# On the convergence rate of the Dirichlet–Neumann iteration for unsteady thermal fluid–structure interaction

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## Abstract

We consider the Dirichlet–Neumann iteration for partitioned simulation of thermal fluid–structure interaction, also called conjugate heat transfer. We analyze its convergence rate for two coupled fully discretized 1D linear heat equations with jumps in the material coefficients across the interface. The heat equations are discretized using an implicit Euler scheme in time, whereas a finite element method on one domain and a finite volume method with variable aspect ratio on the other one are used in space. We provide an exact formula for the spectral radius of the iteration matrix. The formula indicates that for large time steps, the convergence rate is the aspect ratio times the quotient of heat conductivities and that decreasing the time step will improve the convergence rate. Numerical results confirm the analysis and show that the 1D formula is a very good estimator in 2D and even for nonlinear thermal FSI applications.

## Keywords

Solid–fluid interaction Finite element Stability Converging Numerical methods## 1 Introduction

The Dirichlet–Neumann iteration is a basic method in both domain decomposition and fluid–structure interaction (FSI). In the latter case, the iteration arises in a partitioned approach [11], where different codes for the sub-problems are reused and the coupling is done by a master program which calls interface functions of the segregated codes. This allows to reuse existing software for each sub-problem, in contrast to a monolithic approach, where a new code is tailored for the coupled equations. To satisfy coupling conditions at the interface, the subsolvers are iterated by providing Dirichlet and Neumann data for the other solver in a sequential manner, giving rise to its name.

In the domain decomposition context, the iteration has two main problems, namely slow convergence and the need for an implementation using a red-black colouring. The slow convergence can be slightly improved using a relaxation procedure. In fluid–structure interaction, there are typically only two domains, coupled along an interface, making the application straight forward. The convergence rate for the interaction of a flexible structure with a fluid has been analyzed in [35]. There, the added mass effect is proven to be dependent on the step size for compressible flows and independent for incompressible flows. However, the convergence rate is not great for some FSI couplings, which is why a lot of effort goes into convergence acceleration [10]. An alternative are optimized Schwarz methods [13, 15, 29] and the CHAMP scheme (Conjugate Heat transfer Advanced Multi-domain Partitioned) which uses a generalized Robin (mixed) condition at the interface to accelerate the iteration [24], but overlapping domains. Furthermore, for incompressible fluids it is known that the ratio of densities of the materials plays an important role [1, 9]. Finally, the Dirichlet–Neumann iteration was reported to be a very fast solver for thermal fluid–structure interaction between air and steel [4].

Our prime motivation here is thermal interaction between fluids and structures, also called conjugate heat transfer. In particular, we consider two domains with jumps in the material coefficients across the connecting interface. Conjugate heat transfer plays an important role in many applications and its simulation has proved essential [2]. Examples for thermal fluid–structure interaction are cooling of gas-turbine blades, thermal anti-icing systems of airplanes [8], supersonic reentry of vehicles from space [19, 23], gas quenching, which is an industrial heat treatment of metal workpieces [17, 33] or the cooling of rocket nozzles [20, 21].

A convergence analysis of the Dirichlet–Neumann iteration for an FE–FE discretization of a steady heat transfer problem can be found in [32]. Asymptotically, it is found to be the quotient of heat conductivities. In this paper, we present a convergence analysis of the unsteady heat transfer problem. For this model, a 1D stability analysis was presented by Giles [16]. There, an explicit time integration method was chosen with respect to the interface unknowns. On the other hand, Henshaw and Chand provided in [18] a method to analyze stability and convergence speed of the Dirichlet–Neumann iteration in 2D based on applying the continuous Fourier transform to the semi-discretized equations. They show that the ratios of thermal conductivities and diffusivities of the materials play an important role. This is similar to the behavior mentioned above for classical FSI with incompressible fluids where the performance is affected by the ratio of densities of the materials [1, 9].

However, in the fully discrete case we observe in some cases that the iteration behaves differently, because some aspects of the problem are not taken into account by the semidiscrete analysis: the effect of \(\varDelta t\) is not accurately represented and neither are possibly different mesh widths in the two problems. This matters particularly for compressible fluids where a high aspect ratio grid is needed to accurately represent the boundary layer. This leads to geometric stiffness that significantly influences the convergence rate, as we will show.

