1 PIPE STRESS - falatghareh.ir · PIPE STRESS Page 1 of 95 15/11/2002 Rev. 0 1 PIPE STRESS 1.1...

PIPING DESIGN LAYOUT TRAININGLESSON 1

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1 PIPE STRESS

1.1 PREFACE

This lesson will cover the procedures for simple stress analysis required when doing a layout study.Two things to keep in mind; first, use Fluor standards as a guide, and second, the guidelines mentionedin this lesson may be different than jobs you may have worked on in the past. Most clients have theirown engineering standards.

1.1.1 Lesson Objectives

Lessons provide self-directed piping layout training to designers who have basic piping design skills.Training material can be applied to manual or electronic applications. Lesson objectives are:

• To familiarize you with the stress requirements when making a layout.

• To know the different materials and terminology used when making a stress analysis (i.e.nomograph).

• To know the common stress considerations when laying out pipeways, pumps, vertical vessels,etc., avoiding major mistakes and costly changes, and to show you some of the pitfalls that causesthem.

• To familiarize you with Fluor standards on stress analysis. (Fluor standards are a guide; thestandards used on your contract may differ.)

1.1.2 Lesson Study Plan

Take the time to familiarize yourself with the lesson sections.

The following information will be required to support your self-study:Fluor Technical Practices. The following Fluor Technical practices/resources are included in this lessonguide:

000.250.2041, Plant Arrangement. Pipeway Layout - Allowable Pipe Spans000.250.2600, Exchangers - TEMA Nomenclature000.250.2601, Exchangers - Equipment Location and Piping Layout - Shell and Tube

Heat Exchangers000.250.9823, Co-efficient of Expansion Tables000.250.2220, Stress Design - Sketch Procedure000.250.2221, Stress Design - Sketch Information

It should take you approximately 30 hours to read the lesson plan and be prepared to take the test.

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If you have layout questions concerning this lesson your immediate supervisor is available to assistyou. If you have general questions about the lesson, contact Piping Staff - Stress Group.

1.1.3 Study Aid

Videos on Process Plant Layout & Piping Design (SPED) supplement your layout training. It issuggested that you view these videos prior to starting the layout training. You may check-out a copy ofthe videos from the Knowledge Centre (Library).

1.1.4 Proficiency Testing

There is a self-test and a test-grading master included enabling the designer to evaluate theircomprehension of this lesson.

TestingQuestions are true-false, stress calculating and manual fill-in.You are encouraged to use your lesson plan and any reference data during the self-testing.

1.2 THERMAL EXPANSION

Piping Designer Responsibilities

The Piping Designer is responsible for the layout, design, and support of all piping systems and is alsoresponsible for the following items, obtained by using the applicable sections of the Piping technicalpractices:

Locating supports, guides, anchors, compressor hold-downs, and hanger rods.

Providing prespring, cold spring, clearance required for line expansion, and additional line flexibility.

Transmitting and handling stress sketches in complete compliance with procedures outlined inPiping Engineering Practices.

Piping Designer is not responsible for the flexibility calculations or the validity of such calculations madeby the Stress Engineer. Designer is responsible for any calculations or flexibility analysis that wasundertaken and resolved without Stress Supervisor's approval.w

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1.2.1 How to find pipe expansion

Figure #1-01

In order to check the line spacing on the right, one thing we need to know is the thermal expansion.Clearance must be allowed for expansion so that lines will not grow into and damage each other.

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Solution Steps1.2.1.1.1 Write the formula for thermal expansion eL=∆

e - is called the linear co-efficient of thermal expansion. It's valuechanges with the type of material and the change in temperature. Thevalues of "e" we use are given in tables in the Refinery Piping Code andreproduced in this section, page 7. Refer to resource 000.250.9823

The units of "e" are inches per foot.L - is the original length of pipe at installation. In most cases this is at 70o

F, approximately. This is the installation temperature used in the codeexpansion tables. The units of L are in feet.

∆ is the Greek letter "Delta" used to represent the change in length; i.e.the expansion.

1.2.1.1.2 From the Piping Code tables, since "A" spec. Pipe is A53-B (this is carbon steel) and thetemperature is 600oF, e = .0460 inches/foot (per coefficient of expansion tables).

1.2.1.1.3 From the piping layout, L - 110 feet.

1.2.1.1.4 Substitute e and L into the formula. Your calculation will look like this:

∆ = eL c.s. @600oF∆ = .046 X 110∆ = 5.06 inches

For OSIP information refer to 000 250 9822 Properties of Pipe, Attachment 01, Attachment 02 andAttachment 03

1.2.2 Anchors

Definition:

An anchor is a mechanical connection (welded and/or bolted between a pipe (or exchanger, etc.) and astructure. The structure must be strong enough so that it cannot bend excessively under large forces.w

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1.2.2.1 Full Anchors

Definition: A full anchor will not permit the pipe to move or twist in any direction at the point it isanchored.

Figure #1-02

Types of Full Anchors 5A1, 5A2 for 2" and smaller pipe. 5DA15DA2 or 5DA3 will be used with a guide forlarger sizes. Bolted end of a shell and tubeexchanger.

1.2.2.2 Directional AnchorsDefinition: A directional anchor stops movement parallel to the centerline of the pipe, but permitssideways pipe motion.

Figure #1-03

Types of Directional Anchors 5DA1, 5DA2, and 5DA3.

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1.2.3 Guides

Definition: A guide stops sideways movement of a pipe, but permits movementparallel to the pipe's centerline.

Figure #1-04SupportsA pipe support prevents downward motion of a pipe. If the weight of the pipeacting down on the support is great enough, upward motion of the pipe may notbe possible.

EquipmentMost equipment is anchored to a foundation. Therefore equipment nozzles arealso anchors. Generally they are full anchors. The anchors are mechanicallyrigid but may have additional expansion when the equipment is hot. Even if theequipment is not bolted down, the weight may be great enough to make theequipment an anchor point.www.IranPiping.ir



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Problem

Figure #1-05

Find the thermal expansion of each unit header into the interconnecting pipeway on the right.

LINE ∆ = eL ANSWER

FH - 4" = 68' X .088 = 5.98"

R - 8" = 81.5 X .0362 = 2.95"

S - 6" = 83' X .0617 = 5.12"

L -10" = 80' X .0061 = .49"

These expansions are used with general note #2 on 000 250 9815 line spacing pipe for checking linespacing. Line spacing problems will be covered in more detail when pipeway layout is discussed.

Definition: Flexibility of a piping system is a measure of the amount of thermal expansion it can safelyabsorb. Points to remember:

1. The amount of expansion to be absorbed must be known before the flexibility can be checked.

2. The amount of expansion that is considered safe is dependent on the situation.

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How pipes flex when absorbing thermal expansion

Figure #1-06

Solid line is the cold position of the pipe.

Dashed line is the hot position of the pipe.

Expansion to be absorbed is given by the line movement.

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1.2.4 Concepts of Free Thermal Expansion

1. Free thermal expansion is not generally the same as line movement. (It is in this simple case.)

2.This method has its greatest advantage in complex piping arrangements.

3. When "imagining" movement, weight and friction do not exist.

4. This concept is the most useful tool to prevent piping flexibility problems, especially at plotdevelopment and for locating solid supports.

Calculating free thermal expansion

To find the "free thermal expansion" pretend only one end is anchored, find the movement at the otherend, assuming there is no friction and there are no guides.

Figure #1-07

The actual motion at a corner is not easily found if there is no anchor. The stress engineer should beconsulted to determine line expansion in critical cases.

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Figure #1-08

* The actual expansion in this direction can only be determined by the stress engineer. Freeexpansion is found by adding lengths in the direction being computed.

When piping reverses directions the pipe lengths subtract.www.IranPiping.ir



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Figure #1-09

* The actual expansion in this direction can only be determined by the stress engineer.

Using Coordinates to find free expansion:

The algebraic combination of lengths in any direction is the same as the difference in anchorcoordinates. (In all three dimensions, i.e., north, south and elevation).

The fastest way to find the free thermal expansion is to multiply the difference between the anchorcoordinates times the coefficient of expansion. This is where the method has its greatest advantage.

(Carbon Steel @ 300oF e =.0182)

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Figure #1-10North ∆ = 190' X .0182 = 3.46"East ∆ = 65' X .0182 = 1.18"

Expansion can be radially from the centerline or axially along the centerline from some "anchor point".Short vertical drops have little effect on horizontal movement. Ignore it in this problem.

Figure #1-11

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Answer

In the N-S direction the expansion to be absorbed is:

= eL (Coefficient of expansion X Length)= .046 x 30'= 1.38"

In the E-W Direction:

= eL= .046 x 20'= .92"

The location of the anchor needs to be considered in relation to the major piping systems (largediameter pipe, pipe coming from underground, etc.) When finalizing the layout and plot plan.

Relationship of expansion and flexibility requirements are set by the plot plan, since only the differenceis used to find expansion.

The Stress Engineer should be consulted in critical cases.

Now take about five minutes to calculate as before, except change the anchor end of the drum:

Figure #1-12

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Answer

In the N-S direction the expansion to be absorbed is:

= eL= .046 x 10'= .46"

In the E-W Direction:

= eL= .046 x 20'= .92"

The E-W expansion did not change from the previous example. The N-S expansion was reducedconsiderably by just shifting the anchor end of the drum.

Notice also that the free thermal expansion does not depend on the piping arrangement.

The free thermal expansion depends only on the relative locations of the anchor points. This is thegreatest value of learning the free thermal expansion concept, especially for the layout man who islocating equipment.

The second arrangement requires less flexibility (since there is less expansion to be absorbed) andhas the potential of saving pipe and fittings.

Review of Expansion

All thermal expansions are found using the same formula:

eL=∆

Actual expansions are measured from a full anchor or directional anchor to the point where it isnecessary to know the expansion.

When finding free thermal expansion, the lengths to use in the expansion formula are thedifferences between anchor coordinates.

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1.3 FORCE AND STRESS NOMOGRAPHS

Pipe routed in straight lines cost the least. Normally, pipe cannot be routed straight because of thermalexpansion.

Stretching a pipe even a small amount takes a very large force. Preventing pipe from expandingthermally takes an equally large force.

(Note: You will not be held responsible for knowing the following formulas).

Stress = AreaLoad

= AP

Allowable stress varies with material and temperature, but, are on an order of magnitude of:

(a) Pressure = 1,000 to 10,000 psi(b) Deadload = 1,000 to 10,000 psi(c) Thermal = to 20,000 psi

The material engineer checks pressure stresses when calculating wall thicknesses.

Dead load stresses are controlled by proper use of the pipe span charts and checked by the stressengineer when required.

Thermal expansion stresses are roughly determined by piping during the pipe study and finally checkedby the stress engineer.

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Tensile and Compressive Stress

Figure #1-13

Experiments on different materials at different temperatures determine safe stresses. These values aregiven in the piping code.

Strain (Stretching)

∈ is the "unit strain" and is found by dividing the total stretching by the total length being stretched.

Example:

Figure#1-14

inchesinch

100*1.*∈= = .001 * Must use same units of length

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1.3.1 Young's Modulus

E (Young's Modulus) relates the amount of strain (stretching) to the amount of stress (loading). It isdefined as:

E = ∈S

The value of E changes with material and temperature. The stress and strain are measuredexperimentally. E is calculated and is tabulated in the piping code.

E = 30,000,000 P.S.I. for Cold Steel

Normally designed anchors cannot stand large forces because the structure would bend first, and theanchor would not be effective Equipment shells would dimple before they would act as anchors.Expansions are absorbed by bending the piping system rather than compressing it.

1.3.2 Thermal Force Between Two Anchors

Figure #1-15

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Free Expansion eL=∆The force required to prevent the pipe from expanding is the same as the force required to stretch it anequal amount.

Since S = AP

and E = ∈S

and = )(12 inchestoconvertedfeetL

∆∈=

To find P (the Force),

P = SA = E ∈ A = E L12∆

A = E LeL

12A

P =12

eAE

Example:

For a 6" Sch. 40 Pipe at 300oF

P = 12

000,000,30..58.50182. psixinsqx

P = 253,890#

Nomograph A:

See Figure #1-16, Nomograph A

This Chart is based on formula (modified)3

12LEIP ∆=

This formula will not be used in the lesson.

Moment of inertia is the stiffness of object being bent based on its cross-sectional shape. This formulashows force is directly proportional to the deflection. Force is inversely proportional to the bending legcubed.

Size and schedule relates to moment of inertia. Lengths to be added are approximate. The forcefound in this way can differ greatly from a computer output, but is good enough for piping studypurposes.

The total free expansion between the two restraints (guide and anchor) is trying to grow outwards ineither direction simultaneously since it can't actually move at either end.

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1.3.3 Using the Force Nomograph

See 000.250.2230 Stress Design - LayoutAids for Rotating Equipment for examples

Examples

Figure #1-17Steps:

1. Align straight edge with nominal pipe size (6 in), pipe length in bending (20 ft) and mark point onpivot line.

2. Align point on pivot line with total thermal expansion (3.62 in) and read off thermal force (1500#).

The force against the anchor (indicated by the dotted arrow) is equal to but is pushing in the oppositedirection.

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Figure #1-18

Direction Expansion Leg ForceA 35 x .046 = 1.61 25.00 About 380#B 25 x .046 = 1.15 35.00 Less than 200#

Bending leg for T.F. (Thermal Force) B is the sum of lengths at right angles to the expansion in thedirection of B.

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Figure #1-19

FREE THERMAL EXPANSION∆ A = 15 x .0182 = .27 L = 15 T.F.A = 700#∆ B = 20 x .0182 = .36 L = 27 T.F.B = Less than 200#

Vertical force is not required in this example. Both vessel and pipe C.S. at 300oF 8" SCH. 40.

Radial expansion must be added for vertical vessel.

Anchor end of horizontal vessel must be taken into account. If the anchor end and slotted endwere reversed, then T.F.A. would be: ∆ A = (12 + 15) X .0182 = .49

Reversal of anchor end of horizontal vessel causes an increase in anchor force.

Anchor movements are okay to incorporate this way since shell material and temperature are thesame as the pipe.

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Figure #1-20

∆ A = 70 x .0321 = 2.25 L = 25 T.F.A = 2100#∆ B = 25 x .0321 = .80 L = 45 T.F.B = Less than 200#

The guide acts as an anchor for forces in "B" direction, but not in "A" direction.

If the bending leg is longer than those listed on the chart, a flexibility problem does not exist.

Figure #1-21

8" SCH. 40 ∆ A = 5 L = 60 T.F.A = 200#

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Find the Horizontal and Vertical T.F.

Figure #1-22

Force and expansion calculations are the same in plan or elevation.

1. Pump nozzle is not used for flexibility.2. Pump expansion is included in total expansion.3. Moving the anchor end is mandatory.4. Nozzle projections are not used for flexibility here. The stress engineer may include them.5. The piping in the example was dimensioned by roughly following 000 250 2040.

6. Clearances for access maintenance and insurance regulations generally set piping dimensions.The stress and force are checked afterwards, and flexibility is increased only if necessary.

7. Following the Fluor Standards is usually a good guide for stress problems because the stress grouphas already reviewed the standards.

Answer:Horizontal ∆ = .0182 x 25 = .46 L = 16.5

T.F. = 350#

Vertical ∆ = .0182 x 19 = .35 L = 13T.F. = 540#

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If the anchor end was toward the pipeway:

Horizontal ∆ = 15 x .0182 = .27 L = 16.5T.F. = 220#

Obviously it is better for the pump if the anchor is moved.

1.3.3.1.1 Add ALL bending legs at right angles to the expansion.

1.3.3.1.2 Thermal force will be calculated in only one direction, since the bending legs in the otherdirections are so much larger these calculations are unnecessary.

12" SCH. 30 S.S. @ 400 Degrees F.

Figure #1-23

Answer:

∆ = 55 x .038 = 2.09 L = 30I - 249 T.F. = 2100#Although forces parallel to the exchanger were not calculated, it should be noted, if a guide is added onthe long pipe run calculations might then be required. (Calculations by stress might be requiredbecause of limited forces at equipment nozzles.)

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1.3.4 Anchor Movement

Taking the difference between anchor coordinates does not work when portions of the system aredifferent temperatures and/or of materials with different expansion coefficients. Actual temperatureconditions are determined by the stress engineer using the line list, mechanical flow diagram andspecial conditions noted on the stress sketch.

When the equipment a pipe is anchored to is of a different material or at a different temperature, thefree thermal expansion is found by adding or subtracting "anchor movement" to the free expansion ofthe piping.

Example:

Figure #1-24

E-W Free Expansion

Free Expansion of Pipe = .0624 x 20 = 1.248"Vessel Anchor Movement - .0617 x 10 = .617"

= 1.865"

N-S Free Expansion

Free Expansion of Pipe = .0624 x 30 = 1.872"Vessel Anchor Movement = Zero

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Anchor Movement Problem:

Find the N-S and E-W thermal force.

Short pipeway drops (generally about 2'-6") have very little affect on flexibility and are ignored safely.In tight situations (pump calculations) they may be considered. The vertical force is not to becalculated.

Figure #1-25Answer:

N-S Expansion = 20 x .0182 = .364"L = 20 + 25 + 5 = 50T.F. = Less than 200#

E-W Expansion = 70 x .0182 = 1.274"Boiler Anchor Movement = .0362x15 = .543"

Difference = .731"

L = 20 + 5 = 25T.F. = Less than 200#

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Explanation of Bending Stress

Diagram of Tensile Stress

Figure #1-26

Diagram of Bending Stress

Figure #1-27

Strain increases From the Center Outwards. Therefore the Stress is Proportional to the Pipe O.D. for aGiven Amount of Curvature

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Example

Figure #1-28

The formula for calculating stress is:2

3L

DES ∆=

Where:S = Stress in PSIE = Modulus of Elasticity∆ = Thermal GrowthD = Pipe DiameterL = Length of Bending Leg

Guides and anchors have the same effect as in the force calculations. Small diameter piping becomesover stressed before large forces are developed. Large diameter piping creates excessive forcesbefore the piping becomes overstressed.

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1.4 PIPEWAY STUDY

1.4.1 Basic Pipeway Layout

Basic Pipeway Layout Requirements

1. Positive control of thermal expansion for establishing line spacing and for appearance.

2. Minimizing structural forces for economy of steel design and making the anchors more effective.

3. Conservation of berthing space by the use of expansion loops, when required.

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Figure #1-30

Figure #1-31

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Pipeway Layout Steps

1. Determine approximate length of pipeway from plot plan.

2. Establish line sizes and temperatures.

3. Establish preliminary berthing.

4. Anchor all lines near the center of the pipeway.

5. Calculate line spacing at the corners.

6. If the line spacing is wasting berthing room at the turns, determine which lines are giving the mosttrouble.

7. Move the anchors of these lines (one line at a time) closer to the corners. (The line will now havetwo anchors).

8. Place one or more loops between these two anchors.

9. Size the loops to fit the available space.

10. Finalize berthing.

11. Check the anchor forces.

12. Send finished layout to stress for calculations of exact forces to be transmitted to structural, andcheck of loop design.

Lines that will require the biggest loops should be grouped near the outside, with lines requiring smallerloops progressing toward the center. Consideration should be given to placement of small diameterlines where they can get additional support from larger, cooler lines.

If a relief header needs a loop, it must be berthed so as not to interfere with other lines, since the reliefheader can not be pocketed and must slope.w

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Line Spacing with no Flanges near the Corners

Figure #1-32

When there are no flanges between the corner and first guide or anchor on two adjacent lines, linespacing may be based on O.D. of pipe or insulation to O.D. of insulation plus expansion plus 1"clearance.

Where flanges are near pipe intersections the spacing is based on flange diameter rather than O.D. ofpipe. Usually spacing is calculated with one line hot (operating) and one line cold (not operating).

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Bowing of "L" Shapes

Figure #1-33

Bowing:

The bowing can be much greater than the actual movement ( ∆ ) at the corner.

