LCLS-II 2K Cold Box Transfer Line Nozzle Analysis and ... · calculate the allowable nozzle loads...

Pressure Systems Documentation-Calculations

Title: 2K Cold Box Transfer Line Nozzle Analysis

Note Number: 79222-P0004

Author(s): Connor Kaufmann of 12

Pressure Systems Documentation - 2K Cold Box Transfer Line Nozzle Analysis Page 1

LCLS-II 2K Cold Box Transfer Line Nozzle

Analysis and Allowable Loads

Revision History:

Revision Date Released Description of Change

- 01/03/2018 Original release, Issued for Project use

Connor Kaufmann

JLab Cryogenics Group

Mechanical Engineer

Nate Laverdure


Mechanical Engineering Lead

Joe Matalevich


Lead LCLS-II Cold Design

Fredrik Fors

JLab Mechanical Engineering Group

Mechanical Engineer

Approved: 1/11/2018; E-Sign ID : 356883; signed by: DCG: T. Fuell; Re. 1: N. Laverdure; Re. 2: F. Fors; Re. 3: J. Matalevich |






Table of Contents

1.0 Introduction .......................................................................................................................................... 3 2.0 Nozzle Design and Analysis Approach ............................................................................................... 4 3.0 Basis of Allowable Loads ..................................................................................................................... 4 4.0 Vessel Nozzle Junction Stresses Calculation Using WRC 107/537 .................................................. 5 5.0 Nozzle Stresses ...................................................................................................................................... 8 6.0 Weld Stresses at Vessel/Nozzle Junction ............................................................................................ 9 7.0 Replacement Area Calculation ........................................................................................................... 9 8.0 Conclusion and Summary ................................................................................................................. 12 9.0 References ........................................................................................................................................... 12 Appendix A ................................................................................................................................................ 12







1.0 Introduction

The purpose of this Engineering Note is to document the analysis that was performed to ensure

adequate nozzle design for the LCLS-II 2K Cold Box. A secondary motivation was also to

calculate the allowable nozzle loads that the main transfer line may safely impart on the 2K Cold

Box Vacuum Shell. Figure 1 provides a graphical representation of the 2K Cold Box nozzle that

connects to the main transferline. This nozzle connection joins the vacuum jacket (clamshell) of

the Sub-Atmospheric Return to the 2K Coldbox vacuum shell.

This report discusses the nozzle connection design (Section 2), the basis of the analysis that was

performed (Section 3), the calculations (Sections 4 through 7) and the summary / conclusion

(Section 8).

Figure 1: CP1 2K Cold Box Main Transfer Line Nozzle

CP1 2K Cold Box Vessel

CP1 Main Transfer Line

Nozzle Connection

Clamshell Section Approved: 1/11/2018; E-Sign ID : 356883; signed by: DCG: T. Fuell; Re. 1: N. Laverdure; Re. 2: F. Fors; Re. 3: J. Matalevich |






2.0 Nozzle Design and Analysis Approach

In order to receive the incoming Sub-Atmospheric Helium return pipe to the suction of the cold

compressors, a nozzle was designed on the 2K Cold Box vessel. As per standard cryogenic

design, a vacuum jacket is required for process piping in order to minimize heat transfer to

ambient temperature. The focus of this analysis is the nozzle which connects the main transfer

line vacuum jacket to the cold box vacuum shell. As the 2K cold box is an internal JLab design

and the main transfer line is an outside vendor design, it is necessary to limit the loads that the

transfer line may transmit to the 2K coldbox. The 2K coldbox is designed to ASME BPVC 2013,

and thus it is the responsibility of the designers (JLab) to determine a combination of forces and

moments which satisfy code allowable stresses.

To evaluate allowable external loads on the 2K cold box nozzle, the following approach was

taken:

1. Analyze vessel stresses at nozzle/vessel junction using WRC 107/537

2. Analyze nozzle stresses from external forces/moments

3. Analyze weld stresses at nozzle/vessel junction

4. Analyze replacement area required by ASME BPVC

Relevant vessel/nozzle design data are listed in Table 2.1.

