Annealing furnaces are used to heat steel in order to change its chemical structure. In this paper we model an electric radiant furnace. One of the major defects in steel strips processed in such furnaces is a wave-like pattern near the edges of the strip, apparently due to extra heating near the edges. The aim of the paper is to model this effect and provide a way to calculate the elevated temperatures near the edges. We analyse two processes that are suspected to contribute to uneven heating. The modelling involves an asymptotic analysis of the effect of heat flux at the edges and a detailed analysis of the integral equations associated with radiant heat transfer in the furnace.
The high temperatures within a steel annealing furnace preclude any reliable way to take measurements of the temperature; hence the need for mathematical models so that the temperature can be computed. We model an electric radiant annealing furnace with length of order 100 metres through which strips of steel sheet pass at speeds of up to 130 metres per minute in order to achieve the strip temperatures required for annealing. A schematic diagram of the furnace is shown in Fig. 4. The temperature along the furnace is controlled by varying the power supplied to the heating elements and the line speed through the furnace is reduced for strips of large thickness and width in order to achieve the required temperatures within the steel strips. At the beginning of the annealing–coating line there is an automatic welding process which welds the beginning of a new coil of steel sheet to the end of its predecessor, allowing the line to run continuously.
Occasionally the edges of the strip may take a wave-like shape after passing through the furnace and this seems to be a result of extra heating at the edges of the strip. This hypothesis is supported by a COMSOL®; model of the system [1, 2] which shows a trend in increasing steel strip temperatures closer to the edges. The goal of this paper is to gain a better understanding of the nonuniform heating of the strip across its width.
The furnace has already been modelled in a recent Mathematics-in-Industry Study Group (MISG) meeting [5]. However the model developed in that meeting was based on an assumption of uniform heating across the width of the strip and is thus unsuitable for explaining such defects. There is a very limited amount of modelling of such furnaces in the literature. Apart from the papers already cited, perhaps the closest work is [10] which also takes into account the radiative heat transfer within a mullti-zone annealing furnace. However, although the model in [10] is more detailed than that given in [5], it also makes the approximation that the strip temperature does not vary across its width. Other related models concern an electric furnace model for crystal formation in the papers by Pérez-Grande et al. [7], Sauermann et al. [8], Teodorczyk and Januszkiewicz [9].
Because of the high temperatures within the furnace, radiant heat transfer is the primary mode of heat transfer. This is discussed briefly in the MISG paper [5], but for a complete discussion we cite some standard texts by Incropera and DeWitt [4], Modest [6], Siegel and Howell [3].
As a starting point to our modelling, we briefly summarise what was done in [5]. The temperature u of the steel strip is assumed to satisfy the heat equation
x measures distance from the point of entry of the strip into the furnace, z is a distance coordinate in the vertical direction and y is a distance coordinate across the strip;
v is the velocity of the strip through the furnace;
w and h are respectively the width and thickness of the strip.
ρS, CS and kS are the strip’s density, specific heat capacity and heat conductivity respectively.
The functions w and h are typically piecewise constant functions of x and t and v can vary with time, but in this paper we limit our analysis to the desirable steady state operation of the furnace for which these variables are constant.
Equation 1 is supplemented by an initial condition
and boundary conditions. It is assumed that the steel strip enters the furnace at x=0 at constant temperature T0, giving the Dirichlet boundary condition,
$$u(0,y,z,t)=T_{0}. $$
Mathematically, it is also appropriate to specify a boundary condition where the strip exits the furnace at x=L. One could propose a model leading to an appropriate boundary condition there. However we will see soon that heat conduction in the steel strip in the direction of the x-axis is very small, which means that the term involving \(\frac {\partial ^{2} u}{\partial x^{2}}\) can be neglected everywhere except in a small boundary layer near x=L. Physically, heat is not conducted quickly enough for the temperature of the part of the strip that has already left the furnace to affect the temperature within the furnace. Thus, any boundary effect at x=L is not expected to be significant and thus we do not attempt to model it.
Boundary conditions on the remaining parts of the boundary of \(\mathcal {S}\) arise from conservation of energy, which requires that we equate the normal component of the heat flux −kS∇u to the flux of radiant energy leaving the surface. Thus we write
for (x,z)∈(0,L)×(0,h). The incoming surface heat fluxes ϕa, ϕb, ϕc and ϕd are determined by considering an energy balance of the radiation within the furnace.