Distances between guides and anchors around corners will limit the bowing to no more than the ∆ atthe turn, eliminating calculations.

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Problem

Assuming no extra space is available for thermal expansion, determine which lines require loops,based on the line spacing at the east end of the pipeway under consideration.

Figure #1-34

1. Set standard spacing.

2. Check clearance for expansion.

3. Decide which lines require lops.

Do not make any scale drawings!Make a freehand sketch of the section.

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1. Set Standard Spacing:

Figure #1-35

A = 41

2 " + 2" + 1" + 21

10 " = 43

15 " → 16" or 21

4 " + 1" + 3" + 7" = 21

15 " → 16"

B = 7" + 3" + 1" + 21

4 " = 21

15 " → 16" or 21

10 " + 1" + 41

2 " = 43

13 " → 14"

C = per 000.250.9815 → 12" Note: always use the larger dimension

D = per 000.250.9815 →19"Total 63"

See 000.250.9815, Dimensional Chart Line Spacing - Pipe

2. Check Clearance for Expansion (Check Flg. Location)

4" IH ∆ = .0501 x 375' = 18.79" WAS

A = 41

2 " + 2" + 18.79" + 1" +3" +7" = 34.04" → 35" 16"

8" IH ∆ = .0362 x 350' = 12.67"

B = 7" + 3" + 12.67" + 1" +41

2 =25.92" → 26" 16"

4" ∆ = .0362 x 350' = 12.67"

C = 41

2 " + 5.29" + 1" + 183

5 " =13.92" → 14" 12"

10" ∆ = .0061 x 350' = 2.135"

D = 83

5 " + 2.135" + 1" + 43

11 =20.26" → 31" 19"

Total 96" 63"All four lines on the left will require loops, if 33" additional berthing space is uneconomical to obtain.

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1.4.2 Locating Loop Anchors (After the Need for a Loop Has Been Established)

4" S.S. @ 500OF - 2" IH

Figure #1-36

Allowable expansion at the right end, without increasing line spacing =

"75.0"412"2"1"3"7"16 =−−−−−

The maximum distance the anchor may be from the corner is found by dividing the allowable movementby the coefficient of expansion.

Left End L = 6 ÷ .0501 = 120 Ft.Right End L = 0.75 ÷ .0501 = 15 Ft.

The loop(s) will have to absorb at least 565 Ft. x .0501 = 28.31" of expansion.

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Locating Pipeway Loops

Ideally loops shall be located centered between anchors with equal legs on either side of anchor.

Figure #1-37

When this isn't practical make legs on either side of anchor as equal as possible.

Figure #1-38

Friction Forces are determined by the number of pipe supports a line crosses. By making these legsequal, the forces at the anchor should remain nearly balanced.

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1.4.3 Multiple Loops

More than one loop may be required when:

(a) It is impossible to make branch connections flexible enough.(b) Spacing between branches and neighboring lines or steel is limited.(c) When loop becomes too large to support or fit into space available.(d) Anchor forces become too unbalanced and steel cannot be economically braced.

Figure #1-39

If this situation is encountered, check with your supervisor. He will check with stress and structural andtogether a solution will be found. If it is multiple loops instead of added bracing, then:

Figure #1-40

Smaller loops required, but more fittings and welds are used.

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Multiple Loops

More than one loop may be required when:The forces required to bend the loop are too great, and the anchors cannot be economically reinforced.

Figure #1-41

Figure #1-42

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Maximum unbalanced loads should be no more than 2000 lbs.

Figure #1-43

(TF1+FF1) - (TF2+FF2) = Total Unbalanced Load less than 2000 lbs

To insure a thermal force is not balancing a friction force, check separately that friction and thermalforces balance to within 2000 lbs.

Placing Loops

1. Loop width should always be based on utilizing existing supports.

2. Thermal expansion must be allowed for when spacing adjacent loops.

3. Loop width does not have to be near 20 feet just because the loop nomographs happen to use thatnumber. Loop width has only secondary effect on results.

4. Minimum loop height depends on the berthing of the line with respect to the location of the loopsupport.

5. Loops cannot extend too far beyond an existing support or the overhang will cause the loop to"loose its balance." This sets the maximum allowable loop height.

6. The first two points have more influence on loop design than stress formulas, from the piping pointof view.

7. The practical problem of sizing loops at a particular bay is finding which has to be the biggest andsecond biggest, etc.

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Method for Sizing Pipeway Loops

1.4.3.1.1 Anchor lines near their center. Determine which lines require loops by checking the allowableexpansion at each end of the run. If each end will absorb the resulting expansion, no loop isrequired, usually. If the line spacing cannot be adjusted to take the movement, a loop isrequired.

1.4.3.1.2 Determine which of the lines requiring loops need the largest loop, second largest, etc., bythe following:

1.4.3.1.2.1 Multiply the total expansion of each line between its proposed anchors by the pipe'smoment of inertia (E). (The stiffness of a line is measured by its "Moment of inertia.")

1.4.3.1.2.2 The line with the largest of these calculated numbers will require the largest loop, the nextsmaller number, the next smaller loop, etc.

1.4.3.1.2.3 The above rule does not check stress. This is checked after the loops are roughlydimensioned.

1.4.3.1.3 Check the space available for the loops. Make sure that the lines requiring the biggest loopsare berthed near the edge of the pipeway opposite the top of the loop. Fit the loops betweentwo pipe supports using minimum spacing plus allowance for line expansion and bowing.Make the loops as wide as possible, but keep the height to a minimum. If stress or force isextremely high, check with stress engineer for height of loop.

Note: Usually the lines with the most expansion areberthed on the edge of the pipeway so that thethermal expansion grows away from the other pipesat the corners, even if the line doesn't require thelargest loop.

1.4.3.1.4 Send finished pipeway to stress for accurate calculation of anchor forces for transmittal toStructural and accurate evaluation of stresses in the piping.

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Loop Sizing Example

Note: All Pipe is Standard Wall

Figure #1-44

Calculations:

Pipe Ip X ∆ Loop Order

10" 161.0 X 5 = 805 2 4" 7.23 X 11 = 80 4 2" .666 X 15 = 10 516" 562 X 4 = 2248 1 6" 28.1 X 6 = 169 3

This calculation also shows that the 16" line should be berthed where the 6" line is, the 10" line shouldbe where the 16" is, and the 6" line should be where the 2" line is. Notice that this is also the bestarrangement for the beam to carry the weight.

Pipe bridges may be used to absorb thermal expansion, reducing the number of loops required.

Place anchors the same way as normal loop anchors are placed.

On longer than normal span, loop bowing may cause the pipe to lift off intermediate support causingoverspan. Check with stress during layout.

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Pipeway Drops

Short drops are very rigid and can be ignored (depending on pipe size).

Longer drops are flexible and must be anchored to control the amount of expansion they absorb, toprevent overstress.

These requirements vary with pipe size and the location of the drop and anchors, so check with stressduring layout.

1.4.4 Locating Friction Balance

Locating the Friction BalanceOf Liquid Headers That Change Size

Figure #1-45

The anchor is placed at the lines "center of gravity". Find the total pipe weight and divide by two.

6" STD = 31.5#/ft. X 100 ft. = 3,150 lbs. 10" STD = 74.6#/ft. X 100 ft. = 7,460 lbs. 16" STD = 141.7#/ft. X 100 ft. = 14,170 lbs.

TOTAL = 24,780 lbs. divided by 2 = 12,390 lbs.

This is the weight of 12,390 lbs. = 87.4 ft. of 16" STD pipe + water.141.7#/ft

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Locating the Friction Balance of Vapor Headers That Change Size

Steam headers and flare headers should have their anchors located without considering water in theline. Include insulation, however, if present. Using the last example:

Figure #1-46

6" STD = (19.0#/ft. + 3.28#/ft.) X 100 ft. = 2,228 lbs. 10" STD = (40.5#/ft. + 7.07#/ft.) X 100 ft. = 4,757 lbs. 16" STD = (62.6#/ft. + 14.6#/ft.) X 100 ft. = 7,720 lbs.

TOTAL = 14,705 lbs. divided by 2 = 7,353 lbs.

This is the weight of 7,353 lbs. = 95.2 ft. of 16" STD pipe + 3" IH. (62.6 + 14.6)

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Offsite Pipeway Arrangements

Figure #1-47

Alternate routing shortens each individual run so that the number of loops can be minimized if linespacing is increased a little. Loops for offsite flare headers can be avoided in the same way.

Flare Headers in Unit Pipeways

Due to the no - pocketing requirement of flare header design, berthing locations and other layoutdifficulties, flare headers should not be looped in unit pipeways.

Figure #1-48If expansion is too great, the anchor may have to be moved back. If too great, the unbalanced frictionmay be reduced by using Teflon shoes on the heavier side

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1.5 SUPPORT AND PIPE SPANS

1.5.1 Allowable Pipe Spans

The allowable pipe span depends on the following:

1. Stiffness of the Pipe

2. Weight of the Pipe

3. Weight of the Contents

4. Weight of the Insulation

5. Allowable Stress of Pipe Material at Design Temperature.

6. Allowable Sag for Appearance, and Adequate Drainage.

When using the pipe span chart, allowance must be made for deviations from the conditions given onthe chart. In special case (such as plastic pipe), see stress engineer for allowable span information.

Problem

Figure #1-49

Using the pipe span chart 000.250.2041, find the maximum support spacing if pick-ups cannot be used.

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Answer:

4" SCH 40 @ 600oF = 27'-0"3" SCH 40 @ 200oF = 25'-0"2" SCH 40 @ 200oF = 19'-0"1" SCH 80 @ 150oF = 17'-0"

Answer = 17'-0"

Figure #1-50

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1.5.2 Dead Load Calculations

DEAD LOAD CALCULATIONS (Approximate)

Uniform Loads:

Figure #1-51

W = Total weight between supports (pounds)

w = Weight per foot of pipe (include water for test loads) (include commodity and insulationfor operating loads)

l = Distance between supports (in feet)

For weight of pipe and water per foot see 000.250.9822 Attachment 1.

Various other charts can be used for weight of insulation, valves and fittings.

Weights at each support are calculated using half the weight from either side of the support. Generally,fittings can be calculated as straight pipe unless they are especially heavy.

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Dead Load Calculations (Approximate)

Concentrated Loads:

Figure #1-52

W = Total weight of in-line item (pounds)

Such as: Valves, flanges, specialty in-line items, and strainers, weight of branch resting onheader.

Weights of control valves, PSV's, other instruments and specialty items can, often, be obtained fromvendor drawings. The loads should be added to stress sketches when available.

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Example Problem: Dead Load Calculation

Estimate the load on the platform:

Figure #1-53

Header = 6" Sch. 40Commodity = oilSpecific gravity = .8Insulation = 2" thick calcium silicate (4.57#/ft)

Branch = 4" Sch. 40Commodity = oilSpecific gravity = .8Insulation = 1.5" thick calcium silicate (2.55#/ft)4"-300# flange = 29#

Problems on dead load are worked from the top downwards. Loads estimated should have 20% safetyfactor added. w

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Answer

Break the problem into simple sections and add the results:

4" Branch Uniform Case

Figure #1-54

4" Sch. 40 pipe = 10.79 #892

75.17'102

=×=w

Water X 0.8 = 4.41 1.5" insulation = 2.55 W = 17.75#/ft.

Plus: Concentrated Case4"-300# gate = 215#(2)4"-300# w.n. Flgs. = 58#

w = 273#

Figure #1-55

Solve for load at the header end only: #21810

82731

=×=Wb

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Plus: Concentrated Case

Figure #1-56

Total load the header must support equals: 89# = Hor. pipe load218# = CV load

W = wl= 17.75#/ft. X 8' = 142# 142# = Vert. pipe load449# = Total bend leg load

at header

6" Header Uniform Case

Figure #1-57

6" sch. 40 pipe = 18.98 #3362

'2056.332

=×=w

water X 0.8 = 10.01 2" insulation = 4.57

w = 33.56 #4202

'2556.332

=×=w

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Concentrated Case

Figure #1-58

Branch = 449#

5HR1-6 load =l

Wb =

'25'20#449 x= 359#

Total 5HR1-6 load is: 336# +420# +359# 1115# plus 20% = 1338#

Note: Allowable load for 5HR1-6 is 1500# per technical practice 000.250.2154., Piping StandardDrawing - Hanger Rod

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1.5.3 Support Location

Figure #1-59

The sag between two widely spaced supports may cause the pipe to lift off improperly located supports.

Try to equalize the spans on either side of a support, when possible, balancing loads.

Figure #1-60

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PROPER LOOP SUPPORT

Figure #1-61

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Figure #1-62

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Figure #1-63

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1.6 EQUIPMENT

Equipment must be considered in stress analysis. Anchor locations, temperature, shell material, nozzleprojection and physical dimensions all effect stress calculations and need to be transmitted to stress.

1.6.1 Horizontal Vessels

Figure #1-64

*Give operating and design temperature of process inlet and outlet lines. Do not use vessel designtemperature.

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1.6.2 Exchangers

EXCHANGER AVERAGE SHELL TEMPERATURE

Figure #1-65

Average temperature for finding anchor movement is:

800oF+400oF2

TAverage = 600oF

The stress engineer will determine the average temperatures and resulting expansion from theinformation on the stress sketch.

"Shell and tube" exchangers are used to heat and cool a commodity stream, using another commodityisolated in tubes.

Generally the flow through the shell and channel will flow in opposite directions. temperatures andpressures vary at each nozzle. See 000.250.2601, Equipment Location and Piping LayoutShell and Tube Heat Exchangers, for layout details

See Figure#1-66, Exchangers - TEMA Nomenclature

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Figure #1-67

Stress Requirements

1. Shell Material

2. Process Temperatures - both Design & Operating

3. Type of Flow Through Exchanger (Single Pass)

4. Dimensions shown Above

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1.6.3 Vertical Vessels

Note: Use operating temperatures of outlet nozzles only for figuring vessel growth. Do not use vesseloperating temperature.

Expansion occurs both from the tangent line (up or down) and radially from the center of the vessel.Temperatures can vary greatly from the bottom to the top of a tall vertical vessel.

Figure #1-68

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On tall vessels piping will generally be supported and guided off the vessel. Different temperaturesinside the vessel and pipe can cause them to expand at different rates.

Figure #1-69

Care should be taken placing manifolds at the based of vessels. If they must be located at the base ofvessel, the weight must be carried by the vessel support and a base guide used in place of a fieldsupport.

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Figure #1-70

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1.6.4 Pumps (Forces)

Pump Vendors will accept only limited forces and moments at their suction and discharge nozzles.When more than one pump is fed by a single source, one pump can be running (Hot) while the other isshutdown (Cold).

Figure #1-71

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Figure #1-72

Note:

Not only pumps, but also all valve piping systems must be analyzed for all hot-cold temperaturecombinations that are possible.

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Figure #1-73

For a given pipe size and temperature, the horizontal forces are twice as great as in sparing (hot-cold)service.

If hot-cold operation is also occasionally possible, it must also be allowed for during layout.

Information on the pump operation must be included on the stress sketch if other than hot-cold.

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Figure #1-74

N-S force for either pump (during hot or cold) is found using total N-S expansion with bending leg equalto A+B+D.

Vertical force between vessel and pumps does not depend on hot-cold.

Vertical force is found using total expansion between pump support and vessel support with bendingleg equal to C. Since the force pushes down halfway between the pumps, divide by two to find theforce at each pump. Add this force to the hot-cold vertical force, which is occurring simultaneously.

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Figure #1-75

Find forces between pt. "O" and pt. "E" in the usual manner.

The forces calculated are then added to the previously determined loads at one pump.

(Do not divide the forces between the two pumps, except for symmetrical piping.)

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Figure #1-76

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Example Calculation: Symmetrical Pump Suction

Figure #1-77

Forces-Between Pumps Between Vessel and PumpVertical Vertical

∆ = 8.5' x .0141 = .12" ∆ = 18' x .0141 = .254"T.F. = About 390# T.F. = 250# 2 = 125# per PumpBending Leg = 10'-0" Bending Leg = 15'-0"

East-West North-South

∆ = 5' x .0141 2 = .035" ∆ = 15' x .0141 = .212"Use 3 x .035 on Chart = .105" T.F. ‹ 200# per PumpChart Force = 1100# Bending Leg = 19'-0"T.F. = Chart Force = 370#Bending Leg = 7'-0"

If the nozzle size in this example decreases to 3" the allowable thermal force drops from 800 (4"x200#)to 600 (3"x200#).

If the temperature increases the previous example will not work. Additional leg must be added betweenthe pumps.

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Figure #1-78

6" sch. 40 C.S. 600oF design

Vertical Forces (Spare Cold) East-West Forces (Spare Cold)∆ = 8.5 X .046 = .39 ∆ = 5 X .046 = .23 2 = .12T.F. = 480# T.F. = 530#Bending Leg = 14' Bending Leg = 9'

Proper alignment of piping at pumps is critical. Foundations can settle (actually, sinking into theground). To avoid excessive forces, pipe supports generally will be tied into the pump foundation orsprings will be used. Sometimes, several pumps will have a common foundation or will have piles thatlimit settlement.

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See Figure #1-79, Basic Support Principles

Figure #1-80

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Pedestals off the pump base plate support pumps. Thermal growth occurs between this point and thesuction and discharge flanges.

Figure #1-81

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There are various kinds of centrifugal pumps; the main difference that effects piping is the location ofthe suction and discharge nozzles.

Figure #1-82

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When valves are located directly above a nozzle, springs are often used to reduce the loads on thepumps. Pumps should be located where they can be easily supported, usually, under or near the edgeof a pipeway.

Figure #1-83

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Figure #1-84

On steam turbines: As with pumps where differential settlement can occur, foundations for supportsmust be integral with the equipment foundation. Steam supply and exhaust lines must be supportedindependently from the turbine nozzle so that the flange bolts can be removed and the flange alignmentwill not change. See standard 000.250.2352, Pump Piping (Steam) Turbines and ReciprocatingPumps, for typical piping arrangements at steam turbines.

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1.6.5 Air Coolers (Fin Fans)

Air coolers are generally located above pipeways to conserve space but they can be located at grade.Air coolers should be grouped together when practical to share a common support structure. Aircoolers used in vessel overhead condensing service needs to be free draining and piping often needsto be symmetrical (see standard 000.250.2602, Forced Draft and Induced Draft Air CoolerArrangements).

Figure #1-85

The temperature of the upper surface of the header box is the same temperature as the inlet header,and the temperature of the lower surface of the header box is the same temperature as the outletheader.

1. Gap clearance must be checked. If insufficient, upper and lower headers may be cold sprung,or the gaps may be increased. Piping and stress will squad check the vendor drawings.

2. Dead loads must be given on squad check. This is critical especially when vendor platforms areused for any additional support of risers, etc.

3. Check with stress engineer for minimum dimension during early layout.

4. Four nominal branch diameters or 2'-0", whichever one is longer, unless otherwise directed by astress engineer. This length may be required for field to bend and allow for flange mismatchdue to fabrication tolerance.

5. If reinforcing pads are required for pressure, it may be more economical to increase the header

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wall thickness. Check with the stress and material engineers.

Figure #1-86

1. Additional steel may be required. Check with stress engineer early on in layout. If a dummysupport cannot be used, a solid support may be required level with top of fin fan support. Aspring may be required if supported elsewhere.

