line sizing calculation pdf

It is worth noting, however, that if the pipe run is particularly long and in exposed conditions, it is worth checking the running load of the pipe covered in Module 2.12 Steam consumption of pipes and air heaters. To calculate the minimum Pipe size with out considering pressure, D=(Q x 354)/(V x W) Where, D Nominal bore of the pipe (mm) Q Flow Rate (Kg/hour) V Velocity of the Fluid (m/sec) W Specific weight of Fluid (Kg/m3) D= (117000 x 354) / (50 x 21.55) D =196mm PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 6 OF 17 Alternatively, D=595 ((Q x Vs) / V) Where, D Nominal bore of the pipe (mm) Q Flow Rate (Tons/hour) Vs Specific Volume=0.04639m3/Kg V Velocity of the Fluid (m/sec) D = 595 ((117 x 0.04639)/50) D = 196mm STEP 2 FINDING THE STANDARD WALL THICKNESS FOR THE CORRESPONDING NOMINAL BORE. Viewed in isolation, this velocity may seem low in comparison with maximum permitted velocities. Table 10.2.1 compares the actual bore sizes of different sized pipes, for different schedule numbers. Using Figure 10.2.7, draw a vertical line from 450C on the temperature axis until it intersects the 50 bar line (Point A). The point at which lines DE and BC cross will indicate the pipe size required. Y Values of coefficient, valid for t < D/6 and for materials shown. Z= K1 + K2 K1 = For 90 degree elbow = 30ft K2 = for 45 degree elbow = 16ft Z= (30 x 0.02 x 12) + (16 x 0.02 x 2) Z= 7.84 Therefore Pressure drop, P = (21.55 x 402 / 2 x 9.8) ((0.02 x 95)/0.248) + 7.84) P = 27269.617 Kg/m2 P = 2.73 Kg/cm2 Sheet 16 OF 17 PIPE SIZE & PRESSURE DROP CALCULATIONS CASE-1 NB=200 Sheet 17 OF 17 CASE-2 NB=250 Pressure drop = 4.79 Kg/cm2 Pressure drop=2.73 Kg/cm2 Steam Velocity = 50 m/s Steam Velocity = 40 m/s PRESSURE DROP FROM NOMOGRAPHS: Pressure drop in liquid lines (for both laminar and turbulent condition) can also be found out from the nomographs. Substituting these pressure factors (P1 and P2) into Equation 10.2.8 will determine the value forPDF: Following down the left-hand column of the pipeline capacity and pressure drop factors table (Table 10.2.6 - Extract shown in Table 10.2.3); the nearest two readings around the requirement of 0.032 are 0.030 and 0.040. 0000000671 00000 n stream The running load should then be added on to the steam consumption to give the total steam load and the selected pipe checked to ensure it is still correctly sized. 2) NPSH: Where applicable, the pipeline velocities and sizes shall be such as to ensure that the NPSH requirements are less than availability. "IzkWTRnP8),f\glsEl~< Pipes for steam systems are commonly manufactured from carbon steel to ASME B 16.9 A106. Sheet 1 OF 17 revision date: PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 1 OF 17 INTRODUCTION FOR DESIGNING ANY PIPE SYSTEM, THE FIRST ACTIVITY, AFTER FINALISATION OF PROCESS FLOW DIAGRAM, IS DETERMINING THE SIZE OF THE PIPELINES OF VARIOUS FLUIDS. - To provide for mechanical strength of pipe - To provide for corrosion and/or erosion - For cast iron pipe the following values of A shall apply: PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 9 OF 17 Centrifugally cast ------ 3.56mm Statically cast ------------ 4.57mm Y Refer attachment for coefficient values-taken from ANSI B31.1. Bryan Steam Deaerator Sizing Program highlighted cells are for job conditions and to be entered by user Even these velocities can be high in terms of their effect on pressure drop. Pipes, valves, fittings, etc. As can be seen, this procedure is fairly complex and can be simplified by using the nomogram shown in Figure 10.2.9 (in the Appendix of this Module). 3VYN5. 