We can determine the relative importance of the different terms in Eq. (1) by using dimensionless coordinates \(\tilde {x}=x/L\), \(\tilde {y}=y/w\), \(\tilde {z}=x/h\), \(\tilde {t}=tv/L\), where h and w are typical values of the thickness and width of the strip. In terms of the dimensionless variables, the equation takes the form
Taking the typical values L=150 m, v=2 m s −1, w=0.5 m, h=0.5 mm, kS=50 W m −1 K −1, CS=500 J Kg −1 K −1 and ρS=7854 Kg m −3 gives δ=3.8×10−3 and the equation
which was the justification in [5] for neglecting the heat conduction terms for the x and y directions in (1). Note however that boundary conditions must be satisfied, so one expects boundary layers near y=±w/2 where the boundary conditions are satisfied. We wish to investigate these particular boundary layers to see how much they contribute to edge heating. Thus we depart from the analysis in [5] by retaining the terms involving \(\frac {\partial ^{2}u}{\partial y^{2}}\). However, as in [5], we neglect the term involving \(\frac {\partial ^{2}u}{\partial x^{2}}\) and any associated boundary layer for reasons discussed earlier.
ΦS is calculated by considering the energy balance of the radiation within the furnace.
The relatively large coefficient of \(\frac {\partial ^{2} u}{\partial \tilde {z}^{2}}\) in (6) indicates that we can use the approximation u(x,y,z,t)≈T(x,y,t) in our calculations. Thus we consider a model consisting of Eq. (8) with an initial condition
The physical problem has reflectional symmetry through the x-z plane, so we assume that \(\Phi _{E}^{+}=\Phi _{E}^{-}=\Phi _{E}.\)
We wish to investigate two effects that could lead to edge heating of the strip. The first is the creation of a boundary layer near the edges y=±w/2 due to the boundary condition (11) there. We do this in Section 2. The second effect is a variation of ΦS in the direction of the y-axis that might explain extra heating near the edges. This requires a detailed analysis of the radiation heat transfer problem to calculate ΦS. We do this in Section 3. For the boundary layer analysis of Section 2 we use a simple approximation for ΦS that is independent of y.
Analytical treatment of edge heating
The following approximate expression for ΦS, the heat flux entering the upper and lower surfaces of the strip, was derived in [5].
where εS≈0.2 and εW≈0.9 are the emissivities of the strip and furnace materials respectively, σ=5.670×10−8Wm−2K−4 is the Stefan–Boltzmann constant and p is the sum of height and width of a cross-section of the space inside the furnace. The temperature of the furnace walls and heating elements is assumed to be the same and is given by TW. We note that this flux does not vary across the width of the strip. Smaller emissivities are associated with more reflective surfaces, which lead to a greater amount of reflection of radiant heat energy arriving at a surface.
ΦE, the heat flux absorbed at the edges, is expected to be greater than ΦS because the steel strips are formed by cold rolling of steel which results in a rougher, less reflective surface at the edges.
We limit our analysis to the steady state operation of the furnace. This simplifies the analysis because it allows us to approximate the heat flux ΦS using the power supplied to the heating elements. For the non-steady state operation, one needs to take into account the heat dynamics that occur near the inner surface of the furnace walls, which are coupled to the dynamics of radiant heat transfer and heat transfer within the steel strip. For steady state operation, one can simply use the fact that the furnace walls are very good insulators and neglect the heat lost through them.
We thus seek steady state solutions of Eqs. (8), (10) and (11). In order to get a closed-form expression for the solution, we assume in Section 2.1 that ρS, CS, k, ΦS and ΦE are all constant. We analyse the more general case for which these quantities are not constant in Section 2.2.
2.1 The case of constant ρSCS, k, ΦS and ΦE
In terms of the dimensionless variables \(\tilde {x}=x/L\), \(\tilde {y}=y/w\), \(\tilde {T}=T \frac {hv \rho _{S} C_{S}}{\Phi _{S} L}\), Eqs. (8), (10) and (11) become
Here, \(\tilde {T}_{0}=T_{0} \frac {hv \rho _{S} C_{S}}{\Phi _{S} L}\) and δ is given by (5). In these equations, \(0<\tilde {x}<1\) and \(-1/2<\tilde {y}<1/2\).