For the fully discrete case, the convergence rate is in principle analyzed in any standard book on domain decomposition methods, e.g. [30, 34]. There, the iteration matrix is derived in terms of the stiffness and mass matrices of finite element discretizations and the convergence rate is the spectral radius of that. However, this does not provide a quantitative answer, since the spectral radius is unknown. Computing it is in general a nontrivial task. In our context, the material properties are discontinuous across the interface and as a consequence, computing the spectral radius of the iteration matrix is even more difficult.

In [26, 28], a convergence analysis of the Dirichlet–Neumann iteration for the unsteady transmission problem using finite element methods (FEM) on both subdomains is presented. A similar analysis using finite differences (FDM) on one domain and FEM on the other one can be found in [27]. In addition, the corresponding analysis when coupling finite volumes (FVM) with FEM is described in [5, 26]. All these results assume equal mesh sizes on both subdomains, i.e, the aspect ratio is equal to one.

Thus, we present here a complete discretization of the coupled problem using FVM in space on one domain and FEM on the other one with variable aspect ratio *r*. We consider this to be a relevant case, because these are the standard discretizations for the subproblems. The implicit Euler method is used for the temporal discretization. Then, we derive the spectral radius of the iteration matrix exactly in terms of the eigendecomposition of the resulting matrices for the one dimensional case. The asymptotic convergence rates when approaching the continuous case in either time or space are also determined. In the spatial limit, the convergence rate turns out to be proportional to the aspect ratio *r*, whereas in the temporal limit, we obtain 0. Note that the temporal limit turns out to be the ratio of the product of densities and heat capacities of the materials for FEM–FEM couplings instead. Moreover, we also include numerical results where it is shown that the one dimensional formula is a very good estimator for a 2D version of the coupled heat equations and for two nonlinear FSI models, namely the cooling of a flat plate and the cooling of a flanged shaft.

An outline of the paper now follows. In Sect. 2, we describe the model and discretization, as well as the coupling conditions and the Dirichlet–Neumann iteration. Two thermal FSI test cases are introduced in Sect. 3: the cooling of a flat plate and of a flanged shaft. For these, we present numerical convergence rates, motivating further analysis. A model problem, consisting of two coupled discretized heat equations, is presented in Sect. 4 and then analyzed in 1D in Sect. 5. In Sect. 6, an extension of the analysis to 2D and different discretizations are discussed. In Sect. 7, the analytical results are compared to linear and nonlinear numerical results.

## 2 Thermal FSI methodology

We consider the basic setting where on a domain \(\varOmega _1 \subset \mathbb {R}^d\) where *d* corresponds to the spatial dimension, the physics is described by a fluid model, whereas on a domain \(\varOmega _2 \subset \mathbb {R}^d\), a different model describing the structure is used. The two domains are connected via an interface. The part of the interface where the fluid and the structure are supposed to interact is called the coupling interface \(\varGamma \subset \partial \varOmega _1 \cap \partial \varOmega _2\). Note that \(\varGamma \) might be a true subset of the intersection, because the structure could be insulated. At the interface \(\varGamma \), coupling conditions are prescribed that model the interaction between fluid and structure. For the thermal coupling problem, these conditions are that temperature and the normal component of the heat flux are continuous across the interface.

### 2.1 Fluid model

*Re*and the Prandtl number

*Pr*appear. The system is closed by the equation of state for the pressure \(p = (\gamma -1) \rho e\), the Sutherland law representing the correlation between temperature and viscosity, as well as the Stokes hypothesis. Additionally, we prescribe appropriate boundary conditions at the boundary of \(\varOmega _1\) except for \(\varGamma \), where we have the coupling conditions. In the Dirichlet–Neumann coupling, a temperature value is enforced at \(\varGamma \).

### 2.2 Structure model

Finally, on the boundary, we have Neumann conditions \(\mathbf {q}_s(\mathbf {x},t) \cdot \mathbf {n}(\mathbf {x}) = q_b(\mathbf {x},t)\).