2 0 obj <> DArcy (DArcy Thompson 1860 - 1948) added that for fluid flow to occur, there must be more energy at Point 1 than Point 2 (see Figure 10.2.3). For nominal size piping 150 mm and smaller, Schedule 40 (sometimes called standard weight) is the lightest that would be specified for steam applications. AS PER ANSI B31.3 For Straight Pipes, Minimum wall Thickness, t = PD / 2 (SE + PY) Required Wall thickness, t = (t + Corrosion allowance) / Mill tolerance Where, PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 7 OF 17 P Internal Design gage pressure (Kg/cm2) D Outside diameter of pipe as listed in tables of standards or specification or as measured (mm) S Allowable stress value (Kg/cm2) E quality factor. 0000043496 00000 n The selection of piping material and the wall thickness required for a particular installation is stipulated in standards such as EN 45510 and ASME31.1. Z= K1 + K2 Where K is defined as the resistance coefficient of the valve or fitting. AS PER ANSI B31.1 Minimum Wall thickness, tm = ((PDo/2(SE+PY) + A) SE or SF Max. iii) In case of short pipe runs, pressure drops are generally inconsequential. Bernoullis Theorem (Daniel Bernoulli 1700 - 1782) is discussed in Block 4 - Flowmetering. %%EOF It is recommended that pipelines over 50 m long are always checked for pressure drop, no matter what thevelocity. In practice whether for water pipes or steam pipes, a balance is drawn between pipe size and pressureloss. rC-i/SS#]rYlXXVI).1rv5Jt]_VNtQwSuP|; (Refer attachment 1taken from ANSI B31.3) For t D/6, Y = (d + 2c) / (D+d+2c) Negative Mill Tolerance = 12.5% (Generally) Corrosion allowance = 1.5mm (Varies case to case) Since the minimum diameter of the pipe is 196mm, Let us select 8 pipe (200NB) for calculation, Minimum wall Thickness, t = (72.7 x 219.1) / 2 (1055 + 72.7 x 0.7) = 7.20 mm. 1 Using formulae to establish steam flowrate on pressure drop. It follows then, that if a reasonable velocity could be used for a particular fluid flowing through pipes, then velocity could be used as a practical sizing factor. In essence, the friction factor depends on the Reynolds number (Re) of the flowing liquid and the relative roughness (kS/d) of the inside of the pipe; the former calculated from Equation 10.2.6, and the latter from Equation 10.2.7. A 100 mm Schedule 80 pipe has an outside diameter of 114.30 mm, a wall thickness of 8.56 mm, giving a bore of 97.18 mm. 7Fs>k Incase of pipelines located outdoor, higher values of velocity are acceptable. The nomograms in Figures 10.2.9 and 10.2.10 can also be used for superheated steam applications. The method of use is explained in Example 10.2.3. On an SI style Moody chart, the friction factor scale might typically range from 0.002 to 0.02, whereas on an Imperial style Moody chart, this scale might range from 0.008 to 0.08. From point B, project a line vertically upwards until it intersects the inside pipe diameter scale of (approximately) 146 mm (Point C). All these variables are brought together in the DArcy-Weisbach equation (often referred to as the DArcy equation), and shown as Equation 10.2.1. From point A, project a horizontal line to the right until it intersects the steam mass flowrate scale of 30 000 kg/h (30 t/h) (Point B). hbbd``b`$Z-` $. STEP 2: FINDING THE STANDARD WALL THICKNESS FOR THE CORRESPONDING NOMINAL BORE. Typically, pipes are supplied in 6 metrelengths. Address: Copyright 2022 PDFCOFFEE.COM. RECOMMENDED VELOCITY RANGE S.No FLUID 1 STEAM 1.1 SUPERHEATED STEAM 20 TO 75 m/s 1.2 SATURATED STEAM WET STEAM / EXHAUST STEAM 20 TO 40 m/s 1.3 20 TO 30 m/s PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 4 OF 17 2 WATER 2.1 PUMP SUCTION 0.5 TO 1.5 m/s 2.2 PUMP DELIVERY 