We note that h/w and δ happen to be of the same order of magnitude for this industrial application, so the non-dimensional flux term in (15) is of order 1. This indicates that boundary edge heating is significant. However, δ is small, so we expect that the temperature of parts of the strip not close to the edges satisfies
We seek the steady state solution of the whole system (13)–(15), so we set \(\tilde {T}=\tilde {T}_{0}+2\tilde {x}+\tilde {T}_{2}\) and see that \(\tilde {T}_{2}\) must satisfy
We expect \(\tilde {T}_{2}\) to remain close to zero, except in boundary layers near \(\tilde {y}=\pm 1/2\), so we write \(\tilde {y}=\delta ^{1/2}\zeta -1/2\). The scale factor δ1/2 for this inner variableζ is chosen so that heating near the edge \(\tilde {y}=-1/2\) is given by the equations
Outside this boundary layer, the solution must match the outer solution and for this we use the simple matching condition \(\tilde {T}_{2}\to 0\) as ζ→∞. The solution is easily obtained by taking the Laplace Transform with respect to the \(\tilde {x}\) variable,
A similar expression approximates the boundary layer near \(\tilde {y}=1/2\). One can combine the inner and outer solutions to obtain a composite approximation for the steady state solution of (13)–(15), valid for −1/2≤y≤1/2:
In terms of the original variables, one finds that the boundary layer penetrates to a distance
$$2\sqrt{\frac{k_{S} x}{v \rho_{S} C_{S}}} $$
and the increased temperature at the edge is
$$\Phi_{E}\sqrt{\frac{x}{\pi k_{S} v \rho_{S} C_{S}}}. $$
We use these equations to plot an example of increased strip temperature near an edge in Fig. 1. The calculations for the figure use ΦE=ΦS but in fact we expect ΦE>ΦS because the upper and lower surfaces are very smooth and are thus expected to have a lower emissivity than the edge surfaces. Thus we expect the edge temperatures to be greater than those shown in the graphs. Also used in the calculations are the values kS=50 Wm −1K−1, CS=500 JK −1Kg−1, T0=573 K, ρS=7854 Kgm −3, h=0.5 mm, w=0.5 m, v=2 ms −1, L=100 m, ΦE=ΦS=1500 Wm −2.
Fig. 1
The effect of radiation arriving at an edge. The actual effect is expected to be greater than this because of the higher emissivity of the edges
2.2 The case of variable ρS, CS, k, ΦS and ΦE
In this section, we wish to follow the analysis of Section 2.1, but now in the more realistic setting of variable ρS, CS, k, ΦS and ΦE. In practice, the large temperature variation within annealing furnaces requires that we take into account the temperature variation, especially of CS and kS, and to a lesser extent, ρS. The variation of CS and kS with temperature, shown in Figs. 2 and 3, is taken from data in [4]. Figure 3 shows that heat conductivity is approximated well using linear regression:
$$ k_{S}=73.9823-0.0437 T, $$
(26)
Fig. 2
Variation of Cp (J/Kg.K) for steel with absolute temperature T in Kelvin
Fig. 3
Variation of the heat conductivity k (W/m.K) for steel with absolute temperature T in Kelvin
and Fig. 2 shows the Cp data approximated by an interpolating quartic:
To allow for such variations, we assume that ρS, CS and kS are known functions of the strip’s temperature. Further, because our system is at equilibrium, ΦS and ΦE are assumed to be known functions of x which can be calculated by measuring the power supplied to the heating elements in the vicinity of a distance x along the furnace.
The form of Eq. (1) is only valid for constant diffusivity kS. With variable kS, we must instead write
As before, it is useful to consider a new dimensionless variable \(\tilde {x}\), this time chosen to make the coefficients of Eq. (32) more similar to those of the constant coefficient case. We do this by choosing \(\tilde {x}\) to be the solution to
The dimensionless solution of Eq. (35) corresponding to the solution T1 of Eq. (33) is given by
$$\tilde{T}_{1}(\tilde{x})=\frac{T_{1}(x)}{\overline{T}}, \quad \text{where} \quad \overline{T}=\frac{\overline{\Phi}_{S} L}{h v \rho_{S}(T_{0})C_{S}(T_{0})}, $$
and this corresponds to a solution outside boundary layers.