### 2.3 Coupling conditions

*T*is the fluid temperature and \({\varvec{\Theta }}\) the structure temperature and

### 2.4 Discretization in space

### 2.5 Time discretization

### 2.6 The Dirichlet–Neumann method

The Dirichlet–Neumann method is a basic iterative substructuring method in domain decomposition and it is a common choice for treating FSI problems. Therefore, we now employ it to solve the system (11)–(12). This corresponds to alternately solving equation (11) on \(\varOmega _1\) with Dirichlet data on \(\varGamma \) and (12) on \(\varOmega _2\) with Neumann data on \(\varGamma \).

*k*th iteration the two decoupled equation systems

## 3 Thermal FSI test cases

In this section we present two thermal FSI test cases that are solved using the methodology explained in the previous section. The aim of this paper is to estimate the convergence rate of the Dirichlet–Neumann iteration used as a solver for thermal FSI problems. Therefore, we first want to illustrate the behavior for two examples before proceeding to the convergence analysis in the next section. We consider the cooling of a flat plate and the cooling of a flanged shaft. For the first problem, structured grids are used and for the second, unstructured grids.

For the coupling, the Dirichlet–Neumann method as presented in (13)–(14) is used. A fixed tolerance of 1*e*−8 is chosen for all involved equation solvers. The coupling code used has been developed in a series of papers [4, 6, 7]. It’s main feature is time adaptivity, which is not employed here. The coupling between the solvers is done using the Component Template Library (CTL) [22]. In the fluid, the DLR TAU-Code in its 2014.2 version is employed [14], which is a cell-vertex-type finite volume method with AUSMDV as flux function and a linear reconstruction to increase the order of accuracy. The finite element code uses quadratic finite elements and is the inhouse code Native of the Institute for Static and Dynamic at the University of Kassel.

### 3.1 Flow over a plate

The first test case is the cooling of a flat steel plate resembling a simple work piece [7]. It is initially at a much higher temperature than the fluid and then cooled by a constant laminar air stream, see Fig. 1.

The inlet is located on the left, where air enters the domain with an initial velocity of \(\text{ Ma }_{\infty } = 0.8\) in horizontal direction and a temperature of 273 K. Regarding the initial condition in the structure, a constant temperature of 900 K at \(t=0\) is chosen throughout. To determine the Reynolds number, a reference length of \(\hat{x}_{ref}=0.2\,\mathrm{m}\) is chosen.

The grid is chosen Cartesian and equidistant in the structural part. In the fluid region the thinnest cells touch the boundary and then get coarser in *y*-direction with a maximal aspect ratio of \(r=1.7780e5\). The points of the primary fluid grid and the nodes of the structural grid match on the interface \(\varGamma \) and there are 9660 cells in the fluid region and \(n_x \times n_y = 120 \times 9 = 1080\) elements with \(121 \times 10 = 1210\) nodes in the region of the structure.

The left plot in Fig. 4 shows the convergence behaviour of the Dirichlet–Neumann iteration against the time step \(\varDelta t\). One observes that the convergence rates is roughly proportional to the time step \(\varDelta t\). Furthermore, even for \(\varDelta t=1\) a reduction of the error by a factor of ten per iteration is achieved.

### 3.2 Cooling of a flanged shaft

*x*-direction of Mach 0.005. The Reynolds number, based on a reference length of \(\hat{x}_{ref}=0.02\,\mathrm{m}\) is \(Re = 2500\) and the Prandtl number \(Pr = 0.72\).

Summarizing, the Dirichlet–Neumann iteration is a very fast solver for thermal FSI cases with strong jumps in the material coefficients, as the ones presented here. To understand this better, we perform in the next section a convergence analysis for the case of two coupled linear heat equations.

## 4 A model problem: coupled heat equations

We present here a convergence analysis of the unsteady transmission problem with mixed discretizations. In particular, we choose a finite volume method (FVM) on the first subdomain and a finite element method (FEM) on the second subdomain.

### 4.1 Model problem

### 4.2 Semidiscrete analysis

Before we present in the next section an analysis for the fully discrete equations, we want to describe previous results about the behaviour of the Dirichlet–Neumann iteration for the transmission problem in the semidiscrete case.

