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NASA Scientific and Technical Aerospace Reports

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37<br />

MECHANICAL ENGINEERING<br />

Includes mechanical devices <strong>and</strong> equipment; machine elements <strong>and</strong> processes. For cases where the application of a device or the host<br />

vehicle is emphasized see also the specific category where the application or vehicle is treated. For robotics see 63 Cybernetics,<br />

Artificial Intelligence, <strong>and</strong> Robotics; <strong>and</strong> 54 Man/System Technology <strong>and</strong> Life Support.<br />

20040068130 <strong>NASA</strong> Langley Research Center, Hampton, VA, USA<br />

Recent Developments <strong>and</strong> Status of the Langley Single Vector Balance Calibration System (SVS)<br />

Jones, Shirley M.; Rhew, Ray D.; 2004; 6 pp.; In English; Fourth International Symposium on Strain Gauge Balances, 10-13<br />

May 2004, San Diego, CA, USA; No Copyright; Avail: CASI; A02, Hardcopy<br />

The Langley Research Center (LaRC) Single Vector Balance Calibration System (SVS) was first introduced in 2000 by<br />

Peter Parker. The SVS combines the Design of Experiments (DOE) methodology with a novel load application system. Since<br />

that time three systems have been designed <strong>and</strong> developed with different load range capabilities (ranging from 2 pounds to<br />

3,000 pounds). Approximately fifteen balances have been calibrated <strong>and</strong> their data compared to conventional techniques. This<br />

paper will present results of these comparisons, based on the mathematical models <strong>and</strong> accuracies, <strong>and</strong> discuss differences that<br />

were observed. In addition, changes in the implementation of the initial load schedules developed using DOE will be<br />

highlighted. One of the principles behind DOE is r<strong>and</strong>omization. The initial loading schedules used to date have been<br />

r<strong>and</strong>omized in the traditional DOE sense but not for repeat calibrations or experiments. Implementation of this r<strong>and</strong>omization<br />

within blocks <strong>and</strong> its impact on data quality will be reviewed. Areas of potential future development will be presented which<br />

include changes in the centers to include loads with the force position system in the pure error estimates.<br />

Author<br />

Calibrating; Error Analysis; Mathematical Models<br />

20040070764 Louisiana Tech Univ., Ruston, LA, USA<br />

Elastic-Plastic Thermal Stress Analysis of a High-Pressure Cryogenic Storage Tank<br />

Barker, J. Mark; Field, Robert E., <strong>Technical</strong> Monitor; August 15, 2003; 5 pp.; In English<br />

Report No.(s): EB-2003-08-00005-SSC; No Copyright; Avail: Other Sources<br />

The thermal stresses on a cryogenic storage tank contribute strongly to the state of stress of the tank material <strong>and</strong> its ability<br />

to withst<strong>and</strong> operational stresses. These thermal stresses also affect the growth of any surface damage that might occur in the<br />

tank walls. These stresses are particularly of concern during the initial cooldown period for a new tank placed into service,<br />

<strong>and</strong> during any subsequent thermal cycles. A previous preliminary elastic analysis showed that the thermal stress on the inner<br />

wall would reach approximately 1,000MPa (145,000 psi). This stress far exceeds the ASTM specified room temperature values<br />

for both yield (170MPa) <strong>and</strong> ultimate (485 MPa) strength for 304L stainless steel. The present analysis determines the thermal<br />

stresses using an elastic-plastic model. The commercial software application ANSYS was used to determine the transient<br />

spatial temperature profile <strong>and</strong> the associated spatial thermal stress profiles in a segment of a thick-walled vessel during a<br />

typical cooldown process. A strictly elastic analysis using st<strong>and</strong>ard material properties for 304L stainless steel showed that the<br />

maximum thermal stress on the inner <strong>and</strong> outer walls was approximately 960 MPa (tensile) <strong>and</strong> - 270 MPa (compressive)<br />

respectively. These values occurred early in the cooldown process, but at different times, An elastic-plastic analysis showed<br />

significantly reducing stress, as expected due to the plastic deformation of the material. The maximum stress for the inner wall<br />

was approximately 225 MPa (tensile), while the maximum stress for the outer wall was approximately - 130 MPa<br />

(compressive).<br />

Author<br />

Elastic Properties; Stress Distribution; Thermal Stresses; High Pressure; Storage Tanks; Plastic Properties; Cryogenic<br />

Equipment<br />

20040070814 Texas-Pan American Univ., Edinburg, TX, USA<br />

Improved Temperature Dynamic Model of Turbine Subcomponents for Facilitation of Generalized Tip Clearance<br />

Control<br />

Kypuros, Javier A.; Colson, Rodrigo; Munoz, Afredo; January 2004; 13 pp.; In English<br />

Contract(s)/Grant(s): NAG3-2857; No Copyright; Avail: CASI; A03, Hardcopy<br />

This paper describes efforts conducted to improve dynamic temperature estimations of a turbine tip clearance system to<br />

facilitate design of a generalized tip clearance controller. This work builds upon research previously conducted <strong>and</strong> presented<br />

in <strong>and</strong> focuses primarily on improving dynamic temperature estimations of the primary components affecting tip clearance (i.e.<br />

the rotor, blades, <strong>and</strong> casing/shroud). The temperature profiles estimated by the previous model iteration, specifically for the<br />

118

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