Table 2.1: Vessel/Nozzle Design Data

3.0 Basis of Allowable Loads

To analyze the effect of external forces and moments on a nozzle connection to a pressure vessel,

it is industry standard practice to use finite element analysis or an analytical solution called WRC

107/537. Per ASME BPVC Section VIII Division 2 §4.5.15(a), localized stress calculations from

external loads may be calculated using WRC 107. WRC 107 is a graphical solution method

developed by the Welding Research Council for stresses in the vessel based on forces/moments

from the nozzle. In 2010, WRC 537 was released for polynomial fitting data on the WRC 107

graphs, allowing for programmable solutions. To this effect, the WRC 107/537 approach is

conducive for parametrization of external loads and obtaining fast results for nozzle induced

stresses.

Name Symbol Vessel Nozzle Unit

Material Specification - SA 516 Gr. 70 SA 312 TP304/304L -

Basic Allowable Stress in Tension S 20 20 ksi ASME BPVC 2013 SII-D Table 1A

Size Specification - 144" OD x 0.75" W 20 NPS Sch. 10S -

Outside Diameter D 144 20 in

Wall Thickness T 0.750 0.218 in

Vessel and Nozzle Data

Note Approved: 1/11/2018; E-Sign ID : 356883; signed by: DCG: T. Fuell; Re. 1: N. Laverdure; Re. 2: F. Fors; Re. 3: J. Matalevich |






Typically for nozzle connections on vessels that are small and exert negligible loads, the WRC

analysis can be ignored. However, for large nozzles with seismic loads, such as the main transfer

line nozzle (24 NPS), it is reasonable to expect that vessel stresses are critical. Therefore, an

allowable set of nozzle loads should be determined by the vessel designer as a safe upper limit.

Determining the allowable loads for a nozzle connection is inherently a difficult mathematical

problem, as one must determine a single linear combination of the load set {𝐹𝑥, 𝐹𝑦, 𝐹𝑧, 𝑀𝑥,𝑀𝑦, 𝑀𝑧} which results in a stress state less than or equal to the given allowable stress. Since

there are an infinite number of solutions (nozzle loads) that satisfy this constraint, the load set

should logically be parametrized.

From mechanics is known that radial forces and non-torsional moments on the nozzle result in

the highest primary stresses on the vessel, while shears and torsional moments result in

secondary (shear) stresses. In terms of loading, the vessel is much more sensitive to primary

stresses than secondary stresses, and therefore the loads that exert primary stresses are designated

the driving variables for parametrization.

For simplicity in the case of the 2K Cold Box Nozzle, the Radial Force (P) has been designated

as the driving variable, and all other loads are a function of the Radial Force. Because the entire

process has been parameterized, any particular force or moment can be the driving factor, or the

relationship between the loads can be changed. From this point forward, WRC 107/537 can

compute the stress and confirm it is below code allowable limits.

For the sake of conservatism, the strengthening effect of the reinforcement pad was not

considered when analyzing the external loads.

4.0 Vessel Nozzle Junction Stresses Calculation Using WRC 107/537

The first step of calculating the vessel nozzle junction stresses was to determine the loads on the

nozzle end, and convert them into the WRC 537 coordinates. From the parametrization in

Section 3, relationships were selected for the forces and moments as a function of the driving

radial force. Table 4.1 illustrates this parametrization of loads. Figure 4.1 demonstrates the

coordinate axes of the loads, and Figure 4.2 shows the conversion of these nozzle end loads into

the WRC coordinated system which is in the plane of the vessel/nozzle junction.

Table 4.1: Nozzle Load Definition

Name Symbol Vessel Nozzle Unit

Design Pressure - 15 15 psi

Longitudinal Shear Fx - 7,500 lbf Fx = 0.5*Fz

Circumferential Shear Fy - 7,500 lbf Fy = 0.5*Fz

Radial Force Fz - 15,000 lbf Driving Variable

Circumferential Moment Mx - 270,000 lbf-in Mx = 1.5*Fz*e

Longitudinal Moment My - 270,000 lbf-in My = 1.5*Fz*e

Torsional Moment Mz - 180,000 lbf-in Mz = 1.0*Fz*e

Parameterization

Nozzle Loads Definition at Nozzle End Approved: 1/11/2018; E-Sign ID : 356883; signed by: DCG: T. Fuell; Re. 1: N. Laverdure; Re. 2: F. Fors; Re. 3: J. Matalevich |






Figure 4.1: Global Axes for Nozzle Loads

Figure 4.2: WRC 537 Loads in Plane of Vessel Junction

Once the forces and moments have been determined in the correct coordinate system, non-

dimensional values for Primary Membrane (PM), Local Membrane (PL), Bending (Pb), and

Secondary (Q) stresses are computed using WRC 537 polynomial fit parameters. These non-

dimensional parameters are multiplied by the appropriate loads to calculate stresses in the vessel.