*k*) in order to transform the second order derivatives into algebraic expressions. Once they have a coupled system of algebraic equations, they insert one into the other and obtain the Dirichlet–Neumann convergence rate \(\beta \):

*k*is zero. Then, for \(\varDelta t\) small enough, we have \(\tanh \left( -1 / \sqrt{D_2 \varDelta t} \right) \) \(\approx -1 \) and \(\tanh \left( 1 / \sqrt{D_1 \varDelta t} \right) \approx 1 \) and therefore:

Figure 5 shows \(\beta \) as a function of \(\varDelta t\) for \(k=0\). It is almost constant, except for a short dynamic transition between \((\lambda _1/ \lambda _2) \sqrt{D_2/D_1}\) and \(\lambda _1 / \lambda _2\).

Finally, one observes in (20) that the convergence rates of the Dirichlet–Neumann iteration are given by the quotient of thermal conductivities for \(\varDelta t\) large. This suggests that strong jumps in the thermal conductivities of the materials give fast convergence.

### 4.3 Space discretization

### 4.4 Time discretization

### 4.5 Dirichlet–Neumann iteration

We now employ a Dirichlet–Neumann iteration to solve the discrete system (26). This corresponds to alternately solving the discretized equations of the transmission problem (16) on \(\varOmega _1\) with Dirichlet data on \(\varGamma \) and the discretization of (16) on \(\varOmega _2\) with Neumann data on \(\varGamma \).

*k*th iteration the two equation systems

Thus, the Dirichlet–Neumann iteration is a linear iteration and the rate of convergence is described by the spectral radius of the iteration matrix \(\varSigma \).

## 5 One-dimensional convergence analysis

*i*, see Fig. 7. The edges of cell

*i*are then \(x_{i-1/2}\) and \(x_{i+1/2}\) and they form the corresponding dual grid. Moreover, we use the flux function

For the coupling between a compressible fluid and a structure, there would typically be a boundary layer in the fluid, meaning that the mesh would be very fine in direction normal to the boundary, implying \(\varDelta x_1 \ll \varDelta x_2\).

*j*th position, the discretization matrices are given by

*N*as columns. The entries of \(\mathbf V _{N_1}\) and \(\mathbf V _{N_2}\) are not dependent on the entries of \(\alpha _1 \mathbf I - \varDelta t \mathbf A _1\) or \(\mathbf M _2 + \varDelta t \mathbf A _2\) due to their symmetry. Moreover, the matrices \(\varLambda _1\) and \(\varLambda _2\) are diagonal matrices having the eigenvalues of \(\alpha _1 \mathbf I - \varDelta t \mathbf A _1\) or \(\mathbf M _2 + \varDelta t \mathbf A _2\) as entries respectively. These are known and given e.g. in [25, pp. 514–516]:

We are now interested in the asymptotics of (50) with respect to both spatial and temporal resolutions. This corresponds to the computation of two different limits: \(\varDelta t \rightarrow 0\) for a fixed \(\varDelta x_1\) and \(\varDelta x_1 \rightarrow 0\) for a fixed \(\varDelta t\). As an alternative, one could reformulate (50) in terms of \(c:=\varDelta t/ \varDelta x_1^2\) and compute the limits \(c \rightarrow 0\) and \(c \rightarrow \infty \). Both choices give the same results because for a fixed \(\varDelta x_1\), if \(\varDelta t \rightarrow 0\), then \(c \rightarrow 0\) and for a fixed \(\varDelta t\), if \(\varDelta x_1 \rightarrow 0\), then \(c \rightarrow \infty \).

On the other hand, from the spatial asymptotics (55) we can observe that strong jumps in the thermal conductivities of the materials placed in \(\varOmega _1\) and \(\varOmega _2\) will imply fast convergence. This is often the case when modelling thermal fluid–structure interaction, since fluids typically have lower thermal conductivities than structures.

Finally, the aspect ratio *r* also influences the behavior of the fixed point iteration, i.e, the rates will become smaller the higher the aspect ratio, e.g. the higher the Reynolds number in the fluid. This phenomenon is not unknown for PDE discretizations and is referred to as geometric stiffness. As is the case here, refining the mesh to reduce the aspect ratio would lead to faster convergence of the iterative method.

Before presenting numerical results we want to show the results obtained for different space discretization combinations with the same constant mesh width on both subdomains.

## 6 Extension of the analysis

In this section we want to extend the results presented in the previous section by reviewing similar analysis for other choices of space discretizations. In particular, FEM–FEM coupling and 2D FVM–FEM with \(r=1\).