1.0 TO 3.0 m/s 2.3 BOILER FEED DELIVERY 3.0 TO 6.0 m/s 2.4 CITY WATER 0.5 TO 1.5 m/s 3 OIL 3.1 HEAVY OIL (HEATED) 1 TO 2 m/s 3.2 LIGHT OIL 1 TO 2 m/s 4 GASES 4.1 COMPRESSED AIR 5 TO 15 m/s 4.2 NATURAL GAS 10 TO 30 m/s The above table indicates ranges of velocity, which in some cases are large. Required Wall thickness, t = (8.98 + 1.5) / 0.875 = 11.97 mm. PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 15 OF 17 Calculation of Wall thickness Minimum wall Thickness, t = (72.7 x 273.1) / 2 (1055 + 72.7 x 0.7) = 8.98 mm. 3) Pipeline Erosion: High line velocities lead to line erosion particularly in case of wet steam and water. 40 m/s should be considered a practical limit, as above this, noise and erosion will take place particularly if the steam is wet. ChE Li, CONDUCTOR SIZING CALCULATION Requirement 1800 Amps /Twin Higher installation costs will be incurred, including support work, insulation, etc. Alternatively the pipe size can be calculated arithmetically. The next lower factor is always selected; in this case, 0.030. %PDF-1.5 % For SI based friction factors, use Equation 10.2.1; for Imperial based friction factors, use Equation 10.2.2. The Procedure for line sizing is to first select a preliminary size based on assumed velocity and examine the suitability of the selected size from the point of view of the various system requirements discussed above. However, Equation 10.2.3 is difficult to use because the friction factor appears on both sides of the equation, and it is for this reason that manual calculations are likely to be carried out by using the Moody chart. It is essential that the right version of the DArcy equation be used with the selected friction factor. The inside pipe diameter scale recommends a pipe with an inside diameter of about 120 mm. Having sized the pipe using the pressure drop method, the velocity can be checked ifrequired. stream 812 0 obj <>/Filter/FlateDecode/ID[<0FD6F7E39402EF438978A55FE48EF1FD>]/Index[793 38]/Info 792 0 R/Length 92/Prev 101978/Root 794 0 R/Size 831/Type/XRef/W[1 2 1]>>stream Utilising the waste heat from a process, a boiler/superheater generates 30 t/h of superheated steam at 50 bar g and 450C for export to a neighbouring power station. x[K9@{( On one hand, inadequate allowances would result in shortfall in capacity at a future date and On the other hand, excessive allowances result in over sizing of piping, which besides increasing piping costs. Values of K for usual valves and fittings are furnished here. Information required to calculate the required pipesize: A process requires 5 000 kg/h of dry saturated steam at 7 bar g. For the flow velocity not to exceed 25 m/s, determine the pipe size. hWYo7+|Q >DhZXacmt}g$E$ n Q3>}&ii7,lch5Xa?Wd+Y`lPprCk$XN&=WT!n'`M (HkaH g/(DS\xNo>{(M s*2Q!dX*=N#h;89) ii) When line pressures are low, select lower values of velocity to keep pressure drop low. hb```*|cb`NLLNP sfzPXAgoc;c Ad$::;8:@CGc%(A(f`eewl0!ydc,` =0.5 as above but for unlicensed works PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 12 OF 17 STEP 3 CALCULATION OF THE PRESSURE DROP FOR THE SELECTED PIPE SIZE FOR THE RECOMMENDED VELOCITY. Tables of schedule numbers can be obtained from BS 1600 which are used as a reference for the nominal pipe size and wall thickness in millimetres. The allowance to be provided depends on the following factors: a) Size of pipe b) Quality of water c) Proportion of friction drop to total system resistance d) Location of pipe buried or above ground. Hb```# There are eleven Schedules ranging from the lowest at 5 through 10, 20, 30, 40, 60, 80, 100, 120, 140 to schedule No. (Refer attachment 6A & 6B- taken from the CRANE