As in Section 2.1, we set \(\tilde {y}=\delta ^{1/2}\zeta -1/2\); ζ is our boundary layer variable near the edge \(\tilde {y}=-1/2\). We also write \(\tilde {T}=\tilde {T}_{1}(\tilde {x})+\tilde {T}_{2}(\tilde {x},\zeta)\). Rewriting the boundary condition (32) at this edge in terms of the new variables gives
It is very desirable for the industrial application that edge heating is very small. This is consistent with our observation that the physical parameters happen to be such that h/w=O(δ), and thus the right-hand-side of (36) is O(δ1/2). In any case, we assume that
$$\frac{h}{w}\delta^{-1/2}=\epsilon $$
is small and we write \(\tilde {T}_{2}(\tilde {x},\zeta)=\epsilon \theta (\tilde {x},\zeta)+O(\epsilon ^{2})\). This allows us to use a first order Taylor approximation to ρS(T), expanded about the point T=T1,
where \(g(\zeta,\tilde {x})=\frac {\partial \psi }{\partial \tilde {x}}=e^{-\zeta ^{2}/4\tilde {x}}/\sqrt {\pi \tilde {x}}\) and ψ is given by Eq. (25).
In summary, we have found that there is a boundary layer near the edges of the strip. Outside the boundary layer, the temperature T1 of the strip, at a distance x along the furnace, may be found by solving the ordinary differential Eq. (33). With T1(x), we may then calculate \(f(\tilde {x})\) from (40) and then χ from (41). This gives us θ from (38). The actual perturbation to the temperature near the edge y=−w/2 is given by
The radiative heat exchange between the furnace inner surface and the strip is considered in this section. The schematic geometry of the problem is presented in Fig. 4 which shows the cross section and the side view of the furnace and the strip. The furnace is modelled as a hollow rectangular box with length much larger than the dimensions of the cross section. The heating elements are assembled on the top and bottom inner surfaces of the furnace. We make the following assumptions about the radiative heat transfer within the furnace.
Fig. 4
Sketch of the furnace; a cross-section, b side view
1.
The heating elements are distributed uniformly over the top and bottom inner surfaces and the the density of the input electric power is specified as a constant.
2.
All surfaces are considered opaque gray. All surfaces emit and reflect radiation diffusely; the typical emissivity of the furnace wall surface and the heating element is εW=εE=0.9 and of the strip is εS=0.2. For an opaque gray surface, the reflectivity ρ and emissivity ε are related by ρ=1−ε.
3.
Temperature changes within the furnace are gradual and radiative and thus convective heat transfer along the length of the furnace can be ignored. The strip temperature at the entry of the furnace is at room temperature and it can reach up to 700 °C at the last heating stage, which is still significantly lower than the temperature of wall surface and the heating elements. Considering that the radiative power is proportional to the fourth power of the temperature, the dominant radiation is from the wall surfaces and the heating elements.
These assumptions simplify the analysis and are reasonable for a furnace with brick covered wall and a steel strip with rough surface finishing. For a steel strip with smooth surface finishing, a partly specular reflection model shall be considered.
We use these assumptions to develop a two dimensional model of the temperature distribution within the furnace. The model is two dimensional only in the sense that it relies on the approximation that there is only a gradual variation of temperature in the direction of the moving strip.
We are interested in temperature variations across the strip and for this we must solve a system of integral equations for the radiative and reflective heat exchange between surfaces within the furnace.
3.2 Mathematical model
For a diffuse surface, it is well known that the net radiation method can be used to analyse the heat transfer. This method is discussed in many texts on thermal radiation such as the works of Modest [6] and of Siegel and Howell [3]. The method, which involves an energy conservation argument for the absorption, emission and reflection of radiation inside an enclosure, results in an integral equation.
