Boundary Layers

J. Gordon Leishman

doi:https://doi.org/10.15394/eaglepub.2022.1066.n22

25 Boundary Layers

Introduction

In most flows over surfaces, including those internal and external to the surfaces, viscosity effects are confined to a thin flow region known as the boundary layer. Viscous effects will always be significant when fluids flow across surfaces. The boundary layer is a fundamental concept in aerodynamics and fluid dynamics, in general, because it substantially influences a body’s overall aerodynamic characteristics, including its lift and drag. For example, the concept of the boundary layer, as it develops over the surfaces of an airfoil, is illustrated in the figure below. In this boundary layer region, viscosity effects are significant, and what goes on here is critically important as it affects the aerodynamic characteristics of the airfoil section, or any other body for that matter. However, it should be noted that boundary layers are much thinner in reality than the relative dimensions of the zones shown in this figure.

Concept of a boundary layer as it develops over an airfoil. For clarity, the boundary layer thickness is exaggerated.

One effect produced by the boundary layer development over a body is to create shear stresses on its surface, the cumulative manifestation of shear being skin friction drag. Skin friction is a significant source of overall drag on an aircraft, particularly in high-speed flight, where it can account for about half of the total drag. Another effect is that boundary layers can thicken and detach or separate from surfaces under certain conditions, a phenomenon called flow separation. The onset of boundary layer flow separation from a surface generally has a deleterious effect on its aerodynamics, with a loss of lift and the creation of drag. In many cases, the aerodynamic characteristics of lifting surfaces and other bodies can only be explained with a knowledge of the underlying boundary layer behavior.

Learning Objectives

Understand the basic concept of a boundary layer and appreciate its physical significance as it can affect aerodynamic flows over airfoils, wings, and other body shapes.
Distinguish between the primary characteristics of laminar and turbulent boundary layers.
Know how to calculate the shear stress on a surface under the influence of a boundary layer for particular types of velocity profiles and be able to estimate skin friction drag.
Understand why and under what conditions boundary layers may detach or separate from surfaces and what subsequent effects may be produced.
Know some essential characteristics of thermal boundary layers.

History

Historically, Ludwig Prandtl introduced the concept of the boundary layer. His work on the subject originated from experiments made with his students in Germany at the beginning of the 20th century. Prandtl showed that for fluids with relatively small viscosity that flow over surfaces or bodies, the effects of the internal stresses in the fluid are appreciable only in a region near the fluid boundaries, which he called a boundary layer. Understanding boundary layers and their effects on flow developments was a quantum step forward in growing knowledge of fluid dynamics. Before this, in the 17th century, Isaac Newton discovered that fluids could be deformed. Because of the relative motion between their layers, shear stresses are created in the fluid, resulting in what is now known as Newton’s law of viscosity. Newton also noted no relative motion between the fluid and a solid surface (the “wall”), called the no-slip condition.

As shown in the figure below, the flow velocity in a boundary layer rises quickly from zero at the surface (no-slip condition) and then smoothly and asymptotically approaches the external flow velocity, $V_e$ , as the distance increases from the surface. However, it should be appreciated that a boundary layer is very thin; the vertical extent or thickness of the boundary layer is given the symbol $\delta$ . The boundary layer is said to have a shape or profile, i.e., the velocity in the boundary layer parallel to the surface, $u$ , varies as a function of the distance from the surface $y$ , i.e., in functional form, then $u = u(y)$ . The form of the boundary layer profile depends on many factors, including the nature of the surface and the effects produced by the external flow, e.g., the pressure gradients.

The concept of a boundary layer as it forms adjacent to a solid surface or “wall,” where the flow velocity increases smoothly and asymptotically with distance away from the wall.

Different types of boundary layers will have different velocity profiles, but, as will be discussed, they are usually characterized into either laminar or turbulent boundary layer profiles, each having similar but also different flow characteristics. In general, what goes on inside the boundary layer is very important in aerodynamics and fluid dynamics. One is that it affects the shear produced on a body’s surface over which the boundary layer develops and, therefore, the magnitude of the net skin friction drag created on the body. The properties of the boundary layer also affect whether the flow stays attached to the body’s surface or may separate from the surface.