2. Dummy flexibility helps absorb vertical expansion dummy must be sized correctly to carry theweight.

3. Provide flexibility for vertical expansion, shoe at P.S. Col. may be removed in limited cases.

4. If this dimension becomes too great the piping may become unbalanced and required additionalsupport.

AIR COOLER PROBLEM

See Figure #1-87

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Question:1. Pipe Expansion ______________________2. Total Movement _____________________3. Minimum Flex Leg @ 15,000 PSI Stress __________________________4. Minimum Flex Leg @ 1600 Force _______________________________5. Maximum Span Chart Recommendation __________________________6. Thermal Force _______________________7. Find Min. Dimension __________________8. Minimum Dead Leg Required______________________9. Dead Load @ Nozzle________________________10. Dead Load @ Nozzle________________________

Sample Calculations

1. Pipe expansion = 70' x .014"/ft = .98.

2. Total Movement = 1.5" - .98" = .52" net.

3. Flex leg required at 15000 psi stress = 23 ft.

4. Flex leg required at 1600# force = 30 ft.

5. Span chart recommends 47'-0".

6. Thermal force = 1600#.

7. This dimension should be approximately 28.3' = 302 ft - 102 = 28.3 ft

8. ∆ = 10 ft. (.014 - .0061) = .079" leg required = 4 ft.

9. =+2'3

2'5

4' x 182 lbs/ft2 = 728 lbs

4" - Sch.40 (2' X 16.3# = 33 lbs)4" - 150# W.N. Flg. = 17 lbs728 + 33 + 17 = 778 lbs = Load on all Nozzles

10. (30/2 + 5' (between fittings)) x 182 lbs/ft. = 1820 lbs = additional load from overhead line.The load at these nozzles is 1820 lbs + 778 lbs = 2598#. A vendor will accept this load (2598 lbs)if negotiated prior to award of contract.

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1.7 PIPING DESIGNER STRESS RESPONSIBILITIES

1. Check flexibility and support of all lines by the rule of thumb method and/or by inspection duringlayout.

2. Recognition during layout of stress problems that require consultation with these stressengineer.

3. Submitting lines for stress analysis as required on the line list and in accordance with000.250.2210 of the piping design guide.

4. Submitting additional lines for analysis that fail the rule of thumb methods.

5. Submitting required information on stress sketches.

6. Initially locating:

(a) Anchors(b) Guides(c) Hangers (Check with Stress Engineer for Spring Requirements)(d) Supports (Check with Stress Engineer for Spring Requirements)(e) Loops(f) Expansion Clearances (Including Bowing Effects)(g) Cold Spring for Line Spacing

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1.7.1 Stress Sketch Requirements

Figure #1-88

1. Locate equip. anchors and give info. for calculation of shell temp. (draw outline on stress sketch orsubmit Xerox of 8-1/2" x 11" vendor drawing).

2. Give dimension to the nearest foot (or exact if known).

3. Basic dimension info. same as M.T.O. sketch.

4. Add support location to spool (in red on blueline, pencil original).

5. Use to represent pipeway type support.

6. Locate FS or HR (do not show as a pipeway type support.)

7. Locate support clips (even for carbon steel spools).

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1.7.2 Code Requirements (From ANSI B31.3-1993 Page 41)

The layout and design of piping, including supporting elements, shall be directed toward preventing thefollowing:

1. Piping stresses in excess of those permitted by this code.

2. Leakage at joints.

3. Excessive thrusts and moments on connected equipment (such as pumps and turbines).

4. Excessive stresses in the pipe supporting (or restraining) elements.

5. Resonance with imposed fluid-induced vibrations.

6. Excessive interference with thermal expansion and contraction in piping which is otherwiseadequately flexible.

7. Unintentional disengagement of piping from it supports.

8. Excessive piping sag in piping requiring drainage slope.

9. Excessive distortion or sag of piping (e.g. thermoplastics) subject to creep under conditions ofrepeated thermal cycle.

10. Excessive heat flow, exposing supporting elements to temperature extremes outside their designlimits.

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1.8 GENERAL DESIGN INFORMATION

Recommended Method of Locating Piping Support Points

The primary objective is to obtain practical support point locations compatible with the structures normalto the plant, thereby permitting pipe line routing to be finalized as far as possible during study. Thematerial presented here is primarily for the guidance of the piping designer, detailer or checker andtherefore is limited in scope and subject to changes which will occur when the piping system isanalyzed for flexibility stresses and dead weight loading. Major changes should be avoided withapplication of the following general rules.

1.0 Pipe spans should not exceed the recommended spans as shown in the PDG and asmodified by the notes. Lines at temperatures in excess of those listed may require severelyshortened spans and the table does not apply to lines which may vibrate from mechanicalexcitation, pressure pulsation or mixed phase flow (flashing).

2.0 Temperature growth or contraction must be computed to determine the type of supportrequired. Assumptions that a line is supported properly by rigid or non-elastic supports createa major source of problems. These problems will generally be eliminated if the thermalbehavior of the line is properly evaluated during study. A line that grows off a support is notproperly supported, making it necessary to use an overhead type spring support, or in limitedcases the application of prespring might suffice.

3.0 Support points should be located directly over or under major weight concentrations occurringin vertical lines, and as close as possible to weight concentrations in horizontal lines in orderto attain what is called balancing moments. Dummy supports are to be avoided if reasonablypossible. For individual cases we prefer supports located in a manner that will take intoaccount the type of equipment as listed in the following groups.

3.1 Inlet and outlet risers from top nozzles on pumps.

3.1.1 Ambient temperatures with dead weight on nozzles less than 200 lbs./nom.in. with a maximum of 2000 lbs: 75% of normal span length is permittedadding length of riser and horizontal run, otherwise additional supportrequired. Cast iron pumps 50#/nominal in.

3.1.2 Lines 150oF to 300oF: Subject to flexibility analysis, weight and expansioneffects may permit 75% span as above to non-elastic support if prespring iseffective. To be safe, locate support point directly over riser with 3'-6"minimum clearance from top of line to underside of supporting structure.

3.1.3 Lines 300oF and over: Locate support point directly over riser with sameminimum clearances as above. Where clearances are less it may be

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possible to employ a riser clamp directly below the elbow weld, plus twospring hangers. The line should be reviewed with the Stress Group duringlayout. Dead weight loading will be severely restricted.

3.2 Side inlet and outlet nozzles on centrifugal pumps or compressors.

3.2.1 Ambient temperatures: Risers should be supported from below with 75% ofnormal span permitted like Item 3.1.1.

3.2.2 Lines 150oF to 300oF: Base support usually is sufficient but a spring may berequired if equipment expansion causes large expansion bending momentsto be imposed on the equipment. Normally 75% of span is permissiblesimilar to Item 3.1.1, to a non-elastic pipeway support point. Flexibilityanalysis may require pipeway support point to be an overhead spring,particularly on line sizes 10" and over. Clearances should be based onPDG spring hanger clearance table.

3.2.3 Lines 300oF and over are generally subject to the same conditions as 3.2.2for lines up to and including 6". The line routing should be reviewed duringlayout with a representative of the Pipe Stress group.

3.3 Vertical Vessel Piping

Piping risers on even low temperature vessels may cause support problems becauseof steam out conditions for maintenance and inspection. Vertical vessel growth isfrequently a matter of computing section by section because the temperature may varyfrom 650o or 700o in the reboiler zone to 200o or less in the overhead vapor zone. Thevessel may actually be two or three separate vessels stacked and not alwaysoperating at the same time. It may be a packed column subject to high temperaturesduring regeneration.

Intelligent arrangement of the piping requires some familiarity with the operatingsequences, which is obtained by experience or consulting with the Process orInstrument engineers. When the operating temperature conditions are determinedand type of commodity flow such as vapor, liquid, mixed or flashing mixtures, thenlines are ready to be routed for proper support and flexibility. The following pointersshould help to avoid problems serious enough to cause reorientation or major pipinglayout changes:

3.3.1 Heater to vessel feed lines. These lines are frequently subject to what iscalled mixed phase flow or partial vaporization and therefore subject tovibration. They should be given top priority study-wise due to the priority ofthe heater planning. Pressure drop is usually critical which, together withthe frequent need for alloy piping because of temperature, make optimumrouting an economic necessity. Spring hangers may be an absolute

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necessity and require an overhead structure. Hydraulic rubbers may berequired if the line is resonant with the heater pulse so line routing shouldbe in a manner which permits minimum shock absorber installation eitherinitially or later in the field if vibration develops. Predicting resonance onthese lines is practically impossible and controlling it after start-up, if andwhen it develops, can be quite expansive if the line is not routed reasonablyclose to structures or equipment which can be utilized.

3.3.2 Overhead line from vessel to condensers: This is usually one of the largest,if not the largest, line attaching to a vessel. The trend has been for moreapplication of air coolers to perform the condensing operation, which cancreate a major support problem. The vertical expansion of the vesselfrequently is large, exceeding the compensating growth of the line by morethan one inch. Routing the line down the side adjacent to the condensermay not be the most economical if lengths and elbows have to be added forflexibility reasons, then spring hangers have to be added for unbalancedloads and line stability. To further complicate the problem, relief valves aresometimes added on this line to a blowdown system, linking the flexibility ofboth systems and adding a weight concentration with no visible means ofsupport, because the line is ten feet or more above the nearest availablestructure. The route that appears shortest sometimes turns out the longestunless temperature differential growths are evaluated.

3.3.3 Vessel reflux lines: These lines are normally the smallest line on the vesselsand consequently considered quite flexible. The problem here is createdwhen a control valve assembly is located directly below the nozzle andadjacent to the vessel at grade. Due to the relatively low temperature ofthese lines, the bottom of the Control Valve loop is pulled up over 1-1/2", sothat special guides and spring supports must be detailed if the C.V. manifoldis left in this location. Relocating the C.V. manifold below the pipeway runavoids this problem, or as an alternate, locating the manifold on vesselplatform close to the reflux nozzle. The alternate location on the platformmay or may not be approved by the Instrument or Process engineer if hethinks hand operation of the bypass valve makes it necessary to locate atgrade because of fluctuating operations. It is a matter of opinion andoperators' methods, however, and worth consideration, as automateddesign is becoming more reliable.

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1.9 PUMPS, TURBINES AND COMPRESSORS

EQUIPMENT

1.9.1 A. Pumps

1. Pumps and rotating equipment in general must be considered more delicate than vessels,exchangers and other units that are not constructed with internal moving parts. Forces andmoments on these items must be kept within reasonable limitations to insure proper operations.Any wrap or distortion of the pump shell or support base may cause the impellers to bind andconsequently require shutdown of the plant with extensive repair of the pump or completereplacement.

2. Pumps - Supporting Requirements

With vertical risers from top nozzles (inlet or outlet).

(a) On cast steel pumps at ambient temperatures to 150oF, limit the dead weight on nozzles tothe lesser of 200 lbs./nom. inch of nozzle size or 2000 lbs. On cast iron or aluminum pumpslimit the dead weight load to the lesser of 50 lbs./nom. inch of nozzle size or 500 lbs. Alsolimit the unsupported span length (including the length of the riser) to 75% of the normalspan.

(b) At temperatures of 150oF to 300oF weight and expansion effects may permit handling similarto the above, however it is best to plan a support point directly over the riser with a 3'-6"minimum clearance from the top of line to the underside of the supporting structure.

(c) Lines 300oF and over: Locate support point directly over riser with same minimum clearanceas above. Where clearances are less it may be possible to employ a riser clamp directlybelow the elbow weld, plus two spring hangers. The line should be reviewed with StressGroup during the piping study. Dead weight loading will be severely restricted.

3. Pumps - End or side suction - Side discharge - Supporting

(a) At ambient temperature of 150oF: A base support will take care of the dead weight loading;however, the unsupported span must be limited to 75% of normal span.

(b) At temperatures of 150oF to 300oF: A base support usually is sufficient but a spring may berequired if equipment expansion causes larger expansion bending moments to be imposedon the equipment. Normally 75% of span is permissible to a non-elastic pipeway supportpoint. Flexibility analysis may require pipeway support point to be an overhead spring,particularly on line sizes 10" and over. Clearances should be based on spring hangerclearance table.

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(c) At temperatures over 300oF the same general conditions as (b) above, will apply. The linerouting should be reviewed with an Analyst during layout, especially, if the size is 8" or over.

4. Points to look for and arrangements to avoid

(a) When pump nozzle size is two or more sizes smaller than the line and valve sizes, a springwill probably be required for top suction of discharge lines.

(b) When pump nozzle is the same size as the line and valve ratings are 300# or more, a springwill probably be required for top suction and discharge lines.

(c) When pump risers have an offset before the valves and installation of a 5BSS is impractical,a spring may be required.

(d) When top suction and discharge nozzles are overloaded, an overhead spring may often beavoided by offsetting the line to the side of the pump and installing a 5BSS.

5. Thermal force limitations on pumps

(a) For all practical purposes the pump piping may be designed during the study stage for amaximum reaction of 200#/nominal inch on steel pump nozzles and 50#/nominal inch forcast iron or aluminum pump nozzles. Dead weight must be added algebraically to thethermal loads in all cases to obtain the total vertical loading on the pump nozzles.

6. Stress sketch requirements

(a) For purposes of computing thermal expansion the face of the nozzle shown on the stresssketch must be related dimensionally to the centerline of the pump shaft vertically andhorizontally. Suction lines should have an additional dimension horizontally relating it to thecenterline of the pump shaft vertically and horizontally. Suction lines should have anadditional dimension horizontally relating it to the centerline of the discharge nozzle.

(b) Make sure that flange ratings, size and material if other than steel are also listed.

(c) List any vendor force or moment limitations.www.IranPiping.ir



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1.9.2 Turbine Drivers: Support requirements

1. Steam Inlet

Generally, the turbine connection is subject to expansions in three directions. The Fluor Standard5BS field support may be used only when care has been taken to neutralize the vertical expansion.Normally the 5BSS is far superior where the supply piping is similar to that shown on 000.250.2352,Pump Piping (Steam) Turbines and Reciprocating Pumps. Additional support will normally berequired on the top horizontal turn to the header, compatible with the expansion requirements, andshould be considered with the steam system drawing.

2. Steam Exhaust

(a) To exhaust header

The Fluor Standard indicates routing to an exhaust header. Generally a 5BS at the base ellwill be satisfactory with the riser and horizontal run to the header supported to take care ofthe expansion requirements. Exhaust header expansions must be taken into account.

(b) To exhaust head

An exhaust head may require an anchored stack because of a long riser requirement.Where a short riser is permissible, locate the riser adjacent to a pipe support column topermit a guide as near as possible to the exhaust head, then the use of a field support ispossible at the exhaust flange level.

(c) To a condenser

Condensing type turbine drivers usually are found as drivers for large centrifugalcompressors. When these are mounted close to grade with a vertical exhaust nozzle, thesupport and line expansion control of the exhaust line usually becomes a major problem.The exhaust line is usually large and it becomes necessary to use an expansion joint subjectto vacuum and positive pressure. A supporting structure must be planned during the pipingstudy, and a stress analyst must be consulted. Generally it is better to orient the exhaustflange down and mount the condenser directly below the turbine with only an expansion jointbetween the flanges on the condenser and turbine. Do not approve turbine outlines with avertical exhaust unless the latter case has been thoroughly investigated.

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3. Thermal Force Limitations

(a) Thermal force can normally be considered as being in the same category as for pumps.That is 200#/nominal inch limitation for steel and 50#/nominal inch limitation for aluminum orcast iron nozzles.

(b) In any case where the vendor limits forces and moments to NEMA Standard SM 20 thestress analyst and design supervisor should be notified immediately so that steps may betaken to remove the note from the vendor's drawings. In cases where compliance ismandatory, considerably more piping may be required. Estimating the amount of additionalpiping is nearly impossible and will be determined by the stress analyst. Notes concerningthese limitations are usually found in the upper left- or right-hand corner of the outline andare generally printed in small letters.

(c) Stress sketch requirements are similar to those on pumps.

1.9.3 Centrifugal Compressors:

1. With Turbine Drivers

Generally it is better practice to orient both the suction and discharge nozzles down.Again, this is for reasons of support and control of line expansions. Usually thelocation of other auxiliary equipment, such as lube oil consoles and coolers, benefitfrom this arrangement.

2. With Electric Motor Drive

Orientation with downward suction and discharge nozzles should again be preferred.If upward orientation is mandatory, provision should be made during layout for anoverhead structure. Consult with a Stress Analyst during layout.

3. Thermal forces and limitations are similar to those at turbines.

4. Stress sketch requirements are similar to those at turbines.www.IranPiping.ir



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1.10 GLOSSARY OF STRESS TERMS

ALLOY STEEL A steel which owes it distinctive properties to elements other thancarbon.

ALLOYING ELEMENTS Chemical elements constituting an alloy. In steel, usually the elementsadded to modify the properties of the steel.

ANNEALING A heating and controlled cooling operation to impart specific desirableproperties generally concerned with subsequent fabrication of the alloy,such as softness and ductility. When annealing follows cold working forthe purpose of stress removal, it is called stress annealing.

AUSTENITIC STEEL Steel, which due to its composition has a stable structure at normal(room) temperatures; as for example: the 18-8 types. It is not hardenedby thermal treatment.

BRINELL HARDNESS A hardness number determined by applying a known load to the surfaceof the material to be tested through a hardened steel ball of knowndiameter. Note: Not suitable for measuring the hardness of strip andsheet because of insufficient thickness.

BRITTLENESS A tendency to fracture without appreciable deformation.

BUTT WELD A circumferential weld in pipe fusing the abutting pipe walls completelyfrom inside wall to outside wall.

CARBON STEEL Steel, which owes its distinctive properties chiefly to the variouspercentages of carbon (as distinguished from the other elements) whichit, contains.

COEFFICIENT OFEXPANSION

A number indicating the degree of expansion or contraction of asubstance.The coefficient of expansion is not constant and varies with changes intemperature. For linear expansion it is expressed as the change inlength of one unit of length of a substance having one degree rise intemperature. A Table of Expansion is generally used to determineexpansion or contraction within a piping system.

COOLING STRESSES Stresses caused by uneven contraction, external restraint or localizedplastic deformation during cooling.

CORROSION The gradual destruction or alteration of a metal or alloy caused by directchemical attack or by electrochemical reaction.

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CORROSION FATIGUE Combined action of corrosion and fatigue in which local corroded areasact as stress concentrators, causing failure at the point of stressconcentration and exposing new metal surfaces to corrosion. The failureis progressive and rapid.

CREEP Plastic flow of metal, usually occurring at high temperatures, subject tostress appreciable less than its yield strength. Progresses through first,second, and third stage to fracture or results in stress relaxation.

DUCTILITY The property of elongation, above the elastic limit, but under the tensilestrength.

A measure of ductility is the percentage of elongation of the fracturedpiece over its original length.

ELASTIC LIMIT The greatest stress which a material can withstand without a permanentdeformation after release of the stress.

ELONGATION The amount of permanent extension in the tensile test, usually expressedas a percentage of the original gauge length, as "25 percent in 2 inches."It may also refer to the amount of extension at any stage in any processthat continuously elongates a body, as in rolling.

ENDURANCE LIMIT A limiting stress, below which metal will withstand without fracture; aspecified larger number of applications of such stress.

EROSION The gradual destruction of metal or other material by the abrasive actionof liquids, gases, solids or mixtures thereof.

FATIGUE The tendency of metal to fracture under conditions of repeated cyclicstressing below the ultimate tensile strength but above the yield.

HARDNESS Resistance to indentation by standard balls, diamonds, etc., understandard loads. Also, the degree of cold working.

HEAT TREATMENT A combination of treating and cooling operations timed and applied tometal or alloy to produce desired properties.

HOOKE'S LAW Stress is proportional to strain in the elastic region.

HYDROGENEMBRITTLEMENT

Brittleness sometimes engendered by contact with plating and picklingsolution acid due to absorption of hydrogen by the metal. Theembrittlement is more evident in hardened parts, and can be removed byaging or heating the steel for a prescribed period.

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MAGNETIC PARTICLETESTING

This method of inspection consists of suitably magnetizing the materialand applying a prepared magnetic powder that adheres along lines offlux leakage. On properly magnetized material, flux leakage developsalong surface non-uniformities. This method is not applicable to highmanganese or austenitic stainless steels and nonferrous alloys which arenonmagnetic.