When we compare these with the asymptotics obtained with FVM–FEM discretizations (51)–(55), we observe that while the spatial limit is the same, the temporal limit does not match. This arises from differences in the matrix \(\mathbf S ^{(1)}\) in (30). In the FEM–FEM context, the matrices \(\mathbf S ^{(1)}\) and \(\mathbf S ^{(2)}\) lead to the same expression with only different material coefficients (\(\alpha _1,\,\alpha _2,\,\lambda _1,\,\lambda _2\)). Because of this, the limits of \(\rho (\varSigma )\) are quotients of those coefficients. However, the situation is different in the FVM–FEM context. There, the matrix \(\mathbf S ^{(1)}\) in (32) is missing several mass matrices if we compare it with \(\mathbf S ^{(2)}\) in (33). This unsymmetry between \(\mathbf S ^{(1)}\) and \(\mathbf S ^{(2)}\) causes that the limit of \(\rho (\varSigma )\) when \(\varDelta t \rightarrow 0\) is not balanced between the numerator and the denominator, resulting in 0.

This implies that, opposed to the FVM–FEM case, where convergence can always be achieved by decreasing the time step, for an FEM–FEM coupling, a situation can occur where \(\alpha _1/\alpha _2>\lambda _1/\lambda _2\) and therefore, a decrease in time step can even cause divergence. This is for example the case for an air–water coupling [26].

Secondly, for an aspect ratio of \(r=1\), we were able to extend the 1D results for both FVM–FEM and FEM–FEM to 2D in the following sense (see [5, 26]). In 2D, the iteration matrix \(\varSigma \) is not easy to compute for several reasons. First of all, the matrices \(\mathbf M _1 + \varDelta t \mathbf A _1\) and \(\mathbf M _2 + \varDelta t \mathbf A _2\) are sparse block tridiagonal matrices, and consequently their inverses are not straight forward to compute. Moreover, the diagonal blocks of the same matrices are tridiagonal but their inverses are full matrices.

Due to these difficulties, we approximated the strictly diagonally dominant matrices \(\mathbf M _1 + \varDelta t \mathbf A _1\) and \(\mathbf M _2 + \varDelta t \mathbf A _2\) by their diagonal. Thus, we obtained an estimate of the spectral radius of the iteration matrix \(\varSigma \). This estimator tends to the exact same limits as for the 1D case for both combination of discretizations.

We did not find a way to further extend these results to the high aspect ratio case. However, we will show now by numerical experiments that already the 1D formula (50) is a good estimator for convergence rates in 2D.

## 7 Numerical results

### 7.1 Results in 1D

We first compare the semidiscrete estimator \(\beta \) in (18) with the discrete formula \(|\varSigma |\) in 1D in (50) and experimental convergences rates. The latter are obtained from implementing the Dirichlet–Neumann method (27)–(28). The results are then compared to a reference solution \(u_{ref}\) over the whole domain \(\varOmega \), obtained by choosing a tolerance of 1*e*−10 as a termination criterion.

Physical properties of the materials. \(\lambda \) is the thermal conductivity, \(\rho \) the density, \(c_p\) the specific heat capacity and \(\alpha = \rho c_p\)

Material | \(\lambda \) (W/mK) | \(\rho \) (\(\hbox {kg}/\text{ m }^3\)) | \(c_p\) (J/kg K) | \(\alpha \) (J/K \(\text{ m }^3\)) |
---|---|---|---|---|

Air | 0.0243 | 1.293 | 1005 | 1299.5 |

Water | 0.58 | 999.7 | 4192.1 | 4.1908e6 |

Steel | 48.9 | 7836 | 443 | 3471348 |

Temporal and spatial asymptotics of (50) for the thermal interaction of air at 273 K with steel at 900 K, water at 283 K with steel and air with water

Case | \(\varDelta t \rightarrow 0\) | \(\varDelta x \rightarrow 0\) |
---|---|---|

Air–steel | 0 | 4.9693e−4 \(\cdot \) r |

Water–steel | 0 | 0.0119 \(\cdot \) r |

Air–water | 0 | 0.0419 \(\cdot \) r |

The difference to the semidiscrete analysis in [18] stems from different limits taking place. The semidiscrete analysis implicitly assumes that first a limit \(\varDelta x\) to zero has taken place for \(\varDelta t\) fixed. Thus, a limit first \(\varDelta t\), then \(\varDelta x\) to zero is not addressed by it. This can be seen in Fig. 9 in the following way: for fixed \(\varDelta x\), letting \(\varDelta t\) become very small causes the convergence rate to move into the direction predicted by the fully discrete analysis. However, then keeping this very small \(\varDelta t\) fixed and decreasing \(\varDelta x\) moves that rate back in the vicinity of \(\beta \).