Laminar & Turbulent Boundary Layers

As detailed in the figure below, in a laminar boundary layer, the fluid flows orderly, with smooth layers free of any mixing between successive layers; such layers are called laminae, from which the “laminar” name is derived. The fluid layers in a turbulent boundary layer become mixed, so the flow velocities away from the immediate region at the wall tend to be more uniform. Because of the rotational motion of the fluid and the shear stresses that result from that, vortical eddies and turbulence are also formed, creating significant mixing in the flow. Turbulent boundary layers are inevitably thicker than laminar boundary layers because the effects of flow mixing extend further away from the wall.

Fundamental differences in the characteristics between a laminar boundary layer and a turbulent boundary layer.

Another useful quantitative comparison of the profile shapes of a typical laminar and turbulent boundary layer is shown in the following figure. This presentation is obtained by normalizing the velocity profile by the boundary layer thickness $\delta$ and the outer or edge velocity of the external flow, $V_e$ , i.e., by plotting $u/V_e$ as a function of $y/\delta$ . Note that in the case of a turbulent boundary layer, $u$ would represent the mean or time-averaged flow velocity, not the instantaneous velocity.

Representative non-dimensional velocity profiles for laminar and turbulent boundary layers.

Boundary layer profiles are nearly always plotted in this non-dimensional form because it then allows for ready comparison of their velocity profiles for given values of $V_e$ and $\delta$ , i.e., they are in the general functional form

(1) $\begin{equation*} \left( \frac{u}{V_e} \right) = f \left( \frac{y}{\delta} \right) \end{equation*}$

where $f$ is the form of the velocity profile, so $u/V_e \rightarrow 1$ at the edge of the boundary layer when $y/\delta \rightarrow 1$ . Notice that the velocity gradients, i.e., $d u / d y$ , in a laminar boundary layer are relatively shallow throughout compared to a turbulent boundary layer.

Because the velocity in the boundary layer smoothly and asymptotically approaches the external flow velocity, the value of $\delta$ must be defined rather carefully to avoid ambiguity. By convention, $\delta$ is defined as the value of $y$ for which 99% of the external flow velocity is recovered, i.e., when $u = 0.99 V_e$ .

Shear Stresses & Skin Friction

It has already been discussed that viscous stresses in fluids are produced whenever there is relative motion between adjacent fluid elements, and these stresses produce a resistance that tends to retard the motion of the fluid. The viscous shear stress, $\tau$ , is related to the absolute viscosity, $\mu$ , by using Newton’s law of viscosity formula, i.e.,

(2) $\begin{equation*} \tau = \mu \left( \frac{du}{dy} \right) \end{equation*}$

where $du / dy$ is the rate at which the flow velocity increases (in the $y$ direction) and is equivalent to a strain rate, as explained in the figure below. A characteristic of fluids is that they must be continuously deformed (strained) to produce shear, unlike solid materials, where an applied strain always maintains a residual stress. Therefore, a fluid must be continuously deformed to create stresses; when the strain rate is removed, the fluid will relax to an unstrained state. The strain rate is $d u / d y$ , so the shallower the value of this gradient, the lower the shear stresses.

The shear stress is proportional to the velocity gradient created by a strain rate in the fluid.

Because of the mixing in a turbulent boundary layer, its velocity profile is more uniform away from the wall. However, this case has steeper velocity gradients as the wall is approached. Because of the flow mixing in a turbulent boundary layer, it develops a greater thickness, $\delta$ , than a laminar boundary layer that forms under the same flow conditions. Equation 2 is a general expression that applies to any point in the flow. However, it is restricted to fluids that behave such that they follow a linear stress/strain relationship, i.e., a so-called Newtonian fluid where the slope of the stress/strain-rate relationship is linear, and so the value of $\mu$ is constant.