MECHANICALPROPERTIES

Those properties that reveal the reaction, elastic or plastic, of a materialto an applied stress, or that involving the relationship between stress andstrain; for example, Young's modulus, tensile strength, fatigue limit.These properties have often been designated as physical properties, butthe term "mechanical properties" is technically more accurate andtherefore preferred.

MOMENT OF INERTIA A measure of stiffness or resistance to bending, tension, compression orshear of a material with respect to its geometric shape.

PHYSICAL PROPERTIES Those properties familiarly discussed in physics, exclusive of thosedescribed under Mechanical Properties; for example, density, electricalconductivity; coefficient of thermal expansion. This term has often beenused to describe mechanical properties, but this usage is notrecommended.

PICKLING Immersion in dilute acid or other suitable media for the removal of oxidescale from hot-rolled or otherwise sealed surfaces.

POISSON'S RATIO Ratio expressing the relation of strain normal to the applied load as aproportion of direct strain within the elastic limit. Also relates Module ofElasticity and Rigidity.

PROPORTIONAL LIMIT The highest stress at which the material still follows Hooke's Law. This issimilar to Elastic Limit.

ROCKWELL HARDNESS A measure of the depth of penetration of a penetrator such as a diamondpyramid (Rc) or hardened ball (Rb) under a specified load.

STRAIN Change of shape or size of a body produced by the action of a stress.

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STRESS The intensity of the internal, distributed forces that resist a change in theform of a body. When external forces act on a body they are resisted byreactions within the body, which are termed stresses.

A Tensile Stress is one that resists a force tending to pull a body apart.

A Compressive Stress is one that resists a force tending to crush a body.

A Shearing Stress is one that resists a force tending to make one layer ofa body slide across another layer.

A Torsional Stress is one that resists forces tending to twist a body.

STRESS RELIEVING Heating to and holding at a suitable temperature for the purpose ofreducing residual stresses followed by cooling at such a rate as to leavethe material in essentially stress free condition.

TENSILE STRENGTH The maximum tensile stress which a material will develop. The tensilestrength is usually considered to be the load in pounds per square inch atwhich a test specimen ruptures.

TURBULENCE Any deviations from parallel flow in a pipe due to rough inner walls,obstructions or directional changes.

VELOCITY Time rate of motion in a given direction and sense, usually expressed infeet per second.

WELDING A process of joining metals by heating until they are fused together, or byheating and applying pressure until there is a plastic joining action. Fillermetal may or may not be used.

YIELD STRENGTH The stress at which a material exhibits a specified limiting permanent set.

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1.11 CHARTS AND TABLES

ASTM Material Designation Versus General Name Used on ANSI B31.3 Code Thermal ExpansionChart

GENERAL MATERIAL ASTM CLASSIFICATION

Carbon Steel A 53 Gr A,BA 83 Gr AA 106 Gr A,B

A 120A 135 Gr A,BA 139 Gr A,B

Carbon Steel & A 134 A 335 P 11 Low Chrome A 155 335 P 12

A 333 Gr 6 335 P 15A 335 P 3 335 P 22A 335 P 3b

5-9 Cr A 335 P 5 335 P 5b 335 P 5c 335 P 7

P 9

Austenitic Stainless Steels A 312 TP 304 18 Cr 8 Ni 312 316

312 317 312 321312.00 347

25 Cr 20 Ni A 312 Tp 310Tp 309

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WEIGHT of INSULATION (POUNDS PER LINEAL FOOT)

1. Based on calcium silicate @11 #/ft3

2. Chart must be adjusted for other materials.3. Chart includes banding and covering weight.

1" 1-1/2" 2" 2-1/2" 3" 3-1/2" 4" 4-1/2" 5" 6"

1" 0.72 1.23 1.94 2.76 3.701-1/2" 0.84 1.35 2.52 3.47 4.52

2" 1.01 1.71 2.53 3.48 4.42 5.593" 1.25 2.08 3.01 4.07 5.24 6.654" 1.62 2.55 3.61 4.66 6.07 7.48 9.106" 2.11 3.28 4.57 6.09 7.60 9.82 11.508" 4.13 5.64 7.85 9.48 11.50 13.80 16.00

10" 5.20 7.07 8.93 11.00 13.20 15.50 18.1012" 6.04 8.13 10.50 12.70 15.10 17.40 20.4014" 6.16 8.38 10.70 13.10 15.80 18.50 21.3016" 6.90 9.33 12.00 14.60 17.50 20.50 23.6018" 7.73 10.40 13.30 16.30 19.30 22.60 25.9020" 8.45 11.60 14.60 17.70 21.10 24.60 28.1024" 10.00 13.40 17.00 21.00 24.80 28.70 32.9026" 10.40 14.10 18.00 21.90 26.00 30.20 34.6028" 11.20 15.10 19.20 23.40 27.80 32.20 36.90 41.60 51.4030" 11.90 16.10 20.50 25.00 29.50 34.30 39.10 44.10 54.4032" 12.70 17.10 21.70 26.50 31.30 36.30 41.10 46.60 57.5034" 13.40 18.20 23.00 28.00 33.10 38.30 43.70 49.10 60.5036" 14.20 19.20 24.20 29.50 34.80 40.30 45.90 51.70 63.5042" 16.50 22.20 28.00 34.00 40.10 46.40 52.20 59.20 72.60

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Fluor Daniel

PURPOSEThis practice provides data for the linear expansion of metals. This material is for informationonly; the metals listed in Attachment 01 are not always suitable for the temperatures shown.

SCOPE

This practice covers linear expansion in the following metals:Carbon steel, carbon-moly5 and 9 chrome-molyAustenitic stainless steel12, 17, and 27 chrome25 chrome/20 nickelMonel 673-1/2 nickelAluminumGrey cast ironBronzeBrass70 Cu / 30 NiNi-Fe-Cr

APPLICATIONThis practice should be used as a guide in layout only.

ATTACHMENTSAttachment 01: (18Jan00)Linear Thermal Expansion Of Metals

Practice 000 250 9823Publication Date 18Jan00

Page 1 of 1

FLUOR DANIEL

COEFFICIENT OF EXPANSION TABLES

Piping Engineering

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Fluor Daniel

(Base Temp. = 70°F) Linear Thermal Expansion of Metals (Inches / 100 Feet)

Material

Temp.Degree F

Carbon SteelCarbon-MolyLow-Chrome

(Through 3 Cr Mo)

5 Cr MoThrough9 Cr Mo

AusteniticStainless

Steels18 Cr 8 Ni

12 Cr17 Cr27 Cr

25 Cr20 Ni

Monel 67Ni 30 Cu

3-1/2Nickel

-325 -2.37 -2.22 -3.85 -2.04 -2.62 -2.24

-300 -2.24 -2.10 -3.63 -1.92 -2.50 -2.17

-275 -2.11 -1.98 -3.41 -1.80 -2.38 -2.07

-250 -1.98 -1.86 -3.19 -1.68 -2.26 -1.96

-225 -1.85 -1.74 -2.96 -1.57 -2.14 -1.86

-200 -1.71 -1.62 -2.73 -1.46 -2.02 -1.76

-175 -1.58 -1.50 -2.50 -1.35 -1.90 -1.62

-150 -1.45 -1.37 -2.27 -1.24 -1.79 -1.48

-125 -1.30 -1.23 -2.01 -1.11 -1.59 -1.33

-100 -1.15 -1.08 -1.75 -0.98 -1.38 -1.17

-75 -1.00 -0.94 -1.50 -1.18 -1.01

-50 -0.84 -0.79 -1.24 -0.98 -0.84

-25 -0.68 -0.63 -0.98 -0.77 -0.67

0 -0.49 -0.46 -0.72 -0.57 -0.50 25 -0.32 -0.30 -0.46 -0.37 -0.32

50 -0.14 -0.13 -0.21 -0.20 -0.15

70 0 0 0 0 0

100 0.23 0.22 0.34 0.28 0.23

125 0.42 0.40 0.62 0.52 0.42

150 0.61 0.58 0.90 0.75 0.61

175 0.80 0.76 1.18 0.99 0.81

200 0.99 0.94 1.46 1.22 1.01

225 1.21 1.13 1.75 1.46 1.21

250 1.40 1.33 2.03 1.71 1.42

275 1.61 1.52 2.32 1.96 1.63


Attachment 01 Page 1 of 6

FLUOR DANIEL

LINEAR THERMAL EXPANSION OF METALS

Piping Engineering

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Fluor Daniel


Material

Temp.Degree F


(Through 3 Cr Mo)


AusteniticStainless

Steels18 Cr 8 Ni

12 Cr17 Cr27 Cr

25 Cr20 Ni

Monel 67Ni 30 Cu

3-1/2Nickel

300 1.82 1.71 2.61 2.21 1.84

325 2.04 1.90 2.90 2.44 2.05

350 2.26 2.10 3.20 2.68 2.26

375 2.48 2.30 3.50 2.91 2.47

400 2.70 2.50 3.80 3.25 2.69

425 2.93 2.72 4.10 3.52 2.91

450 3.16 2.93 4.41 3.79 3.13

475 3.39 3.14 4.71 4.06 3.35

500 3.62 3.35 5.01 4.33 3.58

525 3.86 3.58 5.31 4.61 3.81

550 4.11 3.80 5.62 4.90 4.04

575 4.35 4.02 5.93 5.18 4.27

600 4.60 4.24 6.24 5.46 4.50

625 4.86 4.47 6.55 5.75 4.74 650 5.11 4.69 6.87 6.05 4.98

675 5.37 4.92 7.18 6.34 5.22

700 5.63 5.14 7.50 6.64 5.46

725 5.90 5.38 7.82 6.94 5.70

750 6.16 5.62 8.05 7.25 5.94

775 6.43 5.86 8.47 7.55 6.18

800 6.70 6.10 8.80 7.85 6.43

825 6.97 6.34 9.13 8.16 6.68

850 7.25 6.59 9.46 8.48 6.93

875 7.53 6.83 9.79 8.80 7.18

900 7.81 7.07 10.12 9.12 7.43

925 8.08 7.31 10.46 9.44 7.68

950 8.35 7.56 10.80 9.77 7.93

975 8.62 7.81 11.14 10.09 8.17

1000 8.89 8.06 11.48 10.42 8.41

1025 9.17 8.30 11.82 10.75



FLUOR DANIEL


Piping Engineering

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Fluor Daniel


Material

Temp.Degree F


(Through 3 Cr Mo)


AusteniticStainless

Steels18 Cr 8 Ni

12 Cr17 Cr27 Cr

25 Cr20 Ni

Monel 67Ni 30 Cu

3-1/2Nickel

1050 9.46 8.55 12.16 11.09

1075 9.75 8.80 12.50 11.43

1100 10.04 9.05 12.84 11.77

1125 10.31 9.28 13.18 12.11

1150 10.57 9.52 13.52 12.47

1175 10.83 9.76 13.86 12.81

1200 11.10 10.00 14.20 13.15

1225 11.38 10.26 14.54 13.50

1250 11.66 10.53 14.88 13.86

1275 11.94 10.79 15.22 14.22

1300 12.22 11.06 15.56 14.58

1325 12.50 11.30 15.90 14.94

1350 12.78 11.55 16.24 15.30

1375 13.06 11.80 16.58 15.66 1400 13.34 12.05 16.92 16.02

1425 17.30

1450 17.69

1475 18.08

1500 18.47



FLUOR DANIEL


Piping Engineering

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Fluor Daniel

(Base Temp. = 70°F) Linear Thermal Expansion of Metals (Inches /100 Feet)

Material

Temp.Degree F

Aluminum GrayCastIron

Bronze Brass 70 Cr30 Ni

Ni-Fe-Cr

-325 -4.68 -3.98 -3.88 -3.15

-300 -4.46 -3.74 -3.64 2.87

-275 -4.21 -3.50 -3.40 -2.70

-250 -3.97 -3.26 -3.16 2.53

-225 -3.71 -3.02 -2.93 -2.36

-200 -3.44 -2.78 -2.70 -2.19

-175 -3.16 -2.54 -2.47 2.12

-150 -2.88 -2.31 -2.24 -1.95

-125 -2.57 -2.06 -2.00 -1.74

-100 -2.27 -1.81 -1.76 -1.53

-75 -1.97 -1.56 -1.52 -1.33

-50 -1.67 -1.32 -1.29 -1.13

-25 -1.32 -1.25 -1.02 -0.89

0 -0.97 -0.77 -0.75 -0.66 25 -0.63 -0.49 -0.48 -0.42

50 -0.28 -0.22 -0.21 -0.19

70 0 0 0 0 0 0

100 0.46 0.21 0.36 0.35 0.31 0.28

125 0.85 0.38 0.66 0.64 0.56 0.52

150 1.23 0.55 0.96 0.94 0.82 0.76

175 1.62 0.73 1.26 1.23 1.07 0.99

200 2.00 0.90 1.56 1.52 1.33 1.23

225 2.41 1.08 1.86 1.83 1.59 1.49

250 2.83 1.27 2.17 2.14 1.86 1.76

275 3.24 1.45 2.48 2.45 2.13 2.03

300 3.67 1.64 2.79 2.76 2.40 2.30

325 4.09 1.83 3.11 3.08 2.68 2.59

350 4.52 2.03 3.42 3.41 2.96 2.88

375 4.95 2.22 3.74 3.73 3.24 3.18

400 5.39 2.42 4.05 4.05 3.52 3.48



FLUOR DANIEL


Piping Engineering

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Fluor Daniel


Material

Temp.Degree F



Ni-Fe-Cr

425 5.83 2.62 4.37 4.38 3.76

450 6.28 2.83 4.69 4.72 4.04

475 6.72 3.03 5.01 5.06 4.31

500 7.17 3.24 5.33 5.40 4.59

525 7.63 3.46 5.65 5.75 4.87

550 8.10 3.67 5.98 6.10 5.16

575 8.56 3.89 6.31 6.45 5.44

600 9.03 4.11 6.64 6.80 5.72

625 4.34 6.96 7.16 6.01

650 4.57 7.29 7.53 6.30

675 4.80 7.62 7.89 6.58

700 5.03 7.95 8.26 6.88

725 5.26 8.28 8.64 7.17

750 5.50 8.62 9.02 7.47 775 5.74 8.96 9.40 7.76

800 5.98 9.30 9.78 8.06

825 6.22 9.64 10.17 8.35

850 6.47 9.99 10.57 8.66

875 6.72 10.33 10.96 8.95

900 6.97 10.68 11.35 9.26

925 7.23 11.02 11.75 9.56

950 7.50 11.37 12.16 9.87

975 7.76 11.71 12.57 10.18

1000 8.02 12.05 12.98 10.49

1025 12.40 13.39 10.80

1050 12.76 13.81 11.11

1075 13.11 14.23 11.42

1100 13.47 14.65 11.74

1125 12.05

1150 12.38



FLUOR DANIEL


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Fluor Daniel


Material

Temp.Degree F



Ni-Fe-Cr

1175 12.69

1200 13.02

1225 13.36

1250 13.71

1275 14.04

1300 14.39

1325 14.74

1350 15.10

1375 15.44

1400 15.80

1425 16.16

1450 16.53

1475 16.88

1500 17.25



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Fluor Daniel

PURPOSEThis practice establishes guidelines for preparing and submitting piping sketches for stressanalysis and ensures that these sketches are complete and contain the necessary information.This practice eliminates sketching of lines that can be given approval by other means such asinspection at model or equipment study, and provides the Piping Supervisor with a method toverify that the isometric checker has reviewed the Stress Sketch.

SCOPE

This practice provides direction for the interface between Piping Design and Pipe Stressduring the stress sketch development and isometric sign-off phase of the contract.

APPLICATIONThis practice will be implemented during the piping layout phase of the contract. The PipingDesign Supervisor and the Pipe Stress Engineer will utilize this practice to ensure that stressrelated requirements are properly integrated into the piping design.

ACTIVITIES/RESPONSIBILITIES

Step-by-step activities and the responsible parties involved in implementing this practice areoutlined in Attachment 01.

TERMINOLOGYFormal Analysis: A system requiring a manual stress review or a formal computer analysis;however, the Stress Engineer may require that certain lines be sketched in order to determineif a formal analysis is required.

REFERENCESPiping EngineeringPractice 000.250.2221: Stress Design - Sketch Information

Piping EngineeringPractice 000.250.2250: Stress Design - Piping Flexibility Log

ATTACHMENTS

Attachment 01: (11Feb00)Responsibilities And Activity Descriptions

Practice 000 250 2220Publication Date 11Feb00

Page 1 of 1

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STRESS DESIGN - SKETCH PROCEDURE

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Sequence Responsibility Activity Description

1 Lead Stress Engineer Review line list using contract specifications and flow diagrams to determineinitially which lines require sketches (formal submittal) and mark the line list understress column accordingly.

2 Unit Piping Supervisor Refer to line list and initiate Flexibility Log listing line numbers to be sketched.Refer to Piping Engineering Practice 000.250.2250: Stress Design - PipingFlexibility Log.

3 Unit Piping Supervisor /Stress Engineer

Jointly review layouts as this work progresses. Prior to drawing sketch, verify if aformal analysis is actually required for the lines originally listed in the line list.Review closely for any problem areas or additional lines which may require formalanalysis. Update line list and Flexibility Log accordingly.

4 Layout Designer Initiate a sketch / DWD for each line listed in the Flexibility Log. The intent is toprovide the Stress Engineer with a complete system showing all lines of a systemthat affect the piping flexibility of that system. Complex or large systems mayrequire more than 1 sketch or the system may be drawn on roll size sheet.

5 Layout Design Sign off and date in spaces provided after insuring all required data has beenprovided. Submit sketch to Unit Supervisor for review.

6 Unit Piping Supervisor Review sketch for completeness. Sign off and forward.

7 Unit Piping Supervisor orDesignee (Piping Assistantor Contract Clerk)

Order 2 prints of Stress Sketch and place 1 in Stress file for reference until originalis returned. Transmit Stress Sketch original and 1 print (work print) to StressEngineer. Post date "to" Stress in Flexibility Log. For revisions, erase dates to andfrom Stress in Flexibility Log and post new date to Stress for revision.

8 Stress Engineer Inspect line and either approve by inspection, start test calculations or start formalcalculations. If sketch is incomplete or routing is unacceptable, hand carry to UnitSupervisor to rework. Make recommendations to ensure a prompt solution to theproblem.

9 Stress Engineer Add all Stress comments and notes directly on original in red. If necessary, circlecomments in red so they stand out. Complete Stress approval and stress stamp andindicate if sketch is approved, not approved, or approved as marked.

10 Stress Engineer Sign off in space provided, run 1 print of sketch for stress file and return original toUnit Piping Supervisor.

11 Unit Piping Supervisor /Layout Designer

Review stress comments with Layout Designer. Transmit loads and other relevantdata to affect disciplines. Forward original for filing. For checker initiated changesand revisions, review stress comments with checker.

12 Unit Piping Supervisor orPiping Assistant / ContractClerk

Place original in Stress sketch file binder. Remove and destroy print from file.Post date "from" Stress in Flexibility Log.

13 Unit Piping Supervisor Continuously monitor stress file to ensure isometric and model include stressrequirements.

14 Assigned Designers Continuously monitor stress file to ensure isometric and model include stressrequirements.



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RESPONSIBILITIES AND ACTIVITY DESCRIPTIONS

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Checking

15 Piping Checker Review line list and Flexibility Log to determine which sketches pertain to area.Compare finished isometrics to Stress sketch. Ensure that all stress requirementsare met. Negotiate minor differences with Stress Engineer.

16 Piping Checker For checker initiated changes, consult with the Stress Engineer and determine if aresubmittal is required and is so, revise the Stress sketch original and sign off inspace provided. Change Stress sketch revision. Erase Unit Supervisor and StressAnalyst signatures. Forward to Unit Supervisor. Return to Sequence 6. Holdcheck prints until Stress Engineer returns Stress Sketch. Incorporate Stresscomments.