The stress classifications are totaled for the circumferential and longitudinal directions of the

vessel, and then the scalar valued stress intensity is computed.







As an example, to find the circumferential stress in the vessel borne only from the radial load (P), the local membrane induced stress and the bending load induced stress are algebraically totaled. Table 4.2 below depicts the

tabulation of the WRC 537 calculation. As per WRC convention, the stress is calculated at eight points (AU,AL,BU,BL,CU,CL,DU,DL) clocked around the nozzle, and the maximum stress classification result is taken.

𝜎𝜑(𝑃) =𝑁𝜑

𝑃/𝑅𝑚∗

𝑃

𝑅𝑚 ∗ 𝑇±𝑀𝜑

𝑃∗6𝑃

𝑇2

Figure Parameter Stress Category Value AU AL BU BL CU CL DU DL Unit Notes

3C Nφ/(P/Rm) PL 9.5937 2,679 2,679 2,679 2,679 psi

4C Nφ/(P/Rm) PL 14.0743 3,930 3,930 3,930 3,930 psi

1C Mφ/P Pb 0.0736 11,773 -11,773 11,773 -11,773 psi

2C-1 Mφ/P Pb 0.0420 6,722 -6,722 6,722 -6,722 psi

3A Nφ/[Mc/(Rm2β)] PL 3.9171 -1,500 -1,500 1,500 1,500 psi

1A Mφ/[Mc/(Rm-β)] Q 0.0777 -17,051 17,051 17,051 -17,051 psi

3B Nφ/[ML/(Rm2β)] PL 10.5840 8,106 8,106 -8,106 -8,106 psi

1B-1 Mφ/[ML/(Rm-β)] Q 0.0269 11,806 -11,806 -11,806 11,806 psi

Circumferential Pressure Stress PM - 1,425 1,425 1,425 1,425 1,425 1,425 1,425 1,425 psi

Primary Memb. Circ. Stress PM + PL - 13,461 13,461 -2,751 -2,751 2,604 2,604 5,604 5,604 psi

Primary Memb. + Bend. Circ. Stress PM + PL + Pb - 20,183 6,740 3,970 -9,473 14,377 -9,169 17,377 -6,169 psi

Total Circumferential Stress PM + PL + Pb + Q - 31,989 -5,066 -7,835 2,333 -2,674 7,882 34,428 -23,220 psi

3C Nx/(P/Rm) PL 9.5937 2,679 2,679 2,679 2,679 psi

4C Nx/(P/Rm) PL 14.0743 3,930 3,930 3,930 3,930 psi

1C-1 Mx/P Pb 0.0752 12,025 -12,025 12,025 -12,025 psi

2C Mx/P Pb 0.0418 6,687 -6,687 6,687 -6,687 psi

4A Nx/[Mc/(Rm2β)] PL 7.1824 -2,750 -2,750 2,750 2,750 psi

2A Mx/[Mc/(Rm-β)] Q 0.0381 -8,354 8,354 8,354 -8,354 psi

4B Nx/[ML/(Rm2β)] PL 3.8623 2,958 2,958 -2,958 -2,958 psi

2B-1 Mx/[ML/(Rm-β)] Q 0.0365 16,039 -16,039 -16,039 16,039 psi

Longitudinal Pressure Stress PM - 713 713 713 713 713 713 713 713 psi

Primary Membrane Longitudinal Stress PM + PL - 6,349 6,349 433 433 1,892 1,892 7,393 7,393 psi

Primary Memb. + Bend. Long. Stress PM + PL + Pb - 18,375 -5,676 12,458 -11,592 8,579 -4,795 14,080 706 psi

Total Longitudinal Stress PM + PL + Pb + Q - 34,414 -21,715 -3,581 4,447 225 3,559 22,435 -7,649 psi

Shear Stress from MT - - 382 382 382 382 382 382 382 382 psi

Shear Stress from VC - - -318 -318 318 318 psi

Shear Stress from VL - - 318 318 -318 -318 psi

Total Shear Stress - - 64 64 700 700 700 700 64 64 psi

Total Primary Membrane PM + PL - 13,462 13,462 3,479 3,479 3,033 3,033 7,395 7,395 psi * Stress Intensity