Aerospace engineers are particularly interested in the shear stress produced on the surface or “wall” over which the boundary layer flows, i.e., what happens as $y \rightarrow 0$ , because this value determines the skin friction drag produced by the boundary layer on the surface. The stress in the fluid at the wall, which is in the upstream direction, has a reaction shear on the wall in the downstream direction. At the wall, the shear stress is

(3) $\begin{equation*} \tau = \tau_w = \mu \left(\frac{d u}{d y}\right)~\mbox{ as $y \rightarrow 0$} \end{equation*}$

or more usually just as

(4) $\begin{equation*} \tau_w = \mu \left( \frac{d u}{d y} \right)_{y \rightarrow 0} \end{equation*}$

As implied by the shape of the boundary layer velocity profiles, as shown in the figure below, the magnitude of the wall shear stress, $\tau_w$ , produced in the boundary layer (and hence on the wall) will be greater if a turbulent boundary layer flows over it compared with a laminar one.

The shear stress on a surface produced by a flowing laminar boundary layer is much lower than that produced by a turbulent boundary layer.

This latter result is significant because the development of the boundary layer is the source of the shear stress drag or skin friction drag on a flight vehicle. Therefore, it would be desirable to generate low drag by having a laminar boundary layer over as much of the vehicle as possible. However, in reality, it is found that laminar boundary layers do not exist for very long in terms of the downstream distance over which they develop, and so they become turbulent.

Nevertheless, calculating the shear stress caused by the boundary layer is a prerequisite to calculating the drag on any body shape exposed to a flow. As might be expected, drag prediction is difficult for an entire aircraft or other flight vehicles because it has many complex shapes and three-dimensional flows. The boundary layers also take on more complicated three-dimensional forms in this case.

Development of a Boundary Layer

It should be appreciated that a boundary layer is not a static phenomenon, and it is said to “grow'” as it develops with downstream distance over a surface, i.e., the thickness and other properties of a boundary layer will change continuously as it develops downstream over any given surface. Furthermore, the development of a boundary layer may also be affected by other things, such as pressure gradients and surface roughness.

A classic example studied by all engineering students is a boundary layer that develops on the top surface of a smooth flat plate set at zero angle of attack to the oncoming flow, i.e., a uniform velocity flow. Because the surface is flat without curvature, no pressure gradients will be produced over the surface. As shown in the figure below, the thickness of the boundary layer is zero at the plate’s leading edge. Its thickness grows progressively and asymptotically, meaning that its growth rate is initially significant, and then the growth rate slows down as the boundary layer develops further downstream. Notice that the vertical scale used in this figure has been exaggerated for clarity, and boundary layers are physically very thin. As previously mentioned, the thickness of the boundary layer, $\delta$ , can be defined at the height above the surface where the flow velocity on the boundary layer approaches the external or edge flow velocity, $V_e$ .

The development of a boundary layer over a flat plate. The flow initially develops as a laminar boundary layer but soon transitions to a turbulent boundary layer.

The boundary layer begins in laminar form, at least over smooth surfaces, in which the fluid moves in smooth layers or laminae. As the laminar boundary layer increases in thickness and develops downstream, the fluid layers naturally tend to mix. The location of transition, which happens over a finite distance, depends primarily on the Reynolds number. Finally, the boundary layer transforms itself into a well-mixed turbulent boundary layer. Even when the boundary layer becomes turbulent, there is still a thin layer next to the wall with laminar flow, called the laminar sublayer.

Notice that while turbulent boundary layers have a greater thickness than laminar boundary layers, it should be remembered that the velocity profiles of laminar and turbulent boundary layers are also different. While boundary layers are of two primary types, laminar and turbulent, the third type can be considered transitional. A transitional boundary layer is not fully developed because it is neither laminar nor turbulent. However, it usually exists in this form only for a relatively short zone or downstream distance.