Let q(x) be the outgoing heat flux at the location x, which counts both radiant and reflected heat fluxes. The governing integral equation in terms of q(x) takes the form
for surfaces where the temperature T(x) is given, or
$$\begin{array}{@{}rcl@{}} q(\mathbf{x})=p(\mathbf{x})+ \int_{A} q(\mathbf{x'})dF_{d \mathbf{x} - d \mathbf{x'}}, \end{array} $$
(43)
for the surfaces where the input power flux p(x) is specified. In the integral equation ρ(x) is the reflectance of the surface at x and \(\phantom {\dot {i}\!}dF_{d \mathbf {x} - d \mathbf {x}^{\prime } }\) is the exchange view factor between two surface elements dx and dx′, which is defined as,
$$ {\begin{aligned} {\kern-16.5pt}{dF}_{d\mathbf{x}-d\mathbf{x}^{\prime}} \!\equiv\! \frac{\text{diffuse energy leaving} d \text{x directly toward and intercepted by d}~\mathbf{x}^{\prime}} {\text{total diffuse energy leaving d}~\mathbf{x}}\!. \end{aligned}} $$
(44)
Note that dx denotes the differential strip element which, due to the longitudinal symmetry, is infinite in the x3 direction.
The diffuse view factor between two infinitesimal strip elements dx, dx′ located at x and x′ respectively, as shown in Fig. 5, is given by
$$ \begin{aligned} {d \mathbf{x} - d \mathbf{x'} }\,=\, \frac{\cos \beta \sin \beta d \mathbf{x'} }{2r}\,=\,\frac{|(x_{1} -x_{1}')(x_{2} -x_{2}') | d \mathbf{x'} }{2 \left((x_{1} -x_{1}')^{2} + (x_{2} -x_{2}')^{2}\right)^{3/2} } \end{aligned} $$
(45)
Fig. 5
Diagram for calculation of view factors
for perpendicular elements and
$$ \begin{aligned} dF_{d \mathbf{x} - d \mathbf{x'} }= \frac{\sin^{2} \beta d \mathbf{x'} }{2r} = \frac{d^{2} d \mathbf{x'} }{2((x_{1} -x_{1}')^{2} + (x_{2} -x_{2}')^{2})^{3/2} } \end{aligned} $$
(46)
for parallel elements, where β are the angles shown in Fig. 5, d is the perpendicular distance between the two parallel elements, see [3].
We define the kernel k(x,x′) to be zero if the points x and x′ are shielded from each other by another surface, otherwise it is given by
$$ \begin{aligned} k(\mathbf{x},\mathbf{\!x'})\,=\,\!\left\{\!\!\! \begin{array}{ll} \frac{|(x_{1} \,-\,x_{1}')(x_{2} \,-\,x_{2}') | }{2((x_{1} \,-\,x_{1}')^{2} + (x_{2} -x_{2}')^{2})^{3/2} }, & \text{\!\!if x and x' are on perpendicular elements,} \\ \frac{d^{2}}{2((x_{1} -x_{1}')^{2} + (x_{2} -x_{2}')^{2})^{3/2} }, & \text{\!\!if x and x' are on parallel elements.} \end{array} \right. \end{aligned} $$
(47)
The integral equation can be written via kernel k(x,x′)
for a surface where the input power flux is given. The integral equation uniquely determines the outgoing heat flux q(x).
3.3 Numerical procedure
In general such integral equations do not have a closed form solution so a numerical method is needed to find an approximate solution. The integral equation is linear and the discretised equation is a linear system and can be solved by a standard LU decomposition. To numerically solve (48) and (49), all of the surfaces, which because of the assumption of longitudinal symmetry of the problem, are one dimensional domains, are divided into sufficiently small intervals of equal length and the q(x) is assigned on the nodes q(xi). A standard trapezoid method is applied to integrate (48) and (49) numerically, resulting in a linear system with q(xi) as unknowns.
In the actual numerical procedure, however, care must be taken in the treatment of discontinuities and singularities arising from the singularity of the kernel k(x,x′). Let us consider why these arise.
1.
The k(x,x′) function has a discontinuity at the corner points of the wall arising from the two different formulas for the parallel and perpendicular elements. Thus, the numerical integration is performed on the individual planar surfaces. This gives a total of six planar surfaces including four wall surfaces and two strip surfaces.
2.
For a node x located on a furnace wall, the kernel k(x,x′) is only a piecewise smooth function of x′ due to the presence of the steel strip and its shadow effect.