Total Primary Memb. + Bending PM + PL + Pb - 20,185 12,416 12,516 2,540 14,460 4,592 17,378 6,876 psi * Stress Intensity

Total Combined PM + PL + Pb + Q - 34,416 16,649 4,479 4,658 3,220 7,993 34,428 15,572 psi * Stress Intensity

Table 4.2: WRC 107/537 Stress Calculation

Local Membrane Bending







In this case, the stress classifications are compared with to ASME BPVC Section VIII Division 1

and 2 allowable limits. A comparison of calculated stresses and allowable limits is shown in

Table 4.3.

Table 4.3: Comparison of Calculated Vessel Stresses to Allowable Limits

Since calculated stresses are below allowable limits with an additional safety factor of about 1.5,

the 2K cold box nozzle is sufficiently designed to withstand the allowable loads from Table 4.1.

The loads from Table 4.1 shall form the allowable limit for the transfer line loads on the 2K Cold

Boxes.

As the WRC 537 calculation process is tedious and complicated, the complete calculation

process was coded into MS Excel Visual Basic in order to automate the routine. For reference,

both the calculation workbook and the code are in Appendix A. In order to verify the accuracy of

the developed WRC 537 nozzle Excel program, the intermediate and final results were compared

to a commercially available product Bentley AutoNozzle. The differences in the results were less

than 5% and well within the margin for acceptable error in what was originally a hand-calculated

graphical method.

5.0 Nozzle Stresses

Since the WRC 107/537 calculates stresses in the vessel only, there must be additional

verification to ensure that stresses from external loads are not exceeded in the nozzle itself. To

this end, by using basic solid mechanics equations for axial loads, bending, shear and torsion,

one can calculate the induced stresses in the nozzle from external loads. All the external loads

from Table 4.1 result in nozzle stresses lower than allowable limits, and thus are acceptable.

These calculations have been documented in Table 4.4.

Stress Category Symbol Value Unit

PM + PL - 13.46 ksi

PM + PL + Pb - 20.19 ksi

PM + PL + Pb + Q - 34.43 ksi

- S 20.00 ksi ASME BPVC 2013 SII-D Table 1A

PM + PL SPM 24.00 ksi ASME BPVC 2013 SVIII D1 UG-23(d)

PM + PL + Pb SPM + SB 30.00 ksi ASME BPVC 2013 SVIII D1 UG-23(c)

PM + PL + Pb + Q SPS 60.00 ksi ASME BPVC 2013 SVIII D1 UG-23(e)

TRUE -

- S 20.00 ksi ASME BPVC 2013 SII-D Table 1A

PM + PL SPL =1.5S 30.00 ksi ASME BPVC 2015 Section VIII D2 5.2.2.4(a)

PM + PL + Pb SPL =1.5S 30.00 ksi ASME BPVC 2015 Section VIII D2 5.2.2.4(a)

PM + PL + Pb + Q SPS = 3S 60.00 ksi ASME BPVC 2015 Section VIII D2 5.5.6.1(d)(1)

TRUE -

Note

Acceptable Vessel Shell Stress per Div. 2

Acceptable Vessel Shell Stress per Div. 1

ASME BPVC 2013 Section VIII

Division 1 Allowable Limits

Maximum Calculated Values

ASME BPVC 2015 Section VIII

Division 2 Allowable Limits

Name Approved: 1/11/2018; E-Sign ID : 356883; signed by: DCG: T. Fuell; Re. 1: N. Laverdure; Re. 2: F. Fors; Re. 3: J. Matalevich |






Nozzle Stress Analysis from UG-22 External Loading

Name Symbol Value Unit Notes

Long. Stress from Pressure - 0.34 ksi = P*Ri/(2t)

Long. Stress from Radial Force - -1.11 ksi = F/(π(Ro2-Ri2)

Long. Stress from Bending Mom. - 6.07 ksi = (MC2+ML

2)0.5Ro/Ixx

Long. Primary Stress (Max Compressive) - 6.84 ksi

Long. Primary Stress (Max Tensile) 5.30 ksi

Allowable Primary Memb. Stress SPM 15.80 ksi (Compressive)