17 Piping Checker Checker will enter "Yes" on line for Stress approval, in revision block on isometric,if Stress sketch is marked "Resubmit Checked Isometric." If Stress sketch ismarked "Approved" or line did not require Stress analysis, draw line through"Stress."

Isometric Revisions

18 Revision Checker Prior to releasing any revised isometric, review Stress sketch and analyze ifflexibility is affected.

Note!!! If there is any doubt that the change may affect Stress, the checker mustconsult with the Stress Engineer and the Piping Supervisor.

19 Revision Checker If flexibility is affected, consult with Stress Engineer and determine if a resubmittalis required and if so, revise Stress sketch original to agree with revised isometric,sign off in space provided and change revision, place initials on Stress sketchoriginal under the appropriate revision space for that line and isometric sheetnumber. Erase Unit Piping Supervisor and Stress Analyst signatures on sketch.Forward to Unit Supervisor. Return to Sequence 6. Hold Check print until StressEngineer returns Stress sketch. Incorporate Stress comments.

Note!!! If the issued isometric had been signed off by Stress, the Stress Engineerwill review and approve all changes.

Stress Signatures on Isometrics

20 Unit Piping Supervisor orPiping Assistant

Note isometric sheets that must be sent to Stress for signature. check PipingIsometric Record and checked isometric to determine which isometrics requireStress approval signature. Hand carry to Stress Engineer. Wait for approval orleave with Stress Engineer. Receive signed isometrics from Stress Engineer.

21 Stress Engineer (if DesignModel is used on theProject)

In addition to signoff of isometrics, reviews model before and after Client review toensure that all lines approved earlier by inspection only are still acceptable.

Unit Supervisor Monitoring

22 Stress EngineeringSupervisor

Stress Engineer Supervisor must review his work load and take action to meet hisschedule.



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23 Unit Piping Supervisor /Layout Designer

Periodically consult with Stress Engineer to obtain assistance in resolving flexibilityproblems by informal reviews at the model or drawing board to eliminateunnecessary paper flow. Jointly, decide on the following:a. The addition of any line or lines for formal submittal.b. The deletion of any lines or portions of lines which were requested for formal

submittal.Update line list and Flexibility Log as necessary.

24 Unit Piping Supervisor Periodically review Stress sketch file during checking phase to verify thatisometrics checkers have entered their initials on the Stress sketch, indicating finalisometrics agree with the Stress sketch.



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PURPOSEThis practice establishes guidelines to outline the information furnished by Piping Design,Pipe Stress, and Process Engineering to be utilized in the production of Stress Sketches.

SCOPE

This practice includes the following major sections:

SYSTEM BOUNDARY

TITLE BLOCK DATA

GRAPHIC SECTION

SPRING HANGERS

FLARE ISOMETRICS

REFERENCES

ATTACHMENTS

APPLICATIONThis practice will be implemented during the Stress Analysis Phase of the contract and will beutilized when analysis of a piping system is required. Pipe Stress and Process Engineeringwill use this practice to convey information to Piping Design for use in the development ofsystem configuration, process conditions, and pipe supports.

SYSTEM BOUNDARYA line or system requiring stress analysis will be submitted from anchor or equipment to otheranchors or equipment as an isometric sketch or drawing. The original, coinciding with theStress group file copy, will be returned to the responsible Design Supervisor.

TITLE BLOCK DATAData affecting the flexibility and support analysis will be filled in on each Stress Sketch. Datathat is not self-explanatory will be determined as outlined below.

Maximum design and operating temperature for applicable conditions such as thefollowing:

- Startup

- Regeneration

- Hot and cold branch functions (pump with spares, one operating, one shut down;bypasses; systems with swing elbows; and swing reactor system)

- Shutdown

- Steam out (defined by Process)

- Normal flowing conditions

- Decoking

- Upset


Page 1 of 3

FLUOR DANIEL

STRESS DESIGN - SKETCH INFORMATION

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Unusual conditions such as lethal or hazardous commodity flowing in the line or ASME(American Society of Mechanical Engineers) boiler code requirements. Pipe StressEngineering will provide specific instructions regarding system configuration whenjacketed pipe is specified or on pharmaceutical projects where stainless steel pipe withTri-Clover connections are specified.

GRAPHIC SECTIONLine work will be single stroke and may be drawn freehand. Weld dots will be indicated toidentify FMU (fitting makeup) only. Dimensions will indicate distance from centerline ofbranch or ell to support. Round off dimensions to nearest 6 inches. The followinginformation will be included on the sketch:

Location of proposed support points and type such as the following:

- Pipe supports

- Trunnions

- Spring hangers

- Pickups

- Hanger rods

- Dummy supports

- Field supports

- Snubbers

Location and orientation of proposed or actual control points such as the following:

- Anchors

- Equipment

- Guides

- Critical clearance

- Directional anchor

- Branch points

- Spring wedges

- Hold downs

Foundation settlement

SPRING HANGERSThe following information should be indicated as an integral part of the Stress Sketch as soonas stress information has been established. Resubmit revised sketch to Stress when steelinformation becomes available.

Location of spring hanger.

Height of the support point in relation to the centerline of the pipe or to the point on thepipe where the spring hanger is attached.

Type of beam or structure used as supporting point and its orientation.

FLARE ISOMETRICS


Page 2 of 3

FLUOR DANIEL


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The flare isometric will provide Stress and Process Engineering with adequate information toanalyze the complete system on a unit-by-unit basis. Refer to Attachment 02 for flareisometric example. Flare isometrics will adhere to the following:

The isometric will be drawn on roll size layout paper.

The header will be indicated as a complete system through the unit to the interconnectingpipeway main header or blowdown drum.

Two-inch and larger branches will be indicated from the pressure relief valve to the flareheader.

The portion upstream of the pressure relief valve will be submitted with the flareisometric as a package on the following documents:

- Stress Engineering: Stress sketches

- Process Engineering: Stress sketches or isometrics

REFERENCESASME (American Society of Mechanical Engineers)

Piping EngineeringPractice 000.250.2220: Stress Design - Sketch Procedure

Piping EngineeringPractice 000.250.2250: Stress Design - Piping Flexibility Log

ATTACHMENTS

Attachment 01: (11Feb00)Stress Sketch Example

Attachment 02: (11Feb00)Flare Isometric Example


Page 3 of 3

FLUOR DANIEL


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PURPOSEThis practice provides lists defining the properties of pipe for use in design and engineeringcalculations.

SCOPE

This practice includes information about the following major topics:Properties of Pipe by Size and ScheduleLinear Expansion of MetalsModulus of Elasticity of Nonferrous Material

APPLICATION

These tables should be used for reference to specific factors to be used in design andengineering work.

REFERENCESPiping Engineering Practice 000.250.9821: Table Of Weights / Piping Components

Piping Engineering Practice 000.250.9823: Coefficient Of Expansion Tables

ATTACHMENTSAttachment 01: (18Jan00)Properties of Pipe

Attachment 02: (18Jan00)Modulus of Elasticity for Ferrous Material

Attachment 03: (18Jan00)Modulus of Elasticity of Nonferrous Material


Page 1 of 1

FLUOR DANIEL

PROPERTIES OF PIPE

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Description Dimension

D Outside Diameter Of Pipe Inches

Sch Pipe Schedule Non Dimension

t Wall Thickness Inches

d Inside Diameter Of Pipe Inches

d5 Fifth power of "d" Inches To The Fifth Power

Ao D Π/12 Outside Pipe Surface Sq Ft / Ft Length

Ai d Π/12 Inside Pipe Surface Sq Ft / Ft Length

Am (d2 − d2 )Π/4 Metal Area Sq Inches

Af d2 2Π/4 Flow Area Sq Inches

w 3.4Am Weight Of Pipe Lbs / Ft (Carbon Steel)

Ww 0.433 Af Weight Of Water In Pipe Lbs / Ft

Rg (I/A)1/2 = (D2 + d2) ½ / 4 Radius Of Gyrations Inches

I AmRg2 = 0.0491 (D4 - d4) Moment Of Inertia Inches To The Fourth Power

Z 2I/D = 0.0982(d4 - d4)/D Section Modulus Inches Cubed

D Sch t d d5 Ao Ai Am Af w Ww Rg I Z

1/8 10S 0.049 0.307 0.00273 0.106 0.080 0.055 0.074 0.186 0.032 0.1271 0.0009 0.0043

D=0.045 40 STD 40S 0.068 0.269 0.00141 0.106 0.070 0.072 0.057 0.245 0.025 0.1215 0.0011 0.0052

80 XS 80S 0.095 0.215 0.00046 0.106 0.056 0.092 0.036 0.314 0.016 0.1146 0.0012 0.0060

1/4 10S 0.065 0.410 0.01159 0.141 0.107 0.097 0.132 0.330 0.057 0.1694 0.0028 0.0103

D=0.540 40 STD 40S 0.088 0.364 0.00639 0.141 0.095 0.125 0.104 0.425 0.045 0.1628 0.0033 0.0123

80 XS 80S 0.119 0.302 0.00251 0.141 0.079 0.157 0.0072 0.535 0.031 0.1547 0.0038 0.0140

3/8 10S 0.065 0.545 0.04808 0.177 0.143 0.124 0.233 0.423 0.101 0.2169 0.0059 0.0174

D=0.675 40 STD 40S 0.091 0.493 0.02912 0.177 0.129 0.167 0.191 0.568 0.083 0.2090 0.0073 0.0216

80 XS 80S 0.126 0.423 0.01354 0.177 0.111 0.217 0.140 0.739 0.061 0.1991 0.0086 0.0255

10S 0.083 0.674 0.13909 0.220 1.176 0.197 0.357 0.671 0.154 0.269 0.0143 0.0341

1/2 40 STD 40S 0.109 0.622 0.09310 0.220 0.163 0.250 0.304 0.851 0.132 0.261 0.0171 0.0407

D=0.840 80 XS 80S 0.147 0.546 0.04852 0.220 0.143 0.320 0.234 1.088 0.101 0.250 0.0201 0.0478

160 0.188 0.466 0.02198 0.220 0.122 0.384 0.171 1.304 0.074 0.240 0.0221 0.0527

XXS 0.294 0.252 0.00102 0.220 0.066 0.504 0.050 1.715 0.022 0.219 0.0243 0.0577

5S 0.065 0.920 0.6591 0.275 0.241 0.201 0.664 0.683 0.288 0.349 0.0245 0.0467

10S 0.083 0.884 0.5398 0.275 0.231 0.252 0.614 0.857 0.266 0.343 0.0297 0.0566

3/4 40 STD 40S 0.113 0.824 0.3799 0.275 0.216 0.333 0.533 1.131 0.231 0.334 0.0370 0.0706

D=1.050 80 XS 80S 0.154 0.742 0.2249 0.275 0.194 0.434 0.432 1.474 0.187 0.321 0.0448 0.0853

160 0.219 0.614 0.0873 0.275 0.161 0.570 0.296 1.937 0.128 0.304 0.0527 0.1004

XXS 0.308 0.434 0.0154 0.275 0.114 0.718 0.148 2.441 0.064 0.284 0.0579 0.1104


Attachment 01 - Page 1 of 13

FLUOR DANIEL

PROPERTIES OF PIPE

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5S 0.065 1.185 2.337 0.344 0.310 0.255 1.103 0.867 0.478 0.443 0.0500 0.7600

10S 0.109 1.097 1.589 0.344 0.287 0.413 0.945 1.404 0.409 0.428 0.0757 0.1151

1 40 STD 40S 0.133 1.049 1.270 0.344 0.275 0.494 0.864 1.679 0.374 0.420 0.0874 0.1329

D=1.315 80 XS 80S 0.179 0.957 0.803 0.344 0.250 0.639 0.719 2.172 0.311 0.407 0.1056 0.1606

160 0.250 0.815 0.360 0.344 0.213 0.836 0.522 2.844 0.226 0.387 0.1252 0.1903

XXS 0.358 0.599 0.077 0.344 0.157 1.076 0.282 3.659 0.122 0.361 0.1405 0.2137

5S 0.065 1.530 8.384 0.435 0.410 0.326 1.839 1.108 0.796 0.564 0.1037 0.1253

10S 0.109 1.442 6.235 0.434 0.378 0.531 1.633 1.805 0.707 0.550 0.1605 0.1934

1-1/4 40 STD 40S 0.140 1.380 5.005 0.434 0.361 0.668 1.496 2.273 0.648 0.540 0.1948 0.2346

D=1.660 80 XS 80S 0.191 1.278 3.409 0.434 0.334 0.881 1.283 2.997 0.555 0.524 0.2418 0.2914

160 0.250 1.160 2.100 0.434 0.304 1.107 1.057 3.765 0.458 0.506 0.2839 0.3421

XXS 0.382 0.896 0.577 0.434 0.234 1.534 0.630 5.215 0.273 0.472 0.3412 0.411

5S 0.065 1.770 17.37 0.497 0.463 0.375 2.461 1.275 1.066 0.649 0.158 0.166

10S 0.109 1.682 13.46 0.497 0.440 0.613 2.222 2.085 0.962 0.634 0.247 0.260

1-1/2 40 STD 40S 0.145 1.610 10.82 0.497 0.421 0.799 2.036 2.718 0.882 0.623 0.310 0.326

D=1.900 80 XS 80S 0.200 1.500 7.59 0.497 0.393 1.068 1.767 3.632 0.765 0.605 0.391 0.412

160 0.281 1.337 4.27 0.497 0.350 1.431 1.404 4.866 0.608 0.581 0.483 0.508

XXS 0.400 1.100 1.61 0.497 0.288 1.885 0.950 6.409 0.411 0.549 0.568 0.598

5S 0.065 2.245 57.03 0.622 0.588 0.472 3.958 1.605 1.714 0.817 0.315 0.265

10S 0.109 2.157 46.69 0.622 0.565 0.776 3.654 2.638 1.582 0.802 0.499 0.420

40 STD 40S 0.154 2.067 37.73 0.622 0.541 1.074 3.356 3.653 1.453 0.787 0.666 0.561

2 0.167 2.041 35.42 0.622 0.534 1.158 3.272 3.938 1.417 0.783 0.710 0.598

D=2.375 0.188 2.000 32.00 0.622 0.524 1.288 3.142 4.381 1.360 0.776 0.777 0.654

80 XS 80S 0.218 1.939 27.41 0.622 0.508 1.477 2.953 5.022 1.278 0.766 0.868 0.731

160 0.344 1.689 13.74 0.622 0.442 2.190 2.240 7.445 0.970 0.728 1.163 0.979

XXS 0.436 1.503 7.67 0.622 0.393 2.656 1.774 9.030 0.768 0.703 1.312 1.104

5S 0.083 2.709 145.9 0.753 0.709 0.728 5.76 2.475 2.496 0.988 0.711 0.495

10S 0.120 2.635 127.0 0.753 0.690 1.039 5.45 3.531 2.361 0.975 0.988 0.687

2-1/2 40 STD 40S 0.203 2.469 91.8 0.753 0.646 1.704 4.79 5.794 2.073 0.947 1.530 1.064

D=2.875 80 XS 80S 0.276 2.323 67.6 0.753 0.608 2.254 4.24 7.662 1.835 0.924 1.925 1.339

160 0.375 2.125 43.3 0.753 0.556 2.945 3.55 10.01 1.536 0.894 2.353 1.637

XXS 0.552 1.771 17.4 0.753 0.464 4.028 2.46 13.70 1.067 0.844 2.872 1.998

5S 0.083 3.334 411.9 0.916 0.873 0.891 8.73 3.03 3.780 1.208 1.300 0.743

10S 0.120 3.260 368.2 0.916 0.853 1.274 8.35 4.33 3.610 1.196 1.822 1.041

3 40 STD 40S 0.216 3.068 271.8 0.916 0.803 2.228 7.39 7.58 3.200 1.164 3.018 1.724

D=3.500 80 XS 80S 0.300 2.900 205.0 0.916 0.759 3.016 6.60 10.25 2.860 1.136 3.900 2.226

160 0.438 2.624 124.0 0.916 0.687 4.213 5.41 14.33 2.340 1.094 5.040 2.879

XXS 0.600 2.300 64.0 0.916 0.602 5.466 4.15 18.58 1.800 1.047 5.990 3.425



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PROPERTIES OF PIPE

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5S 0.083 3.834 828.0 1.047 1.004 1.021 11.55 3.47 5.000 1.385 1.960 0.979

3-1/2 10S 0.120 3.760 752.0 1.047 0.984 1.463 11.10 4.97 4.810 1.372 2.760 1.378

D=4.000 40 STD 40S 0.226 3.548 562.0 1.047 0.929 2.680 9.89 9.11 4.280 1.337 4.790 2.394

80 XS 80S 0.318 3.364 431.0 1.047 0.881 3.678 8.89 12.51 3.850 1.307 6.280 3.141



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PROPERTIES OF PIPE

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5S 0.083 4.334 1529.0 1.178 1.135 1.151 14.75 3.91 6.390 1.562 2.810 1.248

10S 0.120 4.260 1403.0 1.178 1.115 1.651 14.25 5.61 6.170 1.549 3.960 1.762

40 STD 40S 0.237 4.026 1058.0 1.178 1.054 3.170 12.73 10.79 5.510 1.510 7.230 3.220

Special 0.312 3.876 875.0 1.178 1.015 4.100 11.80 13.96 5.110 1.485 9.050 4.020

4 80 XS 80S 0.337 3.826 820.0 1.178 1.002 4.410 11.50 14.99 4.980 1.477 9.610 4.270

D=4.500 Special 0.375 3.750 742.0 1.178 0.982 4.860 11.04 16.52 4.780 1.404 10.420 4.630

120 0.438 3.624 625.0 1.178 0.949 5.590 10.31 19.00 4.470 1.444 11.660 5.180

Special 0.500 3.500 525.0 1.178 0.916 6.280 9.62 21.36 4.170 1.425 12.770 5.670

160 0.531 3.438 480.0 1.178 0.900 6.620 9.28 22.51 4.020 1.416 13.270 5.900

XXS 0.674 3.152 311.0 1.178 0.825 8.100 7.80 27.54 3.380 1.374 15.290 6.790

5S 0.109 5.345 4363.0 1.456 1.399 1.880 22.43 6.38 9.710 1.928 6.970 2.510

10S 0.134 5.295 4162.0 1.456 1.386 2.290 22.02 7.77 9.530 1.920 8.430 3.030

40 STD 40S 0.258 5.047 3275.0 1.456 1.321 4.300 20.01 14.62 8.660 1.878 15.170 5.450

5 80 XS 80S 0.375 4.813 2583.0 1.456 1.260 6.110 18.19 20.78 7.880 1.839 30.680 7.430

D=5.563 Special 0.438 4.688 2264.0 1.456 1.227 7.040 17.26 23.95 7.470 1.819 23.310 8.380