This can be observed from Fig. 6, showing a node x exposed only to partial heat flux emitted from another wall surface. The kernel k(x,x′) has jumps at x1′ and x2′, each of which lies between two neighboring nodes. The exact positions of x1′ and x2′ can be found from the geometric relation. The numerical integration is performed only on the viewable portion of the relevant subintervals bounded by x1′ (or x2′) and one of the two neighboring nodes.
3.
Due to the singularity of the kernel k(x,x′), when two nodes on the neighboring wall are sufficiently close, the variation of k(x,x′) on a single element is significant for whatever small step size has been chosen. To overcome this singularity, the following approximation is applied to these nodes.
Fig. 6
Shadow effect of the strip
Assuming a linear distribution of the q(x) on the element (xi′,xi+1′), we may estimate the integral in (48) and (49) as
l will be chosen to cover all elements affected by the kernel singularity.
4.
There are two nodes belonging to two neighbouring walls intersecting at a corner point denoted by \( \mathbf {x_{S_{1}}} \) and \(\mathbf {x_{S_{2}}}\) where S1 and S2 indicate the surfaces the nodes belong to. The integration with respect to x′ over the surface S2 for \( \mathbf {x} = \mathbf {x_{S_{1}}} \) should be estimated by calculating its value at a nearby point xε∈S1, \(\mathbf {x}_{\epsilon } \sim \mathbf {x_{S_{1}}}\phantom {\dot {i}\!}\), and then passing to the limit as \(\mathbf {x}_{\epsilon } \rightarrow \mathbf {x_{S_{1}}} \). It can be shown that
Remark: Equation (54) has a clear physical meaning: A differential element at node \(\mathbf {x_{S_{1}}}\) on surface S1 receives half of the total heat flux which is emitted from a neighborhood of \(\mathbf {x_{S_{2}}}\) on surface S2.
3.4 The isothermal surface case
The numerical model we have developed is used to reexamine the isothermal surface case for which the wall temperature TW=900°C and the strip temperature TS=500°C. The heat power absorbed per meter length of strip can be found from the incident heat flux Φs as Q=2wΦs. From (12), one finds
One notices that the above formula is derived under the assumption that the temperature and the outgoing heat flux q(x) are constant on each surface. This can be observed from the integral equations (48) and (49). When q(x) is constant, one may move the term q(x′) out of the integral and leave only the geometric term in the integrand
$$\int_{A} q(\mathbf{x'})dF_{d \mathbf{x} - d \mathbf{x'} }=q(\mathbf{x'})\int_{A} dF_{d \mathbf{x}} - d \mathbf{x'}. $$
Thus, the heat transfers between the surfaces can be calculated by using the view factor. By solving this problem with the numerical method developed in this article, we found that q(x) is actually always varying with the location. However, the variations of q(x) across the wall or strip are not significant. This is particularly true for small εS, as in such cases, the strip reflectance ρS≈1 and the radiated energy from the wall is well reflected by the strip, and thus q(x) becomes less dependent on the location.
Figure 7 shows the comparison of the numerical results and formula (55).
Fig. 7
The strip’s total heat influx calculated by the numerical method and formula (55)
It was found that in the case with wall emissivity εW=0.5, the difference between the numerical result and (55) is more significant than the case with εW=0.9. This indicates that the non uniformity of q(x) in the case εW=0.5 is larger than εW=0.9. This is confirmed by Fig. 8, which shows the distribution of q(x) on the top (or bottom) wall. In the limit case εW=1, formula (55) becomes exact, simply because the reflectance of the wall vanishes and the integral equation is reduced to algebraic equations from which (55) is derived.
Fig. 8
Distributions of q(x) on the top (or bottom) wall. The top plot: εW=0.9; The bottom plot: εW=0.5
It was also found that for the case εW=0.9 and εS=0.2, which is typical in this application, formula (55) is fairly accurate. The total outgoing heat flux q(x) is close to the uniform distribution on each surface. However, one notices that in contrast to the outgoing heat flux, which is dominated by the heat radiation generated by the uniform wall temperature, the net heat flux varies significantly across the wall surface. Figure 9 shows the numerical result for the case εS=0.2 and εW=εE=0.9.