Worked Example #1 – Find the shear stress in a boundary layer

The velocity profiles in a laminar boundary layer have been determined to take on one of the three following characteristic non-dimensional forms, which are plotted in the figure below:

$\mbox{\small Profile A:} \quad \frac{u}{V_e} = \frac{y}{\delta}$

$\mbox{\small Profile B:} \quad \frac{u}{V_e} = \sin \left( \frac{\pi}{2} \frac{y}{\delta} \right)$

$\mbox{\small Profile C:} \quad \frac{u}{V_e} = 2 \left( \frac{y}{\delta}\right) - \left(\frac{y}{\delta} \right)^2$

where $V_e$ is the flow velocity at the edge of the boundary layer, $y$ is the distance from the surface, and $\delta$ is the boundary layer thickness. Find the relative shear stress on the wall is to be determined for given values of $\delta$ and $V_e$ .

Notice that all three profiles are of the “laminar” type with relatively low-velocity gradients throughout. Notice that this is also a one-dimensional flow problem with velocities that only vary in the $y$ direction, so the shear stress on the wall in each case is given by evaluating

$\tau_w = \mu \left( \frac{du}{dy} \right)_{y/\delta\rightarrow 0} = \mu \left(\frac{V_e}{\delta} \right) \left( \frac{d (u/V_e)}{d (y/\delta)} \right)$

Therefore, for Profile A:

$\frac{d (u/V_e)}{d (y/\delta)} = 1$

And for Profile B:

$\frac{d (u/V_e)}{d (y/\delta)} = \frac{\pi}{2} \cos \left( \frac{\pi}{2} \frac{y}{\delta} \right) = \frac{\pi}{2}~\mbox{ as $y/\delta\rightarrow 0$}$

And finally, for Profile C:

$\frac{d (u/V_e)}{d (y/\delta)} = 2 \left(1 - (y/\delta) \right) = 2~\mbox{ as $y/\delta\rightarrow 0$}$

Based on the exact value of $\delta$ and also the same external flow velocity $V_e$ , the grouping

$\mu \left(\frac{V_e}{\delta} \right) =~\mbox{constant}$

is the same, so it becomes clear that Profile A has the lowest relative shear stress and Profile C has the highest, which is readily confirmed by reinspection of the results plotted in the figure above.

Distance-Based Reynolds Number

The developing nature of the boundary layer can be characterized in terms of a local Reynolds number, which is measured in terms of the distance $s$ from the point where the flow initially develops on the surface, i.e.,

(5) $\begin{equation*} Re_ s = \frac{\varrho_{\infty} \, V_{\infty} \, s}{\mu_{\infty} } = \frac{V_{\infty} \, s}{\nu_{\infty}} \end{equation*}$

For example, in the case of a flat plate, as previously discussed, $s = x$ and is measured from the plate’s leading edge to some downstream distance. In many cases, the boundary layer will develop downstream starting from a stagnation point on a body, as shown in the figure below. Generally, the downstream distance will be different for the upper and lower surfaces and will depend on the geometric surface shape.

The downstream distance on a body is often measured from the stagnation point and will differ depending on the surface shape.

Transition

Experiments on smooth surfaces have shown that the boundary layer generally becomes turbulent at Reynolds numbers based on $Re_s$ above about $5 \times 10^{5}$ . The reason is that natural flow disturbances develop even over perfectly smooth surfaces and cause a transition from a laminar to a turbulent boundary layer. In this case, the value of the “critical” Reynolds number for transition to be initiated is denoted by $Re_{\rm cr}$ and the corresponding value of $s$ is denoted by $s_{\rm cr}$ , i.e.,

(6) $\begin{equation*} Re_ {\rm cr} = \frac{\varrho_{\infty} \, V_{\infty} \, s_{\rm cr}}{\mu_{\infty} } \end{equation*}$

Many experiments have examined the transition process from laminar to turbulent flows. In all cases, the region of transition has been found to correlate strongly with the Reynolds number based on downstream distance. Because the turbulent mixing occurs progressively, the transition from a fully laminar boundary layer flow to a fully turbulent process occurs over some distance. Although this distance is usually relatively small, it is still finite. In some cases, the transition will occur at the point where a laminar separation bubble forms on the surface, a phenomenon discussed later in the current chapter.