handbook). The length of travel from the boiler to the unit heater is known, but an allowance must be included for the additional frictional resistance of the fittings. Doc Ref.No. 5 0 obj In this case, a 40 mm pipe is too small, and a 50 mm pipe would be used. viscous PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 13 OF 17 Re = (103x x V x d) / Where, V Mean Velocity of the fluid (m/sec) d Bore of pipe (m) weight density of fluid (Kg/m3) Dynamic viscosity, in centipoise. Most Active Topics Equation 10.2.2 tends to be used by those who traditionally work in Imperial units, and still tends to be used by practitioners in the United States and Pacific rim regions even when metric pipe sizes are quoted. VGS Thickness = 12.70mm Schedule 80 OD = 273.1mm ID = 247.70 mm. From point A, project a horizontal line to the left until it intersects the steam mass flowrate scale of 30 000 kg/h (30 t/h) (Point B). 0 t^VZiTG46iPVc+x+_Vo&2?!Og wqC`["R\^^TzB,5^6wI=ov}R]O_biZ`38sRU\u-Z,.OuzZ=,b~B,_ftn}YLOfZCD+ps5>O_,>/j:$3his>I*FoESX]8s+&`S_khqpuS=1I{Wy`/-zgqz7w%Dp" LJ1~& hD056,%T--Dq63Aiyih` hqZJMZCO 7 Wgg%; `:TL*(,,K?bJL-F? lq_ . Using the information from Example 10.2.4, use Figure 10.2.8 to determine the minimum acceptable pipesize. H\AO0s#Cl6tn/41YM$Y$Y,IU*+5YaZD]O:Lq/]Gk]_Co From Table 10.2.1 and assuming that the pipe will be Schedule 80 pipe, the nearest size would be 150 mm, which has a bore of 146.4mm. SOFCON-STANLEY APPROVED This tutorial offers detailed advice on standards, schedules, materials and sizing for various saturated and superheated steam duties. Superheated steam can be considered as a dry gas and therefore carries no moisture. This, in turn, means that either: The cost of installing 80 mm steam pipework was found to be 44% higher than the cost of 50 mm pipework, which would have had adequate capacity. x[I+_u'2C@v79#LrySA* v_[VM_}U1~~s7_}}tXs9|=X{Ogc/p#|= jZ/AAz?_`!wp it_? 68SK@=9;/aZx$idRny8yle}kwVOg]fyF\q c7-ZY4zle\ZC6.-u)M0INtm HY.9?'[G\KR|%IfTpLOZkZM&.}W{wx~yU8,9^GM+.G+vN_1n`-~O|p'\yIS)|w:4sPs>ISdy3"OR{6% endstream endobj 115 0 obj << /Type /FontDescriptor /Ascent 891 /CapHeight 656 /Descent -216 /Flags 34 /FontBBox [ -558 -307 2034 1026 ] /FontName /DMOHKI+TimesNewRoman,Bold /ItalicAngle 0 /StemV 160 /XHeight 0 /FontFile2 120 0 R >> endobj 116 0 obj << /Type /Font /Subtype /TrueType /FirstChar 32 /LastChar 176 /Widths [ 250 0 0 0 0 0 0 0 333 333 0 0 250 333 250 278 500 500 500 500 500 500 500 500 500 0 333 0 570 0 570 0 0 722 667 722 722 667 611 778 778 389 0 0 667 944 722 778 611 778 722 556 667 722 722 1000 722 722 667 0 0 0 0 0 0 500 556 444 556 444 333 500 556 278 333 0 278 833 556 500 556 556 444 389 333 556 500 722 500 500 444 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 333 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 400 ] /Encoding /WinAnsiEncoding /BaseFont /DMOHKI+TimesNewRoman,Bold /FontDescriptor 115 0 R >> endobj 117 0 obj << /Type /ExtGState /SA false /SM 0.02 /TR2 /Default >> endobj 118 0 obj << /Filter /FlateDecode /Length 39414 /Length1 60568 >> stream The smallest pipe size, which meets all the system requirements, is the optimum size for the intended service. Equations 10.2.9 and 10.2.10 are shown below. 0Xv+Hn4ANyA&e~EHnkz/n=zHL`l7N/?