120 0.500 4.563 1978.0 1.456 1.194 7.950 16.35 27.04 7.060 1.799 25.740 9.250

160 0.625 4.313 1492.0 1.456 1.129 9.700 14.61 32.97 6.330 1.760 30.030 10.800

XXS 0.750 4.063 1107.0 1.456 1.064 11.34 12.97 38.55 5.610 1.722 33.640 12.100

D Sch t d d5/103 Ao Ai Am Af w Ww Rg I Z

5S 0.109 6.407 10.80 1.734 1.677 2.23 32.2 7.58 13.95 2.304 11.84 3.58

10S 01.34 6.357 10.38 1.734 1.664 2.73 31.7 9.29 13.74 2.295 14.40 4.35

Special 0.250 6.125 8.62 1.734 1.604 5.01 29.5 17.02 12.75 2.256 25.50 7.69

6 40 STD 40S 0.280 6.065 8.21 1.734 1.588 5.58 28.9 18.98 12.51 2.246 28.10 8.50

D=6.625 80 XS 80S 0.432 5.761 6.35 1.734 1.508 8.40 26.1 28.58 11.29 2.195 40.50 12.23

120 0.562 5.501 5.04 1.734 1.440 10.70 23.8 36.40 10.29 2.153 49.60 14.98

160 0.719 5.189 3.76 1.734 1.358 13.32 21.1 45.30 9.16 2.104 59.00 17.81

XXS 0.864 4.897 2.82 1.734 1.282 15.64 18.8 53.17 8.16 2.060 66.30 20.03



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PROPERTIES OF PIPE

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Fluor Daniel


5S 0.109 8.407 42.00 2.258 2.201 2.92 55.5 9.91 24.04 3.010 26.40 6.13

10S 0.148 8.329 40.10 2.258 2.180 3.94 54.5 13.40 23.59 3.000 35.40 8.21

20 0.250 8.125 35.40 2.258 2.127 6.58 51.8 22.37 22.45 2.960 57.70 13.39

30 0.277 8.071 34.20 2.258 2.113 7.26 51.2 24.70 22.15 2.950 63.40 14.69

40 STD 40S 0.322 7.981 32.40 2.258 2.089 8.40 50.0 28.56 21.68 2.940 72.50 16.81

8 Special 0.375 7.875 30.30 2.258 2.062 9.72 48.7 33.00 21.10 2.920 82.90 19.22

D=8.625 60 0.406 7.813 29.10 2.258 2.045 10.48 47.9 35.60 20.80 2.910 88.80 20.58

80 XS 80S 0.500 7.625 25.80 2.258 1.996 12.76 45.7 43.40 19.80 2.880 105.70 24.52

100 0.594 7.439 22.80 2.258 1.948 14.96 43.5 50.90 18.80 2.850 121.40 28.14

120 0.719 7.189 19.20 2.258 1.882 17.84 40.6 60.60 17.60 2.810 140.60 32.60

140 0.812 7.001 16.80 2.258 1.883 19.93 38.5 67.80 16.70 2.780 153.70 35.63

XXS 0.875 6.875 15.40 2.258 1.800 21.30 37.1 72.40 16.10 2.760 162.00 37.57

160 0.906 6.813 14.70 2.258 1.784 21.97 36.5 74.70 15.80 2.750 165.90 38.48

5S 0.134 10.482 127.00 2.810 2.740 4.47 86.3 15.20 37.40 3.750 63.00 11.72

10S 0.165 10.420 123.00 2.810 2.730 5.49 85.3 18.70 36.90 3.740 76.90 14.30

20 0.250 10.250 113.00 2.810 2.680 8.25 82.5 28.00 35.70 3.710 113.70 21.16

30 0.307 10.136 107.00 2.810 2.650 10.07 80.7 34.20 34.90 3.690 137.50 25.57

10 40 STD 40S 0.365 10.020 101.00 2.810 2.620 11.91 78.9 40.50 34.10 3.670 160.80 29.91

D=10.75 60 XS 80S 0.500 9.750 88.10 2.810 2.550 16.10 74.7 54.70 32.30 3.630 212.00 39.40

80 0.594 9.654 80.00 2.810 2.500 18.92 71.8 64.30 31.10 3.600 244.80 45.50

100 0.719 9.314 70.10 2.810 2.440 22.63 68.1 76.90 29.50 3.560 286.20 53.20

Special 0.750 9.250 67.70 2.810 2.420 23.56 67.2 80.10 29.10 3.550 296.30 55.10

120 0.843 9.064 61.20 2.810 2.370 26.24 64.5 89.20 27.90 3.520 324.30 60.30

140 XXS 1.000 8.750 51.30 2.810 2.290 30.63 60.1 104.1 26.00 3.470 367.90 68.40

160 1.125 8.500 44.40 2.810 2.230 34.02 56.7 115.7 24.60 3.430 399.40 74.30

5S 0.156 12.438 298.00 3.340 3.260 3.17 121.5 21.0 52.60 4.450 122.40 19.20

10S 0.180 12.390 292.00 3.340 3.240 7.11 120.6 24.2 52.20 4.440 140.50 22.00

20 0.250 12.250 276.00 3.340 3.210 9.82 117.9 33.4 51.10 4.420 191.90 301.0

30 0.330 12.090 258.00 3.340 3.170 12.88 114.8 43.8 49.70 4.390 248.50 39.00

STD 40S 0.375 12.000 249.00 3.340 3.140 14.58 113.1 49.6 49.00 4.380 279.00 43.80

12 40 0.406 11.938 242.00 3.340 3.130 15.74 111.9 53.5 48.50 4.370 300.00 47.10

D=14.00 XS 80S 0.500 11.750 224.00 3.340 3.080 19.24 108.4 65.4 47.00 4.330 362.00 56.70

60 0.562 11.626 212.00 3.340 3.040 21.52 106.2 73.2 46.00 4.310 401.00 62.80

Special 0.625 11.500 201.00 3.340 3.010 23.81 103.9 80.9 45.00 4.290 439.00 68.80

80 0.687 11.376 191.00 3.340 2.980 26.04 101.6 88.5 44.00 4.270 475.00 74.50

100 0.843 11.064 166.00 3.340 2.900 31.53 96.1 107.2 41.60 4.220 562.00 88.10

120 XXS 1.000 10.750 144.00 3.340 2.810 36.91 90.8 125.5 39.30 4.170 642.00 100.70

140 1.125 10.500 128.00 3.340 2.750 41.09 86.6 139.7 37.50 4.130 701.00 109.90



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Fluor Daniel


160 1.312 10.126 106.00 3.340 2.650 47.14 80.5 160.3 34.90 4.070 781.00 122.60



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Fluor Daniel


5S 0.156 13.688 481 3.67 3.58 6.78 147.2 23.1 63.7 4.90 163 23.2

10S 0.188 13.624 469 3.67 3.57 8.16 145.8 27.7 63.1 4.88 195 27.8

10 0.250 13.500 448 3.67 3.53 10.80 143.1 36.7 62.0 4.86 255 36.5

20 0.312 13.375 428 3.67 3.50 13.44 140.5 45.7 60.8 4.84 315 45.0

30 STD 0.375 13.250 408 3.67 3.47 16.05 137.9 54.6 59.7 4.82 373 53.3

14 40 0.438 13.125 389 3.67 3.44 18.66 135.3 63.4 58.6 4.80 429 61.4

D=14.00 XS 0.500 13.000 371 3.67 3.40 21.21 132.7 72.1 57.5 4.78 484 69.1

60 0.594 12.814 345 3.67 3.35 24.98 129.0 84.9 55.8 4.74 562 80.3

Special 0.625 12.750 337 3.67 3.34 26.26 127.7 89.3 55.3 4.73 589 84.1

80 0.750 12.500 305 3.67 3.27 31.22 122.7 106.1 53.1 4.69 687 98.2

100 0.938 12.125 262 3.67 3.17 38.47 115.5 130.8 50.0 4.63 825 117.9

120 1.094 11.814 230 3.67 3.09 44.32 109.6 150.7 47.5 4.58 930 132.8

140 1.250 11.500 201 3.67 3.01 50.07 103.9 170.2 45.0 4.53 1027 146.8

160 1.406 11.188 175 3.67 2.93 55.63 98.3 189.1 42.6 4.48 1117 159.6

5S 0.165 15.670 945 4.19 4.10 8.21 192.9 27.9 83.5 5.60 257 32.2

10S 0.188 15.624 931 4.19 4.09 9.34 191.7 31.8 83.0 5.59 292 36.5

10 0.250 15.500 895 4.19 4.06 12.37 188.7 42.1 81.7 5.57 384 48.0

20 0.312 15.375 859 4.19 4.02 15.40 185.7 52.4 80.4 5.55 474 59.3

30 STD 0.375 15.250 825 4.19 3.99 18.41 182.7 63.6 79.1 5.53 562 70.3

40 XS 0.500 15.000 759 4.19 3.93 24.35 176.7 38.8 76.5 5.48 732 91.5

16 60 0.656 14.688 684 4.19 3.85 31.62 169.4 107.5 73.4 5.43 833 116.6

D=16.00 Special 0.750 14.500 641 4.19 3.80 35.90 165.1 127.5 71.5 5.40 1047 130.9

80 0.844 14.314 601 4.19 3.75 40.14 160.9 136.5 69.7 5.37 1157 144.6

100 1.031 13.938 526 4.19 3.65 48.48 152.6 164.8 66.1 5.29 1365 170.6

120 1.219 13.564 459 4.19 3.55 56.56 144.5 192.3 62.6 5.23 1556 194.5

140 1.438 13.124 389 4.19 3.44 65.79 135.3 223.7 58.6 5.17 1761 220.1

160 1.594 12.814 345 4.19 3.35 72.10 129.0 245.1 55.8 5.12 1984 236.7

5S 0.165 17.670 1723 4.71 4.63 9.24 245.2 31.4 106.2 6.31 368 40.9

10S 0.188 17.624 1700 4.71 4.61 10.52 243.9 35.8 105.6 6.30 417 46.4

10 0.250 17.500 1641 4.71 4.58 13.94 240.5 47.4 104.1 6.28 549 61.0

20 0.312 17.375 1584 4.71 4.55 17.36 237.1 59.0 102.7 6.25 679 75.5

ST 0.375 17.250

1527 4.71 4.52 20.76 233.7 70.6 101.2 6.23 807 89.6

30 0.438 17.124 1472 4.71 4.48 24.17 230.3 82.2 99.7 6.21 932 103.6

18 XS 0.500 17.000 1420 4.71 4.45 27.49 227.0 93.5 98.3 6.19 1053 117.0

D=18.00 40 0.562 16.876 1369 4.71 4.42 30.79 223.7 104.7 96.9 6.17 1171 130.2

Special 0.625 16.750 1318 4.71 4.39 34.12 220.4 116.0 95.4 6.15 1289 143.3

60 0.750 16.500 1223 4.71 4.32 40.64 213.8 138.2 92.6 6.10 1515 168.3



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Fluor Daniel


80 0.938 16.126 1090 4.71 4.22 50.23 204.2 170.8 88.4 6.04 1834 203.8

100 1.156 15.688 950 4.71 4.11 61.17 193.3 208.0 83.7 5.97 2180 242.2

120 1.375 15.250 825 4.71 3.99 71.81 182.7 244.2 79.1 5.90 2498 277.6

140 1.562 14.876 728 4.71 3.89 80.66 173.8 274.3 75.3 5.84 2750 305.5

160 1.781 14.433 627 4.71 3.78 90.75 163.7 308.5 70.9 5.77 3020 335.6



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Fluor Daniel


5S 0.188 19.624 2910 5.24 5.14 11.70 302.5 39.8 131.0 7.00 574 57.4

10S 0.218 19.564 2870 5.24 5.12 13.55 300.6 46.1 130.2 6.99 663 66.3

10 0.250 19.500 2820 5.24 5.11 15.51 298.6 52.7 129.3 6.98 757 75.7

20 STD 0.375 19.250 2640 5.24 5.04 23.12 291.0 78.6 126.0 6.94 1114 111.4

30 XS 0.500 19.000 2480 5.24 4.97 30.60 283.5 104.1 122.8 6.90 1457 145.7

20 40 0.594 18.814 2360 5.24 4.93 36.20 278.0 122.9 120.4 6.86 1704 170.4

D=20.00 Special 0.625 18.750 2320 5.24 4.91 38.00 276.1 129.3 119.6 6.85 1787 178.7