Other Properties of Boundary Layers

Besides the velocity profile $u = u(y)$ or $u/V_e = f(y/\delta)$ in the boundary layer, there are three other parameters that engineers use to quantify the characteristics of boundary layers, namely: 1. The displacement thickness $\delta^*$ ; 2. The momentum thickness, $\theta$ ; 3. The shape factor, $H$ .

Displacement Thickness

The displacement thickness of a boundary layer is given the symbol $\delta^*$ and is defined by

(7) $\begin{equation*} \delta^* = \int_0^\delta \left( 1 - \frac{u}{V_e} \right) dy \end{equation*}$

the idea of which is illustrated in the figure below. Therefore, the displacement thickness of a boundary layer can be interpreted as equivalent to the height or thickness corresponding to the reduction in mass flow associated with the boundary layer profile, i.e., what is, in effect, a mass flow deficit.

The concept of displacement thickness is equivalent to a reduction in mass flow rate by the presence of the boundary layer.

Momentum Thickness

The corresponding momentum thickness of the boundary layer, which is given the symbol $\theta$ , is defined by

(8) $\begin{equation*} \theta = \int_0^\delta \frac{u}{V_e} \left( 1 - \frac{u}{V_e} \right) dy \end{equation*}$

This parameter also has physical meaning because it is a measure of the reduction in momentum in the flow from the development of the boundary layer, i.e., a quantity that measures the momentum deficit in the flow. It also provides information about the distribution of momentum within the boundary layer.

Shape Factor

Finally, the shape factor, given the symbol $H$ , is defined in terms of the displacement thickness and momentum thickness by the equation

(9) $\begin{equation*} H = \frac{\delta^*}{\theta} \end{equation*}$

The shape factor is often used as an indicator to help characterize the state of boundary layer flows and evaluate their propensity to stay attached or to separate from surfaces. Notice that because

(10) $\begin{equation*} 1 - \frac{u}{V_e} > \frac{u}{V_e} \left( 1 - \frac{u}{V_e} \right) \end{equation*}$

then the value of $H$ is always greater than unity.

It has been found from experiments that the values of $H$ take on a range of values depending on the flow state. For example, for laminar flows, $H \approx 2.5$ ; for fully turbulent flows, $H \approx 1.5$ . As a boundary layer approaches the point of separation from a surface, the values of $H$ typically increase to 4 or more. Therefore, to calculate the development of a boundary layer over a wing, as the value of $H$ increases to around 4, it would be anticipated that the boundary layer is about to separate from the surface. Therefore, the shape factor is one parameter that can be used to help design a contour of an aerodynamic surface so that the flow remains more attached than it might otherwise.

Pressure Gradients & Flow Separation

A pressure gradient in any given flow will significantly affect the development of a boundary layer. Three types of pressure gradients can develop over a surface, as illustrated in the figure below.

The concept of a pressure gradient. Both favorable and adverse pressure gradients significantly affect the development of boundary layers.

1. A pressure gradient where the pressure $p$ decreases with increasing downstream distance, say $x$ , i.e., the pressure gradient is $dp/dx < 0$ . This gradient is called a favorable pressure gradient because it has favorable effects on the boundary layer developments, i.e., it tends to encourage the downstream development of the boundary layer and prevent it from separating from the surface.

2. A neutral or “zero” pressure gradient where $dp/dx = 0$ , i.e., no pressure changes with downstream distance.

3. A pressure gradient where the pressure $p$ increases with increasing downstream distance, i.e., $dp/dx > 0$ . This gradient is called an adverse pressure gradient because it has adverse effects on the development of the boundary layer, i.e., the pressure forces act to retard the development of the boundary layer and so tend to slow it up. If the pressure gradient is sufficiently adverse, it will eventually cause the boundary layer to slow down to zero near the surface and separate away from the surface.

