. 2) Internal Pressure: Since the longitudinal stress in the vessel is only one half of the cincumf erential stress, abaut one half of the actually used plate thickness is avai lable to resist the load of the weight. 3) External Pressure: If the vessel is not designed for full vacuum because vacuum occurs incidentally only, a vacuum relief valve spould be provided especially when the vessel outlet is connected to a pump. 4) Wind Load: Long vessels with very small t/r (Where t is thickness and r is inside knuckle radius) values are subject to distortion from wind pressure. 5) Impact Loads: Experience shows, that during ship ping, hardly calculable impact loads can demage the vessels. When designing the width of the saddles and the weld sizes this weld sizes, thiz circumstance is to be considered. LOCATION OF SADDLES: The use of only two saddles is prefferred both sta tically and economically over the multiple support system, this is true even if the use of stiffener rings is neces sary. The location of the saddles is sometimes determined by the location of openings, sumps, etc., in the bottom of the vessel if this is not the case, then the saddles can be placed at the statically optimal point. Thin walled ves sels with a large diamenter are best supported near the heads, so as to utilize the stiffening effect of the heads. Long thick walled vessels are best supported where the max imal longitudinal bending stress at the saddles is nearly equal to the stress at the midspan. This point varies with the contact angle of the saddles. The distance bet ween the head tangent line and the saddle shall in no case be more than 0,2 times the lenght of vessel. -x-CONTACT ANGLE Q : The minimum contact angle suggested by the ASME code is 120°., except for very small vessels. For unstiffened cylinders under external pressure the contact angle is man datorily limited to 120 by the ASME code. STRESSES: Vessels supported by saddles are subject to: 1) Longitudinal bending stress 2) Tangential shear stress 3) Circumferential stress PRESSURE VESSEL DESIGN ACCORDING TO THE TURKISH LOYD (T.L.) Required wall thickness for cylindrical shell is gi ven as, where, t=- P R 100. CTte-0,5p P : Design pressure (bar) radius of shell R : Internal nominal tJt : Nominal design strength e : Allowance for welded seams For temperatures up to 50°C: If Ob/2,7 is greater than, tfF/1,3 then 6t ='Cf/1,0 else tft= C>B/2, 7 where, CF= Min. Yield Strenght (Nt/mm2) 0B= Min. Tensile Strenght (Nt/mm2) There are 3 class of pressure vessel according to T.L. e is 1 for class (1) vessels, 0,8 for class (2) vessels and 0,6 for class (3) vessels. Required wall thickness for dished ends is as follows; where, pDo K 20 0,18. Do, R^Do, r ^, 0, 1 Do) where,H : Height of head r : Inside knuckle radius K : (Shape factor), which is a function of H/Do value is indicated in table in further sections. As for the program, the aim of the program to compa re the costs calculated according to each of the standards. Program consists of followings: - Calculation of required wall thickness of shells and dished end. - Calculation of reinforcement. - Calculation of type and number of bolts. - Calculation of dimensions and numbers of the plates used in shell and dished end. - Calculation of general cost of tank. Program cosist of one main program and 2 secondary programs which are related to main program. In the program Turkish Standards (T.S.E) wasn't mentioned for this stan dard is similiar to AD Merkblatter. First the main parameters (Design pressure, design temperature and the bulk.) After this the material which will be used in vessel are determined. For the main purpo se is to compare the 4 standards, same materials were used for each standards. If design temperature and material are definite also permissible design stress values are definite. The program goes on as follows. 1- Nominal wall thickness for torispherical and ellipsoidal head and cylindrical shell are determined. The formula which gives the wall thickness also cosists of cor rosion allowance that is the function of service period of vessel (It was accepted that corrosion speed is 0,15 mm/ year. ) 2- Taking these nominal wall thicknesses into consi deration the real wall thicknesses those will be used in calculations are determined by users. These new thicknes ses will be more than the nominal ones certainly. 3- Materials for nozzles are selected from the menu. 4- Min. permissible strength for the nozzle material are determined. 5- Inside diameter of nozzle is selected by the user, 6- Nominal wall thickness of nozzle is calculated. 7- Taking the nominal wall thickness into cosidera- tion, the real wall thickness of nozzle is determined by the user. -xxi-8- The required reinforcement area and allowable reinforcement area are calculated one by one. 9- If the required reinforcement area is greater tahn allowable reinforcement area, reinforcement plate is used. 10- Required minimum dimensions of the circular reinforcement plate are calculated. 11- If the calculations are being made according to AD Merkblatter, another calculation process is applied. In this case and Va values are inside diameter, according to the nozzle inside diamenter, wall thickness of nozzle and inside diameter values. is inserted in the formula that calculates head thickness with branch and Va is in serted in the formula that calculates shell thickness with branch. 12- Number and type of bolts used in manhole is calculated taking the bolt forces into cosideration. 13- Number and type of plates that produces the vessel is determined. 14- The stresses on the vessel, caused by the carriers, (Bending, shear and circular stresses) are deter mined. It's controlled whether the vessel is in safety. 15- The amount of electrods and submerged welding wire and powder, total electricity costs total welding period and general cost of pressure vessel are determined. -xiix-

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