Acceptable Primary Stress - TRUE -

Nozzle Shear Stresses

Name Symbol Value Unit Notes

Shear Stress from Shear Forces - 1.58 ksi = (VL2+VC

2)0.5/(π*Ri*t)

Shear Stress from Torsion - 1.37 ksi = MT/(2π*Ri2*t)

Shear Stress in Total τ 2.96 ksi

Allowable Shear Stress τ* 16.8 ksi

Acceptable Shear Stress - TRUE -

Table 4.4: Nozzle Stresses Induced by External Loads

6.0 Weld Stresses at Vessel/Nozzle Junction

The nozzle is a set-through nozzle with a penetration of 1 inch past the vessel wall. As the weld

is a full penetration weld per ASME BPVC Section VIII Division 1 UW-16(s), with a 3/8” fillet

cap weld, it is necessary to verify the weld can withstand these external forces and moments. The

calculation for the weld strength due to nozzle loads is shown below in Table 6.1 and Figure 6.1.

The analysis technique is per Blodgett’s “Weld as a Line” method, which resolves are forces and

moments into unit forces per length onto a fictitious weld represented by line elements. By

assuming the resolved unit force acts as pure shear on the fillet weld, the minimum size for the

weld is calculated as about 1/16”. As the specified weld size is 3/8”, the weld has been

sufficiently sized. Also conservatively, only the externally facing weld was considered, and not

the interior vessel weld on the set-through nozzle which has the same size.

7.0 Replacement Area Calculation

For any type of nozzle, regardless of external loading, it is important to verify that it is in

conformance with ASME replacement area calculations. The replacement area calculations are

shown in Table 7.1 below. As the replacement area exceeds the required area, the nozzle has

been sufficiently designed.







Nozzle/Vessel Fillet Weld Stress Analysis

Name Symbol Nozzle A Unit Notes

Nozzle Material Specification - SA-312 304/304L -

Nozzle Allowable Stress S 20 ksi ASME BPVC 2013 SVIII D1 UG-23(a)

Nozzle Size - 20 NPS Sch. 10S -

Nozzle Outside Diameter - 20.000 in

Nozzle Wall Thickness - 0.218 in

Nozzle Length/Eccentricity e 12.000 in

Fillet Weld Specified Size (Leg) w 3/8 in

Fillet Weld Acting Diameter Dw 20.000 in

Fillet Weld Total Length L 62.832 in = π Dw

CG to Fiber Distance Cx 10.000 in = Dw/2

CG to Fiber Distance Cy 10.000 in = Dw/2

CG to Fiber Distance Cz 0.000 in

Fillet Weld Inertia Ix 3141.593 in3 = (π/8) Dw3

Fillet Weld Inertia Iy 3141.593 in3 = (π/8) Dw3

Fillet Weld Inertia Iz 6283.185 in3 = Ix + Iy

Fillet Weld Allowable Stress Sw 9.8 ksi Conservatively assume fillet weld in shear per UW-15(c)(3)

Radial Force P -15,000 lbf

Circumferential Moment MC 180,000 lbf-in

Circumferential Shear VC -7,500 lbf

Longitudinal Moment ML -360,000 lbf-in

Longitudinal Shear VL -7,500 lbf

Torsional Moment MT 180,000 lbf-in

Force in X-Direction Fx 7,500 lbf Please note, origin of coordinate axis not per original nozzle

axis, but translated to be in the plane of the fillet weld Force in X-Direction Fy 7,500 lbf

Force in X-Direction Fz 15,000 lbf

Moment in X-Direction Mx 180,000 lbf-in

Moment in Y-Direction My 360,000 lbf-in

Moment in Z-Direction Mz 180,000 lbf-in

Lineal Force in X-Direction fx -167 lbf/in

Lineal Force in Y-Direction fy -167 lbf/in

Lineal Force in Z-Direction fz -334 lbf/in

Total Force on Weld f 409 lbf/in

Required Weld Leg Size wreq 1/16 in Rounded up to nearest 32nd

Specified Weld Leg Size w 3/8 in

Acceptable Fillet Weld Size - TRUE -

Table and Figure 6.1: Nozzle Weld Analysis







Nozzle Analysis per ASME BPVC 2013 Section VIII Division 1 UG-37

Name Symbol w/ Pad Unit Note

Basic Design

Design Criteria Pass - TRUE -

Internal Design Pressure P 15 psig

External Design Pressure Pext 15 psid

Vessel Shell

Characteristics

Outside Diameter Do 144 in

Nominal Wall Thickness t 0.750 in

Corrosion Allowance c 0 in

Allowable Stress S 20 ksi ASME BPVC 2013 II-D Table 1A

Joint Efficiency E 0.7 - Type (1) Category D Joint, No Radiography per Table UW-3