The figure below shows an example of a boundary layer flow development over a convex hump. The external flow velocity (in this case identified by the edge velocity $V_e$ ) increases over the front of the hump and reduces again over the back. As the flow velocity increases, its static pressure decreases (i.e., from the Bernoulli equation), and as the velocity decreases again, the pressure increases. Consequently, the corresponding pressure gradients are favorable over the front ( $dp/dx$ is negative, decreasing with distance) and adverse over the back ( $d p/d x$ is positive, increasing with distance). The favorable pressure gradient over the front half encourages the boundary layer to stay attached, but the adverse pressure gradient over the back half slows down the boundary layer flow, especially near the surface, and causes it to separate. Notice that when flow separation occurs, the flow velocity and static pressure do not immediately recover to the free-stream values.

Flow over a hump. The flow velocity increases to a maximum as it flows over the crest, with the corresponding pressure reaching a minimum.

The consequence of the preceding observations is that the flow no longer easily follows the body’s contour when the gradient $(d u/d y)_w \rightarrow 0$ , i.e., what happens when the pressure gradient is adverse and tries to slow down the flow. There comes a point where the boundary layer profile develops a point of inflection, so the corresponding shear stress becomes zero. The flow reverses, and a region of recirculating flow develops. It is said that the flow has separated, and the point where the shear stress is zero is called the flow separation point. The formal criterion for the onset of flow separation is that

(11) $\begin{equation*} \tau_w = \left(\frac{d u}{d y} \right)_{\rm wall} = 0 \end{equation*}$

This means the flow will separate from the surface when the wall shear becomes zero. While this criterion is strictly valid only for a steady flow, it represents a quantifiable condition to predict or identify the onset of flow separation in a boundary layer.

It is possible to deduce that turbulent boundary layers are generally less susceptible to flow separation than a laminar boundary layer, all external influences being equal. This outcome is because a turbulent boundary layer has a higher flow velocity near the wall than a laminar boundary layer, so it takes a longer downstream distance for the flow to approach the conditions at the wall that are likely to produce flow separation.

Summary of Boundary Layer Characteristics

The preceding observations about the boundary layer can now be summarized:

1. The flow velocity profile and other boundary layer characteristics, such as its thickness, affect the shear stresses in the fluid and the surface shear or skin friction. Hence, the boundary layer affects the drag of the surface (or body) over which it develops.

2. The boundary layer’s characteristics depend on the Reynolds number. At higher Reynolds numbers, where inertial effects in the flow are much stronger than viscous effects, boundary layers tend to be relatively thin and robust to the extent that they stay attached to surfaces for longer downstream distances. However, at lower Reynolds numbers, the boundary layers are slower and thicker and so more easily prone to separation.

3. The characteristics of the boundary layer are affected by the pressure gradients over the surface on which it develops. For example, if the surface is curved rather than flat, the flow velocities will change along the surface, and so will the static pressures. If the pressure gradient is sufficiently unfavorable or adverse, the boundary layer may detach or separate and leave the surface, a process called flow separation.

4. Most boundary layers will eventually become susceptible to separation from the surfaces over which they develop, especially after they develop over longer downstream distances. The onset of flow separation has deleterious effects on airfoil and wing aerodynamics, including a loss of lift and an increase in drag. Other effects may also be significant to the development of the boundary layer, e.g., surface roughness, flow heating, etc.

Flow Separation on an Airfoil

Boundary layer separation from a body, such as an airfoil section, can have significant consequences, including a large increase in drag and a substantial loss of lift. This outcome is because the rear part of an airfoil creates an adverse pressure gradient, as shown in the figure below, which becomes increasingly adverse with an increasing angle of attack. While pressure is a scalar quantity, in this form of presentation, the pressure is plotted as a vector in a direction perpendicular to the surface of the airfoil, with lower than ambient static pressure areas pointing outward and higher than ambient pointing inward.