We now want to illustrate how \(|\varSigma |\) in (50) gives the convergence rates and tends to the limits computed previously in (51) and (55). To this end, we present two real data examples. We consider here the thermal interaction between air at 273 K with steel at 900 K and water at 283 K with steel at 900 K. Physical properties of the materials and resulting asymptotics for these two cases are shown in Tables 1 and 2 respectively.

Figures 10 and 11 show the convergence rates for the interactions between air and steel and between water and steel, respectively. On the left we have always fixed \(\varDelta x_1\) and *r* and vary \(\varDelta t\), whereas on the right we have fixed \(\varDelta t\) and *r*, and vary \(\varDelta x_1\). Each plot includes graphs for two different values of *r*. In Fig. 10 we choose \(r=1\) and \(r=100\) to illustrate the effect of a neutral or a high aspect ratio. In Fig. 11 we use \(r=0.01\) and \(r=1\) to illustrate how the rates are affected by a small or a neutral aspect ratio.

Again, \(|\varSigma |\) gives the exact convergence rates. Moreover, one observes that the rates on the left plots in Figs. 10 and 11 tend to 0 as predicted in (51) and on the right plots in Figs. 10 and 11 to \(\delta _r\) as predicted in (55).

*r*. To this end, Fig. 12 shows the convergence rates for the interaction between air and steel. In the left plot we have chosen \(\varDelta x_1\) to be coarse and on the right one to be fine. This explains why the convergence rates on the right plot are closer to the spatial limit \(\delta _r\). Furthermore, there is a roughly proportional relation between the convergence rate and the aspect ratio. For coupling with compressible flows, we typically have a high aspect ratio and therefore, the Dirichlet–Neumann iteration will be slowed down. Furthermore, this shows that it is very important to take the aspect ratio into account to make a reasonable prediction of the convergence rate at all.

### 7.2 2D FVM–FEM results

We now want to demonstrate that the 1D formula (50) is a good estimator for the convergence rates in 2D. Thus, we now consider a 2D version of (16) consisting of two coupled linear heat equations on two identical unit squares, e.g, \(\varOmega _1 = [-1,0] \times [0,1]\) and \(\varOmega _2 = [0,1] \times [0,1]\). We use a non equidistant cartesian grid with aspect ratio *r* on \(\varOmega _1\) and an equidistant grid on \(\varOmega _2\). In order to use (50) as an estimator we decided to take the equidistant mesh width on \(\varOmega _2\) as \(\varDelta x_2\) and the mesh width in *x*-direction on \(\varOmega _1\) as \(\varDelta x_1\).

As before, we present two real data examples described in Tables 1 and 2, namely the thermal interaction between air at 273 K with steel at 900 K and air at 273 K with water at 283 K.

Figures 13 and 14 show the convergence rates for the interactions between air and steel and between air and water in 2D respectively. On the left we always plot the rates for fixed \(\varDelta x_1\) and *r* with variable \(\varDelta t\), whereas on the right we have fixed \(\varDelta t\) and *r* and varying \(\varDelta x_1\). As before, each plot includes two different values of *r*. In Fig. 13 we choose \(r=1\) and \(r=100\) as in the 1D case (see Fig. 10) and in Fig. 14 we use \(r=1\) and \(r=1000\) to illustrate the effect of a neutral or a high aspect ratio. To compute \(\beta \) we use the transverse Fourier mode \(k = i \varDelta y,\,i=0,1,2,\ldots ,N_y\) that maximizes it [see (18)]. One observes that the convergence rates predicted by the one-dimensional formula (50) are almost exactly the ones observed in 2D. Thus, the 1D case gives a very good estimator for the 2D model problem.