60 0.812 18.376 2100 5.24 4.81 48.90 265.2 166.4 114.8 6.79 2257 225.7

Special 0.875 18.250 2020 5.24 4.78 52.60 261.6 178.7 113.3 6.77 2409 240.9

80 1.031 17.938 1860 5.24 4.70 61.40 252.7 208.9 109.4 6.72 2772 277.2

100 1.281 17.438 1610 5.24 4.57 75.30 238.8 256.1 103.4 6.63 3316 331.6

120 1.500 17.000 1420 5.24 4.45 87.20 227.0 296.4 98.3 6.56 3755 375.5

140 1.750 16.500 1220 5.24 4.32 100.3 213.8 341.1 92.6 6.48 4217 421.7

160 1.969 16.064 1070 5.24 4.21 111.5 202.7 379.1 87.8 6.41 4586 458.6


10 0.250 21.500 4.59 5.76 5.63 17.1 363 58.1 157.2 7.69 1010 91.8

10 0.312 21.376 4.46 5.76 5.60 21.5 359 72.3 155.6 7.67 1250 113.7

20 ST 0.375 21.250 4.33 5.76 5.56 25.5 355 86.6 153.6 7.65 1490 135.4

22 30 XS 0.500 21.000 4.08 5.76 5.50 33.8 346 114.8 150.0 7.60 1953 177.5

D=22.00 Special 0.625 20.750 3.85 5.76 5.43 42.0 338 142.7 146.4 7.56 2400 218.2

Special 0.750 20.500 3.62 5.76 5.37 50.1 330 170.2 142.9 7.52 2830 257.3

60 0.875 20.500 3.41 5.76 5.30 58.1 322 197.4 139.5 7.48 3246 295.1

Special 1.000 20.000 3.20 5.76 5.24 66.0 314 224.3 136.0 7.43 3646 331.5



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Fluor Daniel


5S 0.218 23.564 7.26 6.28 6.17 16.3 436 55.4 188.8 8.41 1152 96.0

10 10S 0.250 23.500 7.17 6.28 6.15 18.7 434 63.4 187.8 8.40 1316 109.6

Special 0.312 23.376 6.98 6.28 6.12 23.2 429 78.9 185.8 8.38 1629 135.8

20 STD 0.375 23.250 6.79 6.28 6.09 27.8 425 94.6 183.8 8.35 1943 161.9

Special 0.438 23.125 6.61 6.28 6.05 32.4 420 110.1 181.9 8.33 2249 187.4

XS 0.500 23.000 6.44 6.28 6.02 36.9 415 125.5 179.9 8.31 2250 212.5

30 0.562 22.876 6.26 6.28 5.99 41.4 411 140.7 178.0 8.29 2840 237.0

24 Special 0.625 22.750 6.09 6.28 5.96 45.9 406 156.0 176.0 8.27 3140 261.0

D=24.00 40 0.688 22.626 5.93 6.28 5.92 50.3 402 171.1 174.1 8.25 3420 285.0

Special 0.750 22.500 5.77 6.28 5.89 54.8 398 186.3 172.2 8.22 3710 309.0

60 0.969 22.064 5.23 6.28 5.78 70.0 382 238.1 165.6 8.15 4653 388.0

Special 1.031 21.938 5.08 6.28 5.74 74.4 378 252.9 163.7 8.13 4920 410.0

80 1.219 21.564 4.66 6.28 5.65 87.2 365 296.4 158.1 8.07 5670 473.0

100 1.531 20.938 4.02 6.28 5.48 108.1 344 367.4 149.1 7.96 6852 571.0

120 1.812 20.376 3.51 6.28 5.33 126.3 326 429.4 141.2 7.87 7824 652.0

140 2.062 19.876 3.50 6.28 5.20 142.1 310 483.2 134.3 7.79 8630 719.0

160 2.344 19.314 2.69 6.28 5.06 159.4 293 542.0 126.9 7.70 9455 788.0

10 0.312 25.376 10.52 6.81 6.64 25.2 506 85.7 219.0 9.08 2078 160.0

STD 0.375 25.250 10.26 6.81 6.61 30.2 501 102.6 216.8 9.06 2479 191.0

Special 0.438 25.124 10.01 6.81 6.56 35.2 496 119.6 214.7 9.04 2874 221.0

20 XS 0.500 25.000 9.77 6.81 6.54 40.1 491 136.2 212.5 9.02 3257 250.0

Special 0.562 24.876 9.53 6.81 6.51 44.9 486 152.7 210.4 9.00 3639 280.0

26 Special 0.625 24.750 9.29 6.81 6.48 49.8 481 169.4 208.3 8.97 4014 309.0

D=26.00 Special 0.656 24.688 9.17 6.81 6.46 52.2 479 177.6 207.3 8.96 4198 323.0

Special 0.750 24.500 8.83 6.81 6.41 59.5 471 202.3 204.1 8.93 4747 365.0

Special 0.812 24.376 8.61 6.81 6.38 64.3 467 218.5 202.1 8.91 5102 393.0

Special 0.875 24.250 8.39 6.81 6.35 69.1 462 234.8 200.0 8.89 5458 420.0

Special 0.938 24.124 8.17 6.81 6.32 73.9 457 251.2 197.9 8.87 5808 447.0

Special 1.000 24.000 7.96 6.81 6.28 78.5 452 267.0 195.9 8.85 6147 473.0

10 0.312 27.376 15.38 7.33 7.17 27.1 589 92.3 254.9 9.79 2602 186.0

ST 0.375 27.250 15.03 7.33 7.13 32.5 583 110.7 252.5 9.77 3106 222.0

Special 0.438 27.124 14.68 7.33 7.10 37.9 578 128.9 250.2 9.75 3603 257.0

20 XS 0.500 27.000 14.35 7.33 7.07 43.2 573 146.9 247.9 9.72 4086 292.0

28 Special 0.562 26.876 14.02 7.33 7.04 48.4 567 164.7 245.6 9.70 4562 326.0

D=28.00 30 0.625 26.750 13.70 7.33 7.00 53.8 562 182.8 243.3 9.68 5039 360.0

Special 0.656 26.688 13.54 7.33 6.99 56.4 559 191.6 242.2 9.67 5271 377.0

Special 0.750 26.500 13.07 7.33 6.94 64.2 552 218.3 238.8 9.64 5966 426.0

Special 0.812 26.376 12.77 7.33 6.91 69.4 546 235.8 236.6 9.62 6416 458.0



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Fluor Daniel


Special 0.875 26.250 12.46 7.33 6.87 74.6 541 253.5 234.3 9.60 6867 490.0

Special 0.938 26.124 12.17 7.33 6.84 79.7 536 271.1 232.1 9.57 7311 522.0

Special 1.000 26.000 11.88 7.33 6.81 84.8 531 288.4 229.9 9.55 7742 553.0



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Fluor Daniel


5S 0.250 29.500 22.3 7.85 7.72 23.4 683 79.4 296.0 10.52 2586 172

10 10S 0.312 29.376 21.9 7.85 7.69 29.1 678 98.9 293.5 10.50 3210 214

ST 0.375 29.250 21.4 7.85 7.66 34.9 672 118.7 291.0 10.48 3833 255

Special 0.438 29.125 21.0 7.85 7.62 40.6 666 138.0 288.4 10.45 4434 296

20 XS 0.500 29.000 20.5 7.85 7.59 46.3 661 157.6 286.0 10.43 5040 336

30 Special 0.562 28.875 20.1 7.85 7.56 52.0 665 176.8 283.6 10.41 5635 376

30 0.625 28.750 19.6 7.85 7.53 57.7 649 196.1 281.1 10.39 6230 415

Special 0.656 28.688 19.4 7.85 7.51 60.5 646 205.6 279.9 10.38 6514 434

Special 0.750 28.500 18.8 7.85 7.46 68.9 638 234.3 276.2 10.34 7377 492

Special 0.812 28.376 18.4 7.85 7.43 74.5 632 253.2 273.8 10.32 7937 529

Special 0.875 28.250 18.0 7.85 7.40 80.1 627 272.2 271.4 10.30 8499 567

Special 0.938 28.124 17.6 7.85 7.36 85.6 621 291.2 269.0 10.28 9053 604

Special 1.000 28.000 17.2 7.85 7.33 91.1 616 309.8 266.6 10.26 9591 639

10 0.312 31.376 30.4 8.38 8.21 31.1 773 105.6 334.8 11.20 3900 244

STD 0.375 31.250 29.8 8.38 8.18 37.3 767 126.7 332.1 11.18 4660 291

Special 0.438 31.124 29.2 8.38 8.15 43.4 761 147.7 329.4 11.16 5410 338

20 XS 0.500 31.000 28.6 8.38 8.12 49.5 755 168.2 326.8 11.14 6140 384

Special 0.562 30.876 28.1 8.38 8.08 55.5 749 188.7 324.2 11.12 6861 429

32 30 0.625 30.750 27.5 8.38 8.05 61.6 743 209.5 321.6 11.10 7585 474

D=32.00 40 0.688 30.624 26.9 8.38 8.02 67.6 737 230.1 318.9 11.07 8300 518

Special 0.750 30.500 26.4 8.38 7.98 73.6 731 250.3 316.4 11.05 8995 562

Special 0.812 31.376 25.9 8.38 7.95 79.6 725 270.5 313.8 11.03 9682 605

Special 0.875 30.250 25.3 8.38 7.92 85.6 719 290.9 311.2 11.01 10371 648

Special 0.938 30.124 24.8 8.38 7.89 91.5 713 311.2 308.6 10.99 11052 691

Special 1.000 30.000 24.3 8.38 7.85 97.4 707 331.1 306.1 10.97 11714 732

10 0.312 33.376 41.4 8.90 8.74 33.0 875 112.3 378.8 11.91 4686 276

STD 0.375 33.250 40.6 8.90 8.70 39.6 868 134.7 376.0 11.89 5599 329

Special 0.438 33.124 39.9 8.90 8.67 46.2 862 157.0 373.1 11.87 6505 383

20 XS 0.500 33.000 39.1 8.90 8.64 52.6 855 178.9 370.3 11.85 7383 434

Special 0.562 32.876 38.4 8.90 8.61 59.0 849 200.7 367.6 11.82 8256 486

34 30 0.625 32.750 37.7 8.90 8.57 65.5 842 222.8 364.8 11.80 9130 537

D=34.00 40 0.656 32.624 37.0 8.90 8.54 72.0 836 244.8 361.9 11.78 9994 587

Special 0.750 32.500 36.3 8.90 8.51 78.3 830 266.4 359.2 11.76 10835 637

Special 0.812 32.376 35.6 8.90 8.48 84.7 823 287.9 356.5 11.74 11666 686

Special 0.875 32.250 34.9 8.90 8.44 91.1 817 309.6 353.7 11.72 12501 735

Special 0.938 32.124 34.2 8.90 8.41 97.4 810 331.3 350.9 11.69 13326 784

Special 1.000 32.000 33.6 8.90 8.38 103.7 804 352.5 348.2 11.67 14129 831



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Fluor Daniel


10 0.312 35.376 55.4 9.42 9.26 35.0 983 118.9 425.6 12.62 5571 310

ST 0.375 35.250 54.4 9.42 9.23 42.0 976 142.7 422.6 12.60 6659 370

Special 0.438 35.124 53.5 9.42 9.20 48.9 969 166.4 419.6 12.57 7739 430

20 XS 0.500 35.000 52.5 9.42 9.16 55.8 962 189.6 416.6 12.55 8786 488

36 Special 0.562 34.876 51.6 9.42 9.13 62.6 955 212.7 413.6 12.53 9827 546

D=36.00 30 0.625 34.750 50.7 9.42 9.10 69.5 948 236.2 410.7 12.51 10871 604

40 0.750 34.500 48.9 9.42 9.03 83.1 935 282.4 404.8 12.46 12909 717

Special 0.812 34.376 48.0 9.42 9.00 89.8 928 305.2 401.9 12.44 13906 772

Special 0.875 34.250 47.1 9.42 8.97 96.6 921 328.9 398.9 12.42 14904 828

Special 0.938 34.124 46.3 9.42 8.93 103.3 915 351.3 396.0 12.40 15893 883

Special 1.000 32.000 45.4 9.42 8.90 110.0 908 373.9 393.1 12.38 16855 936

Special 0.312 41.376 121.3 11.0 10.83 40.9 1345 138.9 582.2 14.74 8879 423

STD 0.375 41.250 119.4 11.0 10.80 49.0 1336 166.7 578.7 14.72 10621 506

Special 0.438 41.124 117.6 11.0 10.77 57.2 1328 194.4 575.1 14.67 12353 588

XS 0.500 41.000 115.9 11.0 10.73 65.2 1320 221.6 571.7 14.67 14037 668

42 Special 0.562 40.876 114.1 11.0 10.70 73.2 1312 248.7 568.2 14.65 15710 748

D=42.00 Special 0.625 40.750 112.4 11.0 10.67 81.2 1304 276.2 564.7 14.64 17393 828

Special 0.750 40.500 109.0 11.0 10.60 97.2 1288 330.5 557.8 14.59 20685 985

Special 0.812 40.376 107.3 11.0 10.57 105.1 1280 357.2 554.4 14.56 22295 1062

Special 0.875 40.250 105.6 11.0 10.54 113.0 1272 384.4 550.9 14.54 23916 1139

Special 0.938 40.124 104.0 11.0 10.50 121.0 1264 411.4 547.5 14.52 25522 1215

Special 1.000 40.000 102.4 11.0 10.47 128.8 1257 437.9 544.1 14.50 27088 1290



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Fluor Daniel

MaterialE = Modulus Of Elasticity - ksi (multiply tabulated values by 103), For Temp Degrees F

Temperature - Degrees F

-325 -200 -100 70 200 300 400 500 600 700 800 900 1000 1100 1200 1300 1400 1500

Carbon steelswith carboncontent 0.30%or less

31.4 30.8 30.2 29.5 28.8 28.3 27.7 27.3 26.7 25.5 24.2 22.4 20.4 18.0

Carbon steelswith carboncontent above0.30%

31.2 30.6 30.0 29.3 28.6 28.1 27.5 27.1 26.5 25.3 24.0 22.2 20.2 17.9 15.4

Carbon-Mollysteels. Lowchrome steels(2-1/4 Cr thru3 Cr)

32.6 32.8 31.4 30.6 29.8 29.4 28.8 28.3 27.7 27.1 26.3 25.6 24.6 23.7 22.5 21.1 19.4

Intermediatechrome steels(5 Cr thru -9Cr)

32.9 32.3 31.7 30.9 30.1 29.7 29.0 28.6 28.0 27.3 26.1 24.7 22.7 20.4 18.2 15.5 12.7

Austeniticsteels (TP304,310, 316, 321,347)

30.3 29.7 29.0 28.3 27.6 27.0 26.5 25.8 25.3 24.8 24.1 23.5 22.8 22.1 21.2 20.2 19.2 18.1

StraightChromiumsteels (12 Cr,17 Cr, 27 Cr)

31.2 30.7 30.1 29.2 28.5 27.9 27.3 26.7 26.1 25.6 24.7 22.2 21.5 19.1 16.6

Gray Cast Iron 13.4 13.2 12.9 12.6 12.2 11.7 11.0 10.2

Note!!!These data are for information only. Verify suitability of materials for intended service at temperatures shown withMetallurgist or Piping Material Engineer.



FLUOR DANIEL

MODULUS OF ELASTICITY FOR FERROUS MATERIAL

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Fluor Daniel

MaterialE = Modulus Of Elasticity - ksi (multiply tabulated values by 103), For Temp Degrees F

Temperature - Degrees F

-325 -200 -100 70 200 300 400 500 600 700 800 900 1000 1100 1200 1300 1400 1500

Monel 400 27.8 27.3 26.8 26.0 25.4 25.0 24.7 24.3 24.1 23.7 23.1 22.6 22.1 21.7 21.2

Copper - Nickel(70 Cu - 30 Ni)

23.3 22.9 22.7 22.0 21.5 21.1 20.7 20.2 19.6 18.8

AluminumAlloys (6061 &6063)

11.1 10.8 10.5 10.0 9.60 9.20

Copper(99.8% Cu)

16.9 16.6 16.5 16.0 15.6 15.4 15.0 14.7 14.2 13.7

Leaded TinBronze (88 Cu -6 Sn-1.5 Pb 4.5Zn)

14.8 14.6 14.4 14.0 13.7 13.4 13.2 12.9 12.5 12.0

36% NickelSteel (Invar) 36Ni

19.2 19.5 20.0 20.8 21.5 22.0 22.5 22.6 22.6

Note!!!These data are for information only. Verify suitability of materials for intended service at temperatures shown withMetallurgist or Piping Material Engineer.



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MODULUS OF ELASTICITY FOR NONFERROUS MATERIAL

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PURPOSEThis practice is intended as an aid for the Piping Designer in determining the effects of thepiping's thermal expansion or contraction on equipment nozzles.

SCOPE

This practice provides a method, which can be used by the Piping Designer, to determine theacceptability of pipe routings to rotating equipment. Included in this practice are instructionson how to determine the following:

The location of the rotating equipment's Anchor.

The allowable loads on the rotating equipment nozzles.

The loads exerted by the piping on the rotating equipment.

Methods for adding flexibility if the actual force exerted exceeds the allowable force.

APPLICATION

During the initial stages of piping layout, the Piping Designer needs to examine the effects thatthe thermal expansion or contraction of a piping system would have on rotating equipment towhich the given system is located. Optimum equipment location, nozzle orientations, and piperouting can be achieved via the implementation of the techniques outlined in this practice.

The resulting pipe routing is still subject to the review and approval of the review andapproval of the assigned Lead Project Stress Engineer. However, based on the PipingDesigner's correct application of this technical practice, modification to satisfy stressrequirements should be minimized.

Note!!! Refer to Attachments 01 through 04, as indicated below, to determine the location ofequipment Anchors and, therefore, nozzle thermal movements, on various types ofrotating equipment.

Pumps, Normal Case

Refer to Attachment 01, Pumps - Normal Case.

Pumps, Variation CaseRefer to Attachment 02, Pumps - Variation Case.

Turbines, Normal CaseRefer to Attachment 03, Turbines - Normal Case, Figure 1.

Turbines, CommonVariation

Refer to Attachment 03, Turbines - Common Variation, Figure 2.


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STRESS DESIGN - LAYOUT AIDS FOR ROTATING EQUIPMENT

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Centrifugal CompressorRefer to Attachment 04, Centrifugal Compressor.

Allowable LoadsThe maximum allowable force on steel equipment nozzle is 200 pounds times the nominalnozzle size, but must not exceed 2,000 pounds.

Examples:

2-inch, 300 pounds, RF, CS Nozzle, 200 by 2 = 400 pounds

18-inch, 150 pounds, RF, CS Nozzle, 200 by 18 = 3,600 pounds

The latter exceeds the limit; therefore, use 2,000 pounds as a limiting force.

The maximum allowable force on cast iron equipment nozzle is 50 pounds times nominalnozzle size, but must not exceed 500 pounds.

Examples:4-inch, 125 pounds, FF, CI Nozzle, 50 by 4 = 200 pounds

12-inch, 250 pounds, FF, CI Nozzle, 50 by 12 = 600 pounds

The latter exceeds the limit; therefore, use 500 pounds.

EXAMPLERefer to Attachment 05, How to Determine Pipe Length Required For Flexible Pump Layout.

Allowable Force OnPump Nozzle

Eight-inch nozzle times 200 lbs / nom. in. = 1,600 pounds maximum force allowed.

Expansion North-SouthDirection

The 15'-6" leg is the only run in the North-South direction.

15'-6" times 0.0362 = 0.5611" expansion.

Absorbing LegsThe 2 legs 90 degrees to the 15'-6" leg are the East-West leg (11'-0") plus the vertical leg(7'-3").

Total available bending leg = 11'-0" plus 7'-3" = 18'-3".

Nomograph ApplicationRefer to Attachment 06, Nomograph Application - North-South Expansion.


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Expansion East-WestDirection

Assuming that 1 pump is hot and 1 cold, the 11'-0" leg is the only run, expanding in theEast-West direction.

11'-0" times 0.362"/14 = 0.3982" expansion

Absorbing Legs

The legs 90 degrees to the East-West run are the 2 vertical legs (6'-8" and 7'-3") and theNorth-South leg (15'-6").

Total Available Bending Leg = (6'-8") + (7'-3") + (15'-6") = 29'-5".

Nomograph ApplicationRefer to Attachment 07, Nomograph Application - East-West Expansion.

Expansion VerticalDirection

The worst case vertical thermal expansion occurs between the Anchor point at the pumpassumed hot and the support or Anchor on the vertical vessel. The total vertical leg expandingis:

(1'-4") + (7'-3") + (6'-8") + (2'-9") = 18'-0"

18'-0" times 0.0362 "/' = 0.6515" expansion

Absorbing LegsThe legs 90 degrees to the vertical runs and falling along a direct line from the vessel nozzleto the nozzle of the pump assumed hot, are the 11'-0" North-South leg and the 15'-6"East-West leg.

Total Available Bending Leg = (11'-0") + (15'-6") = 26'-6".

Nomograph Application

Refer to Attachment 08, Nomograph Application - Vertical Direction, and Attachment 09,Nomograph A (For Flexibility Based On Piping Force).

ATTACHMENTS

Attachment 01: (11Feb00)Pumps - Normal Case

Attachment 02: (11Feb00)Pumps - Variation Case

Attachment 03: (11Feb00)Figure 1. Turbines - Normal CaseFigure 2. Turbines - Common Variation


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Attachment 04: (11Feb00)Centrifugal Compressor

Attachment 05: (11Feb00)Example: How To Determine Pipe Length Required For Flexible Pump Layout

Attachment 06: (11Feb00)Nomograph Application - North-South Expansion

Attachment 07: (11Feb00)Nomograph Application - East-West Expansion

Attachment 08: (11Feb00)Nomograph Application - Vertical Direction

Attachment 09: (11Feb00)Nomograph A (For Flexibility Based On Piping Force)


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(Note!!! Refer to circled numbers on Nomograph A - Attachment 09)

Step 1 On the force scale, locate maximum allowed force on pump nozzle. 1,600 pounds (Point 1).

Step 2 On Total Thermal Expansion scale, locate expansion in inches. 0.5611" (Point 2).

Step 3 Draw a line from Point 1 to Point 2. Where this line crosses the Pivot Line , locate Point 3.

Step 4 On Nominal Pipe Diameter scale, locate line size 12" (Point 4). When the schedule of pipe is other than the standardweight, use Pipe Moment of Inertia scale. This locates Point 5 on the Pipe Length scale.

Step 5 Draw a line from Point 3 on the Pivot Line to Point 4 on the Nominal Pipe Diameter scale. This locates Point 5 onthe Pipe Length scale.

Read 23'-0" on the Pipe Length scale as the minimum required absorbing pipe length.

Step 6 The available bending leg is 18'-3" (Refer to Page 2) is less than 23'-0". Therefore, a minimum of 5'-0" must beadded to the vertical or East-West direction to be within the maximum allowable force on the pump nozzle.

Step 7 Since equipment elevations cannot be easily changed (both Process and Structural Engineering must becomeinvolved), the simplest method for adding the required bending leg is to add East-West bending leg as shown bydotted line on Attachment 05.



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NOMOGRAPH APPLICATION - NORTH-SOUTH EXPANSION

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Step 1 On the force scale, locate maximum allowed force on the pump nozzle - 1,600 pounds (Point 1).

Step 2 On total thermal expansion scale, locate expansion in inches - 0.3982" (Point 6).

Step 3 Draw a line from Point 1 to Point 6. Where this line crosses the pivot line, locate Point 7.

Step 4 On nominal pipe diameter scale, locate line size 12" (Point 4).

Step 5 Draw a line from Point 7 to Point 4. This locates Point 8 on the pipe length scale.

Note!!! The minimum required absorbing pipe length is 20'-0".

Step 6 The available bending leg is 29'-5" which is greater than the required leg of 20'-0". Therefore, no additionalflexibility is required to accommodate the East-West expansion.



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NOMOGRAPH APPLICATION - EAST-WEST EXPANSION

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Step 1 On the force scale, locate maximum allowed force on the pump nozzle - 1,600 pounds (Point 1).

Step 2 On the total thermal expansion scale, locate expansion in inches - 0.6516" (Point 9).

Step 3 Draw a line from Point 1 to Point 9. Where this line crosses the pivot line, locate Point 10.

Step 4 On a nominal pipe diameter scale, locate line size 12" (Point 4).

Step 5 Draw a line from Point 10, on the pivot line, to Point 4. This locates Point 11 on the pipe length scale.

Note!!! The minimum required absorbing pipe length (bending leg) is 24'-0".

Step 6 The available bending leg is 26'-6" that is greater than the required leg of 24'-0".



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NOMOGRAPH APPLICATION - VERTICAL DIRECTION

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Practice 000 250 2040Date 11Feb00

Page 1 of 5

PLANT ARRANGEMENT - TYPICAL UNIT PLOT ARRANGEMENT

/0002502040.doc Piping Engineering

PURPOSE

This practice establishes recommended guidelines to assist the Piping Designer fordevelopment of a unit plot arrangement.

SCOPEThis practice is arranged in the following major sections:

• RESPONSIBILITY

• ARRANGEMENT OF EQUIPMENT

• EQUIPMENT AND PIPEWAY CLEARANCES

• PIPEWAY LAYOUT

• REFERENCES

• ATTACHMENTS

APPLICATIONThis practice is to be used as a guideline for the development of the unit Plot Plan.

RESPONSIBILITY

It is the Lead Piping Supervisor's responsibility to ensure that this guideline isfollowed, along with any specific client requirements.

ARRANGEMENT OFEQUIPMENT

Note!!! The numbers enclosed in parentheses below refer to specific notes in circleson Attachments 01, 02, and 03.

Equipment Structures

The plant layout of equipment shall utilize common structures for equipment vesselsand pumps. As a rule single installation of equipment will not require a structure.

Vertical Vessels

Vertical vessels (A1) will be on a given centerline established by the largest vessel.The shell of the largest vessel will be 2'- 0" from the aisleway reference line.

Vessels that are considered larger than the average vessel (A1.1) in a unit, will beestablished independently with the shell located 2'- 0" from the aisleway referenceline.

Manways in vertical vessels will normally be located on the side of the vessel awayfrom the pipe rack. This leaves the pipe rack side clear for pipes going to and fromthe rack. Ladders will be located on either side of the vessel.

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Stacking two or more vertical vessels shall be investigated. This investigation shallconsider the process conditions (commodities, temperatures, pressures), verticalheight limitations, and piping layout for economic advantages. The stacking ofvessels requires the acceptance of Process and Vessel engineering.

HorizontalVessels

Horizontal vessels (A2) will have the head of the largest vessel line up with theaisleway reference line. All other horizontal vessels in the same vicinity will have acommon tangent line coordinate with the largest vessel. It may be economical foradjacent vessels to share a common saddle coordinate to utilize a commonfoundation.

The minimum elevation from grade is usually shown on the P&ID if it is critical forprocess reasons. If no elevation is expressed and minimum is required, care shouldbe taken to allow adequate clearance for piping.

Exchangers

Shell and tube heat exchangers (A3.1) will be lined up with their channel heads awayfrom the pipeways, so that tube withdrawal is toward the outside of the unit.

The shell heads will be lined up so that the largest head is in line with the aislewayreference line. All other exchangers are to be lined up to have a common channelnozzle coordinate. It may be economical for adjacent exchangers to share a commonsaddle coordinate to utilize a common foundation.

"G"- fin or fin tube type exchangers will be located (A3.2) with the centerline of theshell nozzles lined up and located such that all piping remains clear of the aislewayreference line.

Horizontal reboilers (A3.3) will preferably be located next to the equipment theyservice.

Pumps

Locate pumps close to the equipment from which they take suction (A4.1). Pumpshandling flammable products are not to be located under pipeways carrying majorproduct lines, air coolers, or vessels. Pumps handling non-flammable products maybe located under pipeways and air cooled exchangers.

Pumps located between pipeways and equipment row should be located to avoidbeing hazardous to pipeway and equipment. Industrial Risk Insurers IM.2.5.2 (IRI)indicates the minimum distance to be 10 feet clear (A4.2); this distance should beverified by the clients requirements.

Layout pump suctions and discharges on common centerlines, allowing the use ofcommon pipe supports (A4.3).