Representative pressure distribution over an airfoil, showing the region of favorable and adverse pressure gradients.

Over the front part of the airfoil, there is a favorable pressure gradient, which encourages the boundary layer to develop normally in the downstream direction. Indeed, the boundary layer may remain laminar during this time, although much depends on the surface roughness. Beyond the point of minimum pressure, there is an adverse pressure gradient over the airfoil, so the boundary layer will transition to being turbulent, and then the subsequent development of the boundary layer begins to slow in the downstream direction as it develops in the adverse pressure gradient.

At low angles of attack, the boundary layer can withstand this gradient, reaching the airfoil’s trailing edge or separating just before that point, as shown in the figure below. However, as the angle of attack increases, the more severe adverse pressure gradients cause the flow to separate at a shorter downstream distance, so the separation point moves forward. Eventually, flow separation occurs near the leading edge, and under these conditions, the airfoil is said to be stalled.

Flow about an airfoil section at increasing angles of attack showing the progressive forward movement of flow separation on the upper surface and the onset of stall.

The turbulence produced in the separated flow region and wake is also a source of unsteady aerodynamic loads and buffeting on the wing. Indeed, a characteristic of stalling the wing of an aircraft during flight is the creation of unsteady aerodynamic loads and buffeting transmitted to the airframe, warning the pilot of an impending wing stall.

Boundary Layer Equations

The “boundary layer equations” are a subset of the full Navier-Stokes equations, which, in principle, are more straightforward (but not easy) to solve, partly because they are cast into a two-dimensional form using order of magnitude approximations. Such approximations require careful justification, either by comparing the resulting approximate solutions with the complete solutions (if those can be obtained) with flow measurements or sometimes with both. Experience using the boundary layer equations has shown their validity for problems bounded by the assumptions and limitations from which they were derived. For example, using the boundary layer equations to solve for the viscous flow over an airfoil at low to moderate angles of attack (below stall) has been well-proven.

Many practical problems can also be solved by using a hybrid or coupled method comprised of essentially inviscid methods (e.g., potential flow methods such as panel methods for the outer flow) combined with a boundary layer approach for the inner near-surface flow, which are sometimes called inviscid/viscous interaction methods. In this approach, the boundary layer solution is coupled to the inviscid approach through a specific type of boundary condition, usually in the form of a displacement thickness of the boundary layer, which gives a “virtual” airfoil shape over which the inviscid solution can be obtained. Such approaches can provide reasonable predictions of the resulting flow at minimal cost compared to a complete Navier-Stokes solution using computational fluid dynamics or CFD.

Momentum Equations

Different approaches can be used to obtain the boundary layer equations. The most intuitive approach is to start with the incompressible form of the momentum equations and to apply them to a problem (such as the flow over an airfoil at lower angles of attack) where the boundary layer development can be assumed to be very thin (e.g., what would be obtained with a flow at higher chord Reynolds numbers). The streamline curvature is low, i.e., the streamlines are not bent by much, so the slope of the streamlines, $dy/dx$ , remains small.

The incompressible form of the momentum (Navier-Stokes) equations can be written in a rather elegant and compact form as

(12) $\begin{equation*} \varrho \frac{D \vec{V}}{Dt} = -\nabla p + \mu \nabla^2 \,\vec{V} \end{equation*}$

where $\nabla^2$ is the vector Laplacian of the velocity field. The equations are also often written in the form

(13) $\begin{equation*} \frac{D \vec{V}}{Dt} = -\left( \frac{1}{\varrho} \right) \nabla p + \nu \nabla^2 \,\vec{V} \end{equation*}$

Expanding out the substantial derivative on the left-hand side gives

(14) $\begin{equation*} \varrho \left(\frac{\partial \vec{V}}{\partial t} + \vec{V} \bigcdot \nabla \, \vec{V}\right) = -\nabla p + \mu \nabla^2 \,\vec{V} \