Nozzle Penetration

Characteristics

Orientation Type - Radial -

Size Specification - 20 NPS Sch. 10S

Outside Diameter D 20.000 in

Nominal Wall Thickness tn 0.218 in

Wall Undertolerance - 12.5 % ASTM A312

Internal Projection h 1.000 in

Internal Proj.Thickness ti 0.218 in

Inside Nozzle Radius Rn 9.782 in

Corrosion Allowance cn 0 in

Shell Axis to Nozzle CL L - in

Shell Inside Radius R 71.25 in

Required Shell Thickness tr 0.054 in As defined in UG-37

Midsurface Shell Radius Rm 71.277 in

Angle Parameter α - rad

Opening Chord d 19.564 in ASME BPVC 2013 Section VII Division 1 Fig. L-7.7.1

Allowable Stress Sn 20 ksi ASME BPVC 2013 SII-D Table 1A

Joint Efficiency E 0.70 -

Does Not Pass Through Cat. A Joint - TRUE - Per Table UW-3 Classification

Reinforcement Pad

Characteristics

Allowable Stress Sp 20 ksi ASME BPVC 2013 SII-D Table 1A

Pad Diameter Dp 30.125 in

Pad Thickness te 0.750 in

Attachment Weld

Characteristics

Outward Weld Leg Leg41 3/8 in

Outer Pad Weld Leg Leg42 9/16 in

Inward Weld Leg Leg43 3/8 in

UG-37(c)

Reinforcement

Required for

Opening in Shell

(Internal Pressure)

Parallel Reinf. Limit LR 19.564 in UG-40(b)

Normal Reinf. Limit LH 1.295 in UG-40(c)

Nozzle Req. Thickness trn 0.010 in UG-27(c)(1)

Shell Req. Thickness tr 0.054 in UG-37(a)

Strength Reduction Factor fr1 1.000 -

fr2 1.000 -

fr3 1.000 -

fr4 1.000 -

Correction Factor F 1.000 - Fig. UG-37 / UW-16(c)(1) & UW-16(c)(2)

Joint Efficiency E1 0.850 - UG-37(a)

Area Available in Shell A1 11.416 in2

Area Available for Outward Projection A2 0.537 in2

Area Available for Inward Projection A3 0.052 in2

Area Available for Outward Weld A41 0.141 in2

Area Available for RePad Weld A42 0.316 in2

Area Available for Inward Weld A43 0.141 in2

Area Available for RePad A5 7.594 in2

Total Available Area Aavail 20.197 in2

Required Area A 1.056 in2

Sufficient Reinforcement - TRUE -

Table 7: Nozzle Replacement Area Calculation







8.0 Conclusion and Summary

In conclusion, the allowable loads for the 2K Cold Box Transfer Line nozzle have been

established. These established allowable loads meet the allowable stress standards of ASME

BPVC 2013 Section VIII Division 1 and Division 2, and thus the design is acceptable.

9.0 References

[1] Rules for Construction of Pressure Vessels, ASME BPVC 2013 Section VIII Division 1

[2] Rules for Construction of Pressure Vessels: Alternative Rules, ASME BPVC 2015 Section

VIII Division 2

[3] Local Stresses in Spherical and Cylindrical Shells Due to External Loads, WRC Bulletin

107, 2002 Update to 1965 Original version

[4] Precision Equations and Enhanced Diagrams for Local Stresses in Spherical and Cylindrical

Shells Due to External Loadings for Implementation of WRC Bulletin 107, WRC Bulletin

537, 2013 Update to 2010 Original version

[5] Design of Welded Structures, Blodgett, 1966

Appendix A

The calculations, code and supporting files for this technical report are located at:

Document Location

Report M:\cryo\LCLS II ANALYSIS FOLDER\SCB - TL Nozzle\Reports

Excel Calculations M:\cryo\LCLS II ANALYSIS FOLDER\SCB - TL Nozzle\Excel

AutoNozzle Model M:\cryo\LCLS II ANALYSIS FOLDER\SCB - TL Nozzle\AutoNozzle


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