{7a:N>.,\ Since the Wall thickness is 11.97 mm which is not a standard wall thickness, we can go for the next standard value i.e) 12.70 mm. (Refer attachment 2 for standard wall thickness) PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 8 OF 17 Thickness = 10.31mm Schedule 60 OD = 219.1mm ID = 198.48 mm. DESCRIPTION 107 0 obj << /Linearized 1 /O 109 /H [ 768 697 ] /L 188414 /E 76742 /N 29 /T 186155 >> endobj xref 107 16 0000000016 00000 n 5 0 obj AS PER ANSI B31.4 Nominal Wall thickness, tn = t + A Where, t Pressure design wall thickness (mm) t = PiD / 2S S Applicable allowable stress value, psi S= 0.72 x E x Specified minimum yield strength of the pipe, psi A Sum of allowances for threading and grooving, corrosion AS PER ANSI B31.8 Nominal Wall thickness, t = (P x D) / 2xSx E x T Where, S Specified minimum yield strength, psi F Design factor E Longitudinal joint factor T Temperature derating factor PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 10 OF 17 VALUE OF COEFFICIENT Y IN VARIOUS CODES As per IBR, 1977, Regulation 350 Y = 0.5 As per BS 806, 1980 Y = 0.5 As per DIN 2413, 1972 Y = 0 for T < 1200C = (1-E/2) for T >/= 1200C where T is the design temperature As per ANSI B31.1, 1977 & As per ANSI B31.3, 1977 Y is a function of temperature and has following values: Temperature (0C) Ferritic Steels Austenitic Steels 482 510 538 566 593 621 0.4 0.5 0.7 0.7 0.7 0.7 0.4 0.4 0.4 0.4 0.5 0.7 WELD JOINT EFFICIENCY, E IN VARIOUS CODES As per IBR, 1977, Regulation 350 E = 1 for seamless ERW steel pipes = 0.9 for Welded Steel pipes for thickness thickness 29mm PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 11 OF 17 As per ANSI B31.1, 1977 Seamless pipe = 1.0 Single or double butt-welded pipe with 100% radiography = 1.0 Double Butt-welded pipe = 0.9 ERW pipe = 0.85 Single butt-welded pipe = 0.80 Special Welded pipe ASTM A 211 = 0.75 Furnace Butt-welded pipe = 0.6 As per BS806, 1980 E = 1.0 for seamless, ERW and pipes complying with the requirements of BS3601, BS3602: Part 1 and BS 3604 = 1.0 for Submerged arc welded pipes complying with the requirements of BS3602, Part 2, test category-1(100% NDT for welds) = 0.95 for submerged Arc welded pipes complying with the requirements of BS3602: Part 2, test category-2. Selecting the appropriate pipe size (nominal bore) for a particular application is based on accurately identifying pressure and flowrate. This can only be feasible if; the steam is dry, the pipe is very well insulated, relatively short, straight, horizontal and can supply the required pressure at the point ofuse. Consequently there is no chance of pipe erosion due to suspended water droplets, and steam velocities can be as high as 50 to 70 m/s if the pressure drop permits this. From the European Moody chart (Figure 10.2.4), Where: kS/D = 0.000 3 Re = 93 585: Friction factor (f) =0.005. 0000003911 00000 n ^4Z: Am0>`uT,}g #p-`@iN[:E;s They are commonly referred to as Blue Band and Red Band; this being due to their banded identification marks. The difference in energy is used to overcome frictional resistance between the pipe and the flowingfluid. This is generally expressed in terms of equivalent pipe length. The following additional guidelines may be considered while selecting a suitable value from the range. 0000046174 00000 n MH.l^,J\G S}e9H \?*whC[ Y The reason for the difference is the type of friction factor used. It follows, therefore, that pressure drop through the distribution system is an importantfeature. endstream endobj 794 0 obj <>/Metadata 31 0 R/PageLayout/OneColumn/Pages 789 0 R/StructTreeRoot 35 0 R/Type/Catalog>> endobj 795 0 obj <>/Font<>>>/Rotate 0/StructParents 0/Type/Page>> endobj 796 0 obj <>stream Sorry, preview is currently unavailable. PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 2 OF 17 STEP 1: CALCULATION OF MINIMUM DIAMETER OF THE PIPE ASSUMING RECOMMENDED VELOCITIES. )p$5l?x The term that relates fluid density, velocity and viscosity and the pipe diameter is called the Reynolds number, named after Osborne Reynolds (1842-1912, of Owens College, Manchester, United Kingdom), who pioneered this technical approach to energy losses in flowing fluids circa1883. 