Given:
A 0.25-inch thick steel tank is supported on four base plates. The tank contains water at 150 °F and is partially filled. The tank is in a 70 °F stagnant environment.
Ambient air at 70°F ho = 1.5E-6 BTU/(s*°F*in 2 ) |
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Heated air at 150°F hi = 4.7E-7 BTU/(s*°F*in 2 ) |
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Heated water at 150°F hi = 1.3E-4 BTU/(s*°F*in 2 ) |
Ambient air at 70°F ho = 1.6E-6 BTU/(s*°F*in 2 ) |
Find: The thermal stress and displacement due to the contents.
This particular analysis uses a two-step analysis procedure. First, the temperature distribution of the model is calculated using a steady state heat transfer analysis. Second, the temperature is imported into a stress analysis to calculate the thermal expansion.
This example concentrates on performing the analysis, not on the creation of the model. Therefore, the model geometry is provided. Model setup consists of applying the loads as convection, and performing the analysis.
The effects of the hot water (and air above the water) will be simulated in the analysis by applying a convection load, as follows:
The effects of the ambient air around the gussets will be simulated in the analysis by applying a convection load.
The effects of the heat conducting out of the support plate, into the support pier, and convecting into the environment will be simulated with a heat flux on the model, as follows.
Use Setup Model Setup
Parameters to view the Analysis Parameters dialog box. The only input required for this analysis is the Convection multiplier. This value controls the convection and heat flux. The other multipliers are acceptable with the default of 1 because there are no loads affected by the multipliers.
Run the analysis using the Analysis Analysis
Run Simulation command.
Review the temperature results when the analysis is done: Results Contours Temperature
Calculated Temperature. The range should be 92 to 149°F, with the following criteria:
To better see the temperature drop along the top of the tank, create a path plot of the temperature.
The next stage of the analysis is to perform the stress analysis. Refer to the page Examples: Linear and Dynamic Stress: Thermal Stress of a Tank for the continuation.
Hand Calculations
One disadvantage of the plate element is that only one convection load can be applied per surface. The convection inside the tank and natural convection outside the tank cannot be applied individually. These two effects must be combined together and applied to the model as one convection load. The heat transfer on the inside and outside can be written as follows:
Q = hi x A x (150°F - Tcalc) + ho x A x (70°F - Tcalc) |
(1) |
where h is the convection, A is the area, and Tcalc is the calculated temperature at a node. In the model, the heat transfer can be written using an equivalent convection coefficient (he) and equivalent convection temperature (Te) as follows:
Q = he x A x (Te - Tcalc) |
(2) |
When these two equations are set equal to each other, the unknowns he and Te can be solved by forcing the heat transferred via the calculated temperatures to be equal, and the heat transferred via the environment temperatures to be equal, or
(hi + ho)x A x Tcalc = hex A x Tcalc |
(3) |
hi x A x 150°F + ho x A x 70°F = he x A x Te |
(4) |
Equation (3) yields the calculation for the equivalent convection coefficient
he = hi + ho |
(5) |
and solving equation (4) for the equivalent environment temperature and substituting equation (5) yields
Te = (150 x hi + 70 x ho) / (hi + ho) |
(6) |
The convection conditions shown in Figure 1 were calculated with the Film/Convection Coefficient Calculator, so equations (5) and (6) yield the equivalent conditions in Table 1 that are applied to the model:
Table 1: Convection Calculations
Location |
Inside Convection hi, BTU/(s*°F*in 2 ) |
Outside Convection ho, BTU/(s*°F*in 2 ) |
Equivalent Convection he, BTU/(s*°F*in 2 ) |
Equivalent Ambient Temperature Te, °F |
---|---|---|---|---|
Below water level | 1.3E-4(buoyancy, turbulent vertical plate, 150 F ambient, 148 F wall, water properties at 149 F) | 1.6E-6(buoyancy, turbulent vertical plate, 70 F ambient, 148 F wall, air properties at 109 F) | 1.32E-4 | 149 |
Air space above water level (top of tank) | 4.7E-7(buoyancy, laminar horizontal plate facing down, 150 F ambient, 105 F bulk average of top, air properties at 127 F) | 1.5E-6(buoyancy, turbulent horizontal plate facing up, 70 F ambient, 105 F bulk average of top, air properties at 88F) | 1.97E-6 | 89 |
The conduction out of the 4x8 inch support pad can be estimated by using equations for a fin. Think of the tank as sitting on a 4x8 inch concrete pier {k = 1.3E-5 BTU/(s*°F*in)}. The tank end of the pier is maintained at a hot temperature, and cooling around the pier {h = 1.6E-6 BTU/(s*°F*in 2 )} creates an arrangement identical to a fin. As an approximation, assume the pier is long enough so that the floor end is at the ambient temperature {Tamb = 70°F}. The equation for the heat loss from such as fin is
Q = (T-Tamb) [h x perimeter x k x A] 0.5 |
(7) |
If the pad is around 135°F, this equation yields
Q = (135-70°F) [1.6E-6 BTU/(s*°F*in 2 ) x 24 in x 1.3E-5 BTU/(s*°F*in) x 32 in 2 ] 0.5 = 8.2E-3 BTU/s
or on a per area basis, Q = (8.2E-3 BTU/s)/(32 in 2 ) = 2.6E-4 BTU/(s*in 2 ).