Caesar 2 pipe stress free download

Compare the pump operating loads with and without the structure. Would friction increase the significance of the structure? Page: 8 Tutor m. Task 3: No room for a loop; install an expansion joint instead. Review the types of joint assemblies. A tied expansion joint on the riser and below the valve will be best suited to absorb the horizontal pipe growth over the pump. Use this value to select the number of convolutions.

Then install the expansion joint and analyze its suitability. Check the pump operating loads. Why is it so high?

The catalog shows a 20 convolution joint provides To save time in this examination, the expansion joint will be placed between the flange and pipe rather than between the nozzle and flange. Torsional rotation Ry is 0. Run through the linear interaction formula for a quick check Actual Allowed Ratio Axial 0. Page: 10 Tutor m. Length A of the Standards of EJMA Other convolution counts are available; watch out for fatigue rating of cycles ; consult the manufacturer.

Page: 11 Tutor m. Task 4: What if the long weld neck flange is connected to a vessel? It will be re-connected by the nozzle specification next. The nozzle provides no axial flexibility but the longitudinal and circumferential bending flexibilities appear significant. Page: 12 Tutor m. Results: Compare the updated pump loads. These loads are greatly improved but still exceed the limit of 2.

Including this flexibility in the loop and expansion joint models will be left to the student. Check other structural results and pipe stresses. Conclusion: The drop in load is significant but additional flexibility either the loop or expansion joint is required to satisfy the pump limitations. Assuming that added flexibility for the pump will drop the vessel loads, evaluate the current vessel loads. Stresses are calculated using a Division 1 — Design by Rule — approach while they are evaluated using the Division 2 — Design by Analysis — approach.

Since not all of the Division 2 criteria will be examined here, the Division 1 maximum allowable stress limits defined above will be used rather than the Division 2 design stress intensities. This calculated using pressure stress equations. Pb is bending due to pressure. Additional checks would be required if fatigue failure is anticipated; in which case the peak stresses need be calculated and comparisons be made to the endurance limit.

Test this by running the analysis with and without pressure thrust. Page: 14 Tutor m. Task 5: What effect does friction have on the pump loads? Mz to Table 4 ratio is 2.

The limit is 2. Model: Try 0. Conclusion: Pump loads are very sensitive to system supports and their friction. Page: 15 Tutor m. The limits on model size are reported in the input processor, to inform the user during model construction. The help text details exactly what is expected, why, and when appropriate the code reference. When necessary, the help text shows the expected units for the current data cell.

The same help engine is used to provide program diagnostics in the event of system or program failures. Diagnostic messages are available for computational as well as system abnormalities. All help and diagnostic messages provide complete contact information to ensure users have a variety of methods available for contacting the Intergraph support staff. The input graphics module reduces most input modeling mistakes, by permitting the display of the major elemental data.

Node numbers, restraints, spring hangers, nozzles, tees, bends, expansion joints, and rigid elements can all be shown graphically.

Numeric data such as element lengths, temperatures, and pressures can also be displayed. The interactive rotate, pan, and zoom features of the input module are controlled directly from the cursor pad. A "high light" option is available to selectively plot any portion of the model matching a particular search criteria, such as "all the pipe of a certain temperature.

Additionally, the output graphics can show the direction of restraint action, and the individual details displacements, forces, and stresses on each element in the model as the cursor is moved through the model.

This error checker analyzes the user-specified input and checks it for consistency from both a "finite element" and "piping" point of view. Two types of messages are generated by this error checker, warnings and fatal errors.

Warning messages are conditions which may be errors, but are numerically acceptable. For example, warning messages are generated when a change in direction is encountered, without a bend or tee being specified. Fatal error messages are generated when the specified input data is inconsistent or illogical, for example if the corrosion allowance is larger than the corresponding wall thickness.

Jobs can be analyzed with warning messages, but not with fatal error messages. Interactive Report Review Once a job has been analyzed, the solution results are available for review at any time. The review module is interactive, allowing the selective review of individual output reports for individual load cases.

Reports can be generated in any units system simply by altering the configuration. Reports can be viewed on the terminal screen, or sent to a printer or to a disk file. These libraries contain the necessary parameters required to build the element stiffness matrix as well as dimensioning and detailing data. Graphics Display of Solution Data Once the solution data is available it can alternatively be reviewed in a graphical format.

This presentation shows how the system responds to a particular set of loads by plotting the system in its deformed position. These plots can also include restraint, force, and stress data. These graphics results can be shown on the terminal screen, sent to a printer, or saved in PCX format for incorporation into desktop publishing documents. This customization can be controlled on a directory by directory basis, accommodating different users or different client needs.

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