AircoolersAircoolers will normally be located above the pipeways (A5).

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Furnaces

Furnaces should be located upwind or sidewind from the rest of the unit and beseparated by at least 50 feet.

Compressors

Compressors should be located downwind from the rest of the unit, be separatedfrom the other equipment, and preferably not located in an enclosed building.

Valve Manifolds

Operational valve manifolds, control valve manifolds and utility stations (A6) are tobe located for operability and access.

EQUIPMENT ANDPIPEWAY CLEARANCES

Walkways2'- 6" horizontal by 7'- 0" vertical (C1.1).

Aisleway

For forklift or similar equipment 6'- 0" horizontal by 8'- 0" vertical. For portablemanual equipment operation 3'- 0" horizontal by 8'- 0" vertical (C1.2).

Access Way

Mobil equipment access (hydraulic cranes, trucks, etc.) 10'- 0" horizontal by 10'- 0"vertical (C1.3).

Flange Clearance

Between adjacent equipment (example: shell and tube heat exchangers) 1'- 6"clearance between flanges if no other access is required (C2).

Foundation Footings

Minimum (2'- 6") walkway clearances are required between foundations of anyequipment and any adjacent equipment or piping.

Pump Clearances

For pumps extending under the pipeways, a minimum 10'- 0" (C4.1) clearance isrequired between pumps at opposite sides of the rack. This clearance need not be ina straight line down a series of pumps under the rack.

Minimum clearance of 3'- 0" is required between pumps (C4.2). The 3'- 0"dimension is a minimum requirement between adjacent equipment, foundation orpiping.

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Exchanger Clearances

Clear aisleway for exchanger shell head removal will be 6'- 0" when using a fork lifttruck or portable "A" frame (C4.3).

3'- 0" clear platform is required when using a mobile crane positioned at channel endto remove shell cover (C4.3.1).

3'- 0" clear when shell cover is fixed and removal is not required.

Miscellaneous Clearances

Platforms will be 1'- 0" minimum clear of piping or pipeway (C4.4.1). Allowclearance for drain funnels in front of pumps (C4.4.2).

Road Clearances

The requirements for drainage ditches or underground pipeway easement mayincrease the dimension from the edge of roads to equipment (C5).

PIPEWAY LAYOUT

For pipeway support elevations (P1), refer to Practice 000.250.2041: PlantArrangement - Pipeway Layout - Allowable Pipe Spans.

• Pipe support spacings shall be maximized using the limits of pipe spans andstructural integrity.

Location of electrical and instrument raceways will be determined by one of thefollowing:

• When electrical is located primarily aboveground (P2.1), raceways for electricaland instruments will be located as shown (vertical or horizontal, with horizontalbeing the alternate location), taking care not to interfere with pipe turn-outs andexpansion loops.

• On projects where electrical is predominately aboveground, the top level of thepipeway (P2.2) will be reserved for electrical and instrument raceways.

Drop space (P3), if required, for utility, steam trap, or vent piping drop space widthis set by minimum clearance for largest line and may be on either or both sides ofpipeway as required.

The centerline of line drops (P4) will normally be 2'- 0" from centerline of P.S.column or end of cantilever, whichever is applicable. Special consideration needs tobe given to large diameter lines.

Width of rack (P5) will be determined by the flow diagram transposition.

Refer to Practice 000.250.2010: Plant Arrangement - Flow Diagram TranspositionInstructions.

For pipe support spacing (P6), refer to Practice 000.250.2041.

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REFERENCES

Piping EngineeringPractice 000.250.2005: Plant Arrangement - Plot Plan Development

Instructions

Piping EngineeringPractice 000.250.2010: Plant Arrangement - Flow Diagram Transposition

Instructions

Piping EngineeringPractice 000.250.2015: Plant Arrangement Location Control Plan

Instructions

Piping EngineeringPractice 000.250.2041: Plant Arrangement - Pipeway Layout – Allowable

Pipe Spans

ATTACHMENTS

Attachment 01: (11Feb00)Unit Plot Arrangement

Attachment 02: (11Feb00)Section Thru Pipeway, Standard Arrangements

Attachment 03: (11Feb00)Space Allocation At Support Columns

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PURPOSEThis practice defines the responsibilities of the Piping Designer for layout, design, and supportof all piping systems.

SCOPE

This practice includes the following major sections:

RESPONSIBILITY

TERMINOLOGY

STRESS DESIGN RESPONSIBILITIES

SUPPORT CRITERIA

STRESS ENGINEER RESPONSIBILITIES

REFERENCES

APPLICATIONThis practice applies to all Piping Designers on all Fluor Daniel projects.

RESPONSIBILITYAssigned Project Piping Engineer, Lead Design Supervisor, and Lead Stress Engineer areresponsible for implementing this practice.

TERMINOLOGYLayout and Design: The arrangement of all equipment; the routing of the piping thatconnects the equipment; and the conceptual definition of hard supports, pre-engineered,and engineered supports.

Hard Supports: Structural steel or concrete structures provided by the structuraldepartment.

Pre-Engineered Supports: Supports such as base supports, rod hangers, shoes, guides,and anchors as shown in the detail practices listed in Piping Engineering Practice000.250.50201: Piping Support Elements.

Engineered Supports: Supports such as spring hangers, spring can base supports,snubbers, and constant support spring hangers specially designed by Stress Engineer for aspecific location. Engineered supports will be listed in Piping Engineering Practice 000250 50201.

STRESS DESIGNRESPONSIBILITIES

OverviewPiping Designer will create a sound piping layout and a design that includes the followingitems:


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STRESS DESIGN - RESPONSIBILITIES

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Accurate interpretation of the P&ID (Piping And Instrumentation Diagram).

Routing of the line.

Correct mechanical construction of the piping materials and components.

An evaluation of the line's workability regarding stress and flexibility.

Incorporating Stress Engineer's comments and requirements on lines analyzed by stress.

Proper support of the line during operation, maintenance, and hydrotest.

Stress Engineer supports Piping Designer's effort. Stress Engineer verifies that the designmeets applicable criteria; assists in finding solutions to complex problems; helps to optimizethe original layout of equipment and equipment support requirements; and designs engineereditems such as spring hangers and flexible joints.

Policy StatementPiping Designer is responsible for the layout, design, and support of all piping systems and isalso responsible for the following items, obtained by using the applicable sections of thePiping technical practices:

Locating supports, guides, anchors, compressor hold downs, and hanger rods.

Providing prespring, cold spring, and clearance required for line expansion and additionalline flexibility.

Transmitting and handling stress sketches in complete compliance with proceduresoutlined in Piping Engineering Practice 000.250.2220: Stress Design - Sketch Procedure.

Piping Designer is not responsible for the flexibility calculations nor the validity of suchcalculations made by the Stress Engineer. Designer is responsible for any calculations orflexibility analysis that was undertaken and resolved without Stress Supervisor's approval.

Design Guidelines

The following guidelines apply to piping design stress considerations:

Prefer pipe routing, fittings, and loops to provide flexibility. Where space and otherlimitations preclude this approach, request assistance from Project Lead Stress Engineer.

Design piping to require a minimum number of anchors and guides.

Keep weight stresses off equipment nozzles using base supports and anchors, or rodhangers or structural supports.

To obtain flexibility that accommodates expansion at towers and drums, arrange theequipment locations and nozzle orientations so that the natural run of the piping willprovide sufficient flexibility.

Note!!! For hot piping, do not locate nozzles so that the most direct pipe routing is theend result.

When computing stresses and allowing for expansion, use the worst case operatingconditions (hot line and cold tower, or vice versa, or both: 1 pump hot, 1 pump cold).

Consider startup conditions when lines and equipment are brought up to operatingconditions from the cold conditions. Consider flexibility for lines that may be steam orhot gas purged and that are subject to regeneration, decoking, and dryout conditions.Ensure that outdoor piping in cold climates can contract the required amount.

Investigate expansion, or the lack of it, in closed relief systems and hot blowdownsystems.


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Calculate and correctly apply the thermal expansion of the pipe to select the proper shoelength.

Incorporate rigid supports for exhaust stacks of relief systems venting to the atmosphere.

To avoid differential expansion problems, investigate equipment tube anchors on verticaland horizontal tube heaters.

Investigate cold piping conditions at bypasses around exchangers.

Make the branch lines more flexible rather than installing expansion loops or expansionjoints in the header.

Investigate spring supporting or Teflon mounting pumps instead of using flexible pipingon hot pump suction lines.

Apply cold spring and prespring to piping for the following reasons:

- Detailed stress analysis requires it.

- It maintains adequate pipe spacing.

Take cold spring into account during analysis, and indicate it on drawings to ensure sounddesign.

To maintain adequate pipe spacing, use cold spring to make clearance corrections in pipegroups or racks, thus preventing excessive spreading between lines. Line size has nobearing on this. Show cold spring with 50 percent of the total movement at operatingtemperature. There is no minimum limit to the amount of cold spring that may be used;however, consider using less than 1 inch cold spring only where dictated by the designconditions.

Use extreme care in selecting the maximum temperature used to calculate expansion. Theoperating temperature often is not the maximum temperature experienced by the processlines. For instance, most process lines must be steamed out at higher temperatures thanthose encountered during normal operation.

Both Piping Designer and Stress Engineer must investigate using engineered expansionjoints and other flexible connectors to eliminate piping forces on equipment. Noexpansion joint, either metal or elastomer bellows, shall be specified or purchased withoutthe approval of Stress Group Supervisor or Project Lead Stress Engineer.

Guide axial expansion joints on each side and anchor at changes of direction of pipe runsto take hydrostatic thrust, friction force, velocity thrust, and the mechanical spring rate ofthe joint.

SUPPORT CRITERIAHard supports and pipe supported by pre-engineered or engineered element are to be designedin, not added on.

During layout, Designer should plan, visualize, define, and communicate to Stress Engineerthe method of support for all pipe lines.

Talk early with Structural Engineer to establish concepts and schedule requirements.Continue this communication throughout the project, providing detailed definitions of supportlocations, anchor locations, anchor forces, and other data required for support design.


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STRESS ENGINEERRESPONSIBILITIES

Lead Stress Engineer must validate calculations and flexibility analysis provided to PipingDesigner and must further validate items listed in Policy 1 of the Pipe Stress Analyst DesignGuide (refer to Piping Engineering Practice 000.250.1201: Piping Stress Analysis - GeneralOperating Practices.

REFERENCESPiping EngineeringPractice 000.250.1201: Piping Stress Analysis - General Operating Practices

Piping EngineeringPractice 000.250.1202: Piping Stress Analysis - Limiting Criteria On Equipment

Piping EngineeringPractice 000.250.2220: Stress Design - Sketch Procedure

Piping EngineeringPractice 000.250.50201: Piping Support Elements


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PIPING DESIGN LAYOUT TRAININGLESSON 1- STRESS TEST

Page 1 of 615/11/2002 Rev. 0

STRESS TESTName __________________________________

Instructions: Place all answers in the spaces provided. Use the back of this sheet for calculations.Attach additional sheets if required. Please show your work. Minumum passing grade is 71.

True or False (First Ten Questions) (Each Question is Worth 3 Points)

1. _______ Carbon steel at 500F expands more than stainless steel at 480F.

2 ._______ A spring hanger is placed over a pump to reduce thermal forces.

3. _______ If all other conditions are identical, a 6" SCH 80 piping system will have largerforces than a 6" SCH 40 system.

4. _______ Every spool on a job must be sent to Stess.

5. _______ The expansion into a pipeway loop can never exceed 10" or the anchor forcewould be too great.

6. _______ When locating pipeway anchors, balancing friction forces isn't important.

7. _______ All long runs on a pipe rack should have an anchor.

8. _______ If a guide is added to a bending leg, the stress changes.

9. _______ If two anchors are not moved, but the piping between them is rerouted, the freeexpansion in the North-South, East-West, and vertical directions is not changed.

10._______ A given size pipe filled with water spans a greater distance than when filled withsteam.

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11. Using your judgement, what is the best orientation of a nozzle (8") on vessel B, if a pipeline (C.S. @ 350F) is to be routed between vessels A and B. (Ignore vertical movements.)

Give answer as N, S, E or W. DO NOT MAKE A CALCULATION!__________ (2 pts)

12. Find the FREE thermal expansion in inches at Point "A" (Indicate direction).

DISTANCE DIRECTION

_________ (3 pts) _________ (1 pt)

_________ (3 pts) _________ (1 pt)

_________ (3 pts) _________ (1 pt)

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13. Find the vertical thermal expansion at nozzles A,B, C and D. The average temperature of each section is given below. Also give the direction of movement. (Up or Down)

DISTANCE: DIRECTION:

A. ___________ (3 pts) ___________ (1 pt)

B. ___________ (3 pts) ___________ (1 pt)

C. ___________ (3 pts) ___________ (1 pt)

D. ___________ (3 pts) ___________ (1 pt)

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16A. Calculate the thermal forces at pump "A" nozzle. Also indicate direction. (Interpolate if the bend leg is midway between two values.)

Pump "A" is operating.Pump "B" is spare.

DIRECTION:

a. T.F. (Vert.):_______________ (4pts) ___________ (1 pt)

b. T.F. (Horz.):_______________ (4pts) ____________ (1 pt)

16B. If the temperature is increased to 630F and the allowable T.F. on the pump nozzle is 1200lbsin any direction.

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a. Show ALL calculations on this page (Ignore weight) (3 pts)

b. Figure: T.F. (Vert.): _______________ (3 pts)

T.F. (Hor.): _______________ (3 pts)

c. Will the current configuration work ______________ (1 pt)

d. If not, draw recommended configuration on this page. (2 pts)

e. Figure: Rerouted T.F. (Vert.) _______________ (3 pts)

Rerouted T.F. (Hor.) _______________ (3 pts)

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17. PUMP SUCTION LINE

a) Calculate the thermal forces at the pump. T.F. (Vert.) :_____________ (3pts)

T.F. (Horz.) :_____________ (3 pts)

b) Are the T.F.'s allowable? __________ (1 pt)

c) Is the max. stress below 10,000 PSI? __________ (1 pt)

d) Considering the load on the pump due to the weight ofthe piping system, and using the "span" chart, is, in youropinion, the line self-supporting? __________ (1 pt)

e) If the T.F. (vert.) and the force due to weight are to be considered asacting simultaneously, what is your recommendation?

_____________________________________________________________

______________________________________________________________. (3 pts)

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PIPE STRESS TEST GRADING MASTERPage 1 of 7

15/11/2002 Rev. 0

PIPE STRESS TEST- GRADING MASTERName ___________________________________

Instructions: Place all answers in the spaces provided. Use the back of this sheet for calculations.Attach additional sheets if required. Please show your work.

True or False (First Ten Questions) (Each Question is Worth 3 Points)

1. ___F___ Carbon steel at 500F expands more than stainless steel at 480F.

2. ___F___ A spring hanger is placed over a pump to reduce thermal forces.

3. ___T___ If all other conditions are identical, a 6" SCH 80 piping system will have largerforces than a 6" SCH 40 system.

4. ___F___ Every spool on a job must be sent to Stess.

5. ___F___ The expansion into a pipeway loop can never exceed 10" or the anchor forcewould be too great.

6. ___F___ When locating pipeway anchors, balancing friction forces isn't important.

7. ___T___ All long runs on a pipe rack should have an anchor.

8. ___T___ If a guide is added to a bending leg, the stress changes.

9. ___T___ If two anchors are not moved, but the piping between them is rerouted, the freeexpansion in the North-South, East-West, and vertical directions is not changed.

10. ___F___ A given size pipe filled with water spans a greater distance than when filled withsteam.

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11. Using your judgement, what is the best orientation of a nozzle (8") on vessel B, if a pipeline (C.S. @ 350F) is to be routed between vessels A and B. (Ignore vertical movements.)

Give answer as N, S, E or W. DO NOT MAKE A CALCULATION!__SOUTH__ (2 pts)

12. Find the FREE thermal expansion in inches at Point "A" (Indicate direction).

DISTANCE DIRECTION

_3.068"__ (3 pts) ____E____ (1 pt)

_.642"___ (3 pts) ____N____ (1 pt)

_.642"___ (3 pts) ____D____ (1 pt)

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13. Find the vertical thermal expansion at nozzles A,B, C and D. The average temperature of each section is given below. Also give the direction of movement. (Up or Down)

DISTANCE: DIRECTION:

A. __1.742"___ (3 pts) __UP______ (1 pt)

B. ____.23"___ (3 pts) __DOWN___ (1 pt)

C. ___1.00"___ (3 pts) __UP______ (1 pt)

D. __1.455"___ (3 pts) __UP______ (1 pt)

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16A. Calculate the thermal forces at pump "A" nozzle. Also indicate direction. (Interpolate if the bend leg is midway between two values.)

Pump "A" is operating.Pump "B" is spare.

DIRECTION:a. T.F. (Vert.):_900# to 1100#_ (4pts) __DOWN___ (1 pt)

b. T.F. (Horz.):_800# to 1000#_ (4pts) __WEST____ (1 pt)

CALCULATIONS:

T.F. (Vert.) = .0316 X 11.5 = .36Bending Leg = 14'-0"T.F. = 900# to 1100#

T.F. (Hor.) = = .11Bending Leg = 10'-0"T.F. = 800# to 1000#

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16B. If the temperature is increased to 630F and the allowable T.F. on the pump nozzle is 1200lbsin any direction.

a. Show ALL calculations on this page (Ignore weight) (3 pts)

b. Figure: T.F. (Vert.): __1500# to 1700#_ (3 pts)

T.F. (Hor.): __1400# to 1600#_ (3 pts)

c. Will the current configuration work _____NO______ (1 pt)

d. If not, draw recommended configuration on this page. (2 pts)

e. Figure: Rerouted T.F. (Vert.) ___600# to 800# _ (3 pts)

Rerouted T.F. (Hor.) __800# to 1000#_ (3 pts)SKETCH:

CALCULATIONS:

[With configuration as is (Question 16A)]

T.F. (Vert.) = .0511 X 11.5 = .588 T.F. (Hor.) = = .179Bending Leg = 14'-0" Bending Leg = 10'-0"T.F. = 1500# to 1700# T.F. = 1400# to 1600#

[With rerouted configuration (above)]

T.F. (Vert.) = .0511 X 11.5 = .588 T.F. (Hor.) = = .179Bending Leg = 18'-0" Bending Leg = 12'-0"T.F. = 600# to 800# T.F. = 800# to 1000#

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17. PUMP SUCTION LINE

a) Calculate the thermal forces at the pump. T.F. (Vert.) :_800# to 900#_ (3pts)

T.F. (Horz.) :_400# to 500#_ (3 pts)

b) Are the T.F.'s allowable? __YES____ (1 pt)

c) Is the max. stress below 10,000 PSI? __YES____ (1 pt)

d) Considering the load on the pump due to the weight ofthe piping system, and using the "span" chart, is, in youropinion, the line self-supporting? __YES____ (1 pt)

e) If the T.F. (vert.) and the force due to weight are to be considered asacting simultaneously, what is your recommendation?

__SPRING HANGER FROM THE BEAM ABOVE THE PUMP.___________

_____________________________________________________________. (3 pts)

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PIPE STRESS TESTGRADING MASTER

Encircle each wrong answer on the students test. Minimum passing grade is 71.

(Correct pts) (Maximum)Total points for Questions 1 through 10 (True / False) _________ (30 pts)Points for Question 11 _________ (2 pts)Total points for Question 12 (6 answers) _________ (12 pts)Total points for Question 13 (8 answers) _________ (16 pts)Total points for Question 16A (4 answers) _________ (10 pts)Total points for Question 16 B (5 answers, sketchand calculations) _________ (18 pts)Total points for Question 17 (6 answers) _________ (12 pts)

Grade Average _________ Total (100 pts)

GRADE AVG:

100-96 EXCELLENT 95-83 VERY GOOD 82-71 GOOD 70 and below FAIL

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