### 7.3 Thermal FSI test cases

Finally, we want to relate the results for the two nonlinear applications (the two cooling systems introduced in Sects. 3.1 and 3.2: the cooling of a flat plate and of a flanged shaft) to our analysis. The left plot in Fig. 15 shows the convergence behaviour for the flat plate and the right one for the flanged shaft. We plot the experimental convergence rates, the one-dimensional formula (50), the semidiscrete estimator (18) for the maximizing Fourier mode and the spatial limit \(\delta _r\) specified in (55).

In order to apply the 1D formula (50) here, some assumptions need to be made, since we partly have unstructured meshes and nonuniform temperatures. Thus, we assume air at 273 K on the first subdomain with steel at 900 K on the second subdomain for the cooling of a flat plate and air at 273 K with steel at 1145 K for the cooling of a flanged shaft. The density, heat capacity and heat conductivity of air and the density of steel are given in Table 1. In addition, the heat conductivities and heat capacities of steel at 900 and 1145 K are obtained from the nonlinear coefficient functions (3) and (4) by inserting \(\varTheta = 900\,\mathrm{K}\) or \(\varTheta = 1145\,\mathrm{K}\) respectively. This gives \(\lambda = 39.82\) and \(c_p = 1.3684e3\) for steel at \(900\,\mathrm{K}\) and \(\lambda = 39.8\) and \(c_p = 572.75\) for steel at 1145 K.

*e*−5 which is the width of the fluid cells touching the interface in the

*y*-direction and \(\varDelta x_2 = 1.6667\) which is the width of the structure cells in both directions. Thus, we have an aspect ratio of \(r=1.7780e4\). On the other hand, choosing \(\varDelta x_1\) and \(\varDelta x_2\) for the cooling of a flanged shaft is more difficult due to the unstructured grids. In order to get an upper bound for the aspect ratio

*r*, we choose \(\varDelta x_1 = 1.6538\)

*e*−4 which is the minimum width of all the fluid cells touching the interface in direction normal to the wall and \(\varDelta x_2 = 1.1364\) which is the maximum width of all the structure cells touching the interface tangential to the wall. This gives \(r=6.8713e3\).

From the left plot in Fig. 15 one observes with these choices that (50) predicts the rates accurately for the cooling of a flat plate. Note that the semidiscrete estimator \(\beta \) does not show any change with \(\varDelta t\). Remember that \(\beta \) is almost always constant, except for a short dynamic transition between \((\lambda _1 /\lambda _2) \sqrt{D_2/D_1}\) and \(\lambda _1/\lambda _2\) as shown in Fig. 5. Here, we would have to choose a \(\varDelta t\) larger than 1*e*6 to see the transition.

Finally, on the right plot in Fig. 15 one can see that (50) predicts the convergence rates for the cooling of a flanged shaft to be only slightly smaller compared to the actual performance. This could be due to either the unstructured grids used or to the nonconstant temperature in the structure, which varies from room temperature to 1145 K. Again, \(\beta \) is almost constant.

## 8 Summary and conclusions

We considered the Dirichlet–Neumann iteration for thermal FSI and studied the convergence rates. To this end, we considered the coupling of two heat equations on two identical domains. We assumed structured grids on both subdomains, but allowed for high aspect ratio grids in one domain. An exact formula for the convergence rates was derived for the 1D case. Furthermore, we determined the limits of the convergence rates when approaching the continuous case either in space (\(r\lambda _1 / \lambda _2 \)) or time (0). This was confirmed by numerical results, where we also demonstrated that the 1D case gives excellent estimates for the 2D case. In addition, numerical experiments show that the linear analysis is relevant for nonlinear thermal FSI problems.

All in all, strong jumps in the coefficients of the coupled PDEs imply fast convergence. On the other hand, the coupling iteration will be slow when the material coefficients are continuous over all the subdomains, i.e, \(\lambda _1 = \lambda _2\), and therefore \(\delta _1 \sim 1\). For coupling of structures and compressible flows, the aspect ratio in the fluid has to be taken into account, since the convergence rate is proportional to it. For the nonlinear cooling problems considered here, the convergence rate was still around 0.1 for large \(\varDelta t\). When encountering divergence anyhow, this can be solved by reducing the time step. Note that in a time adaptive setting, it is standard to allow for a feedback loop between the nonlinear solver and the time stepper.

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