Fig. 9
Net heat influx on the strip and the wall surfaces
This is not a surprising result because the view factors of the strip to various wall locations are very different and the portion of the heat energy emitted from the wall which is eventually absorbed by the strip is largely determined by the relative geometric position, or in other words, by the view factor.
Through these comparisons, we found that the numerical results correctly reflected the geometrical effects due to the view factor and matched very well with formula (55) at the limit case εS≈0 as expected. This validates the numerical method.
3.5 The strip temperature distribution
We now consider the problem of the temperature distribution of the strip under conditions close to those of the real furnace. The isothermal model considered in the previous section shows that the net emitted heat from the wall varies significantly across the wall surface. In the actual furnace, the electric heating elements, which are assembled at the top and bottom wall, are usually equally powered. Consequently, the temperature distribution of the heating elements must be varying. Thus, we consider the modelling problem stated as follows:
1.
The power input density of the top and bottom heating elements is specified as a constant p=1.294×104Wm−2, which is typical in this applications.
2.
The side wall surface is considered as a perfect thermal insulated surface.
3.
εW=εE=0.9 and εS=0.2, where εE denotes the emissivity of the heating elements.
4.
Find the strip surface temperature distribution.
It will be shown that the temperature variation along the width of the strip is small, less than two percent. Together with the fact found in [5] that the coefficient of the y diffusive term was very small, we may assume that the strip temperature rise is proportional to the net heat influx. One also notices that the strip temperature TS is significantly below the wall temperature and has only a very minor influence on the internal heat transfer. Thus the variations of the strip heat influx along the width at different longitudinal locations are expected to be similar. To confirm this, we examine two locations where the strip temperatures are very different, namely, TS=500°C and TS=20°C.
1.
The strip temperature 500°C.
The numerical results are shown in Fig. 10. It was found that
2.
The temperature of the electric power element varies from 949°C to 983°C. The temperature variation is about 3%.
3.
The temperature of the side wall varies from 949°C to 956°C. The temperature variation is about 0.7%.
4.
The strip net power influx varies from 2.186×104Wm−2 to 2.216×104Wm−2. The net influx variation is about 1.3%.
5.
TemperatureTS=20°C.
The numerical results are shown in Fig. 11. It was found that
6.
The temperature distributions of the heating element and side wall are similar to the case TS=500 with a slightly lower temperature range.
7.
The net heat influx of the strip is indeed very similar to the case TS=500. Figure 12 shows the comparison of the two results.
Fig. 10
Case 1: TS=500°C
Fig. 11
Case 2: TS=20°C
Fig. 12
The comparison of the net heat influx of the strip for TS=500°C and TS=20°C
Based on these results, we may calculate the strip temperature along the width by using the strip heat influx at TS=500°C. The result is shown in Fig. 13. The temperature of the strip is seen to be varying smoothly with about 7°C in magnitude. The temperature variation would be about 1.2°C if the calculation was based on the isotherm model discussed in Section 3.3.
Fig. 13
The predicted temperature variation TS across the strip width
Concluding remarks
We have analysed in detail two effects that contribute to extra heating of the steel strip at its edges.
The numerical results of Section 3 indicate that the geometrical effect due to view factors would account for an elevated temperature at the edges of about 7°C.
The analysis of Section 2 took into account the fact that the edges of the strip are really surfaces themselves. Although these surfaces are small, they contribute significantly to temperature increases at the edges because the rate of heat conduction away from the edges is slow. If one assumes that the edges are smooth and have an emissivity of about 0.2, the same as the larger surfaces of the steel, then this effect would result in temperature elevations of about 9°C at the edges. In reality the edges are much more rough than the rest of the strip’s surface. The actual temperature elevation is proportional to the emissivity, so an emissivity of 0.5, for example, would contribute to a temperature elevation of about 22°C near the edges. Moreover these elevated temperatures occur within about 1 cm of the edge of the strip, resulting in potentially damaging high temperature gradients.
Declarations
Authors’ contributions
SWT was responsible for Section 2, SW was responsible for Section 3. Both authors read and approved the final manuscript.
Competing interests
The authors declare that they have no competing interests.
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Authors’ Affiliations
(1)
Mathematics Department, University of Auckland
References
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