5) Noise: High line velocities in case of piping carrying compressible fluids lead to high noise levels. endstream endobj startxref From point A, draw a horizontal line to the steam flowrate of 270 kg/h, and mark Point B. %PDF-1.4 1ExJ`@=6q `*-eY[1J({Z+:Q.TtSuW| mP~~w:{MG:1KE}1|;7uXp:'PX\&>*t#8s?G'$02v^61#]vc#?^8y A pipe with a bore of 130 mm is required; the nearest commercially available size, 150 mm, would be selected. The advantage of using these formulae is that they can be programmed into a scientific calculator, or a spreadsheet, and consequently used without the need to look up tables and charts. - Wet steam is delivered to the point ofuse. The following information isrequired. The heat lost by the insulated pipework was some 21% higher from the 80 mm pipeline than it would have been from the 50 mm pipework. In specific cases where pressure drop considerations are unimportant, velocities in excess of 75 m/sec, up to 100 m/sec may also be considered. As a result, there are numerous graphs, tables and slide rules available for relating steam pipe sizes to flowrates and pressuredrops. %(* dL4? 793 0 obj <> endobj Bernoulli relates changes in the total energy of a flowing fluid to energy dissipation expressed either in terms of a head loss hf (m) or specific energy loss g hf (J/kg). <> Select the point on the saturated steam line at 7 bar g, and mark Point A. 0000001465 00000 n In our case the flow is turbulent we can select the friction factor value from the graph, (Refer attachment 4- taken from CRANE hand book), f =0.02 PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 14 OF 17 Finding Z: From a piping isometric, Let us assume, Total pipe length = 95 m Pipe fittings: 90 degree elbows = 12nos. endstream 0000002445 00000 n AGEING: While sizing pipelines for water service, the likely increase in pressure drop with the ageing of pipe due to increase in pipe roughness, encrustation of pipe with scale, dirt, foreign matter, etc., should be considered. Consider the system shown in Figure 10.2.6, and determine the pipe size required from the boiler to the unit heater branch line. A lower pressure might be available at the point of use, which may hinder equipment performance. Empirical formulae exist for those who prefer to use them. 0000003046 00000 n 45 degree elbows = 2 nos. 1 Any non-insulated parts of the 80 mm pipe would lose 50% more heat than the 50 mm pipe, due to the extra heat transfer surface area. The same material may be used for condensate lines, although copper tubing is preferred in someindustries. 0000000768 00000 n Unit heater steam load = 270kg/h. Draw a horizontal line from the saturation temperature line at 7 bar g (Point A) on the pressure scale to the steam mass flowrate of 5 000 kg/h (Point B). From the knowledge gained at the beginning of this Module, and particularly the notes regarding the DArcy equation (Equation 10.2.1), it is acknowledged that velocity is an important factor in sizing pipes. 2999 Regardless of schedule number, pipes of a particular size all have the same outside diameter (not withstanding manufacturing tolerances). Using Figure 10.2.8, draw a vertical line from 450C on the temperature axis until it intersects the 50 bar line (Point A). % When the Reynolds number exceeds 4000, the flow is called TURBULENT. The loss in the total energy of fluid flowing through a circular pipe must dependon: u = The mean velocity of the fluid flow(m/s), = The dynamic viscosity of the fluid (kg/m s =Pas), italic-p - body text.jpg= The fluid density(kg/m). 