Can the global (accumulated) discretization error be less than the local error during a step? Explain.

Short Answer

Expert verified
Answer: Although theoretically possible in rare cases where local errors significantly cancel each other out, the global discretization error is typically larger than the local error during a specific step in numerical integration methods. This is because the global error accumulates local errors across all steps in the process.

Step by step solution

01

Define Local and Global Discretization Errors

Local discretization error is the error that occurs during a single step of numerical integration, which arises because the numerical method is using an approximate solution instead of the true solution. The local error is a measure of the difference between the true solution and the approximate solution for a particular step. Global discretization error, on the other hand, is the accumulated error over all steps in the numerical integration process. It gives an overall idea of how accurate the numerical solution is compared to the true solution over the entire interval.
02

Relationship Between Local and Global Discretization Errors

In numerical integration methods, the global error is an accumulation of local errors that occur during each step of the process. Since the local error is the error for a single step and the global error is the sum of these local errors for all steps, the global error is generally larger than a single local error. However, it may be possible that some of the local errors will cancel each other out (e.g., positive and negative errors) when estimating the global error. The method's error analysis would determine the exact impact of the local errors on the global error. In such cases, it is theoretically possible for the global error to be smaller than the local error for a particular step of the process. However, this situation is relatively unlikely.
03

Conclusion

In summary, while it is theoretically possible for the global (accumulated) discretization error to be smaller than the local error during a specific step, this situation is relatively rare. The global error is typically larger than the local error, as it accumulates the local errors across all steps in the numerical integration process. To have a smaller global error in such cases, local errors would need to cancel each other out in a significant manner, which is not frequently observed.

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Most popular questions from this chapter

Consider steady one-dimensional heat conduction in a pin fin of constant diameter \(D\) with constant thermal conductivity. The fin is losing heat by convection to the ambient air at \(T_{\infty}\) with a convection coefficient of \(h\), and by radiation to the surrounding surfaces at an average temperature of \(T_{\text {surr }}\). The nodal network of the fin consists of nodes 0 (at the base), 1 (in the middle), and 2 (at the fin tip) with a uniform nodal spacing of \(\Delta x\). Using the energy balance approach, obtain the finite difference formulation of this problem to determine \(T_{1}\) and \(T_{2}\) for the case of specified temperature at the fin base and negligible heat transfer at the fin tip. All temperatures are in \({ }^{\circ} \mathrm{C}\).

For a one dimensional steady state variable thermal conductivity heat conduction with uniform internal heat generation, develop a generalized finite difference formulation for the interior nodes, with left surface boundary node exposed to constant heat flux and right surface boundary node exposed to convective environment. The variable conductivity is modeled such that the thermal conductivity varies linearly with the temperature as \(k(T)=k_{o}(1+\beta T)\) where \(T\) is the average temperature between the two nodes.

The wall of a heat exchanger separates hot water at \(T_{A}=90^{\circ} \mathrm{C}\) from cold water at \(T_{B}=10^{\circ} \mathrm{C}\). To extend the heat transfer area, two-dimensional ridges are machined on the cold side of the wall, as shown in Fig. P5-76. This geometry causes non-uniform thermal stresses, which may become critical for crack initiation along the lines between two ridges. To predict thermal stresses, the temperature field inside the wall must be determined. Convection coefficients are high enough so that the surface temperature is equal to that of the water on each side of the wall. (a) Identify the smallest section of the wall that can be analyzed in order to find the temperature field in the whole wall. (b) For the domain found in part \((a)\), construct a twodimensional grid with \(\Delta x=\Delta y=5 \mathrm{~mm}\) and write the matrix equation \(A T=C\) (elements of matrices \(A\) and \(C\) must be numbers). Do not solve for \(T\). (c) A thermocouple mounted at point \(M\) reads \(46.9^{\circ} \mathrm{C}\). Determine the other unknown temperatures in the grid defined in part (b).

The explicit finite difference formulation of a general interior node for transient heat conduction in a plane wall is given by $$ T_{m-1}^{i}-2 T_{m}^{i}+T_{m+1}^{i}+\frac{\dot{e}_{m}^{i} \Delta x^{2}}{k}=\frac{T_{m}^{i+1}-T_{m}^{i}}{\tau} $$ Obtain the finite difference formulation for the steady case by simplifying the relation above.

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