3 0 obj 2. H\UtW9o$wn\ RHI%7B$AbGkc-RVG/izxRvE/j~ks9ACr3Fc|&q~13zMBf1pV+U ! All Rights Reserved. As a general rule, for turbulent flow with Reynolds numbers between 4 000 and 100 000, SI based friction factors will be of the order suggested by Equation 10.2.4, whilst Imperial based friction factors will be of the order suggested by Equation 10.2.5. The pipe size may be selected on the basisof: 2022 Spirax Sarco Limited. As previously mentioned, the friction factor (f) can be difficult to determine, and the calculation itself is time consuming especially for turbulent steam flow. Learn how we and our ad partner Google, collect and use data. In the United Kingdom, piping to EN 10255, (steel tubes and tubulars suitable for screwing to BS 21 threads) is also used in applications where the pipe is screwed rather than flanged. These have been tried and tested over many years, and which appear to give results close to the pressure factor method. IF NOT REPEAT THE PROCESS. Air Venting Heat Losses and a Summary of Various Pipe Related Standards, Previous - Introduction to Steam Distribution. In case of indoor piping where background PIPE SIZE & PRESSURE DROP CALCULATIONS Sheet 5 OF 17 noise is generally low, use an upper limit of 50 m/sec for steam velocity. % Refer attachment 3A for Viscosity of water and steam 3B for Viscosity of water and Liquid petroleum Products 3C for Viscosity of various Liquids 3D for Viscosity of gases and vapours Re = ((103 x 21.55 x 50 x 0.1985) / 2.936) = 72848.689 When the Reynolds number for a flow through a closed conduit is less than 2000, the flow is said to be LAMINAR. The following information is required, and the procedure used for the calculation is outlinedbelow. 4) Water Hammer & Surge Pressures: High line velocities result in significant pressure increases due to water hammer or surge action. QZ(E-W]^nhh7[DnxuSC From point B, project a line vertically upwards until it intersects 50 m/s on the steam velocity scale (Point C). The pressure loss bar/100 m scale reads about 0.9 bar/100 m. The pipe length in the example is 200 m, so the pressure drop is: Velocity (usually pipes less than 50 m in length). The value of Y may be interpolated for intermediate temperatures. 160. As the schedule number increases, the wall thickness increases, and the actual bore is reduced. These schedule numbers bear a relation to the pressure rating of the piping. GF(R/ 4Oe2=8+-v7[/yBcwSp}&#Z. 0000001775 00000 n owhS8$] 6YF!P\8\WzC\@lrI3z. 4WTac#u ;=I,ilWT@j{YwZ>5|S~qAk -=t1I;9=[;>{33Q_NQK^V(X.%+G+NT P~KrlGN5Vb;mhW 6Z"X]c{.4o WY?HuA.?7.S3Wn,rD]J?'tk"|>,ow++nrR}UTNiS {9F" !TREF*`WTf({hxREN\Ld A19E5 jDd?=Nu =c eJfp $; K_a { Pipe sizing is a crucial aspect of steam system design. The pipe roughness or kS value (often quoted as curly-e - body text.jpg in some texts) is taken from standard tables, and for commercial steel pipe would generally be taken as 0.000 045 metres. For Main Steam Line Let us assume, 1) Working fluid: Superheated steam 2) T=500C= 932 F 3) P=72.7 Kg/cm2 4) Flow rate=117 tones/hr =117000Kg/hr 5) Specific weight of superheated steam=21.55 Kg/m3 6) Velocity =50m/sec. STEP 3: CALCULATION OF THE PRESSURE DROP FOR THE SELECTED PIPE SIZE FOR THE RECOMMENDED VELOCITY. A similar pipe length, but with more fittings, would increase the allowance towards20%. Qp`#+E[eK'%$o"k^p4$1A! In this instance, revised length = 150 m + 10% =165m. From Table 10.2.2 (an extract from the complete pressure factor table, Table 10.2.5, which can be found in the Appendix at the end of this Module) PDF can be determined by finding the pressure factors F1 and F2, and substituting them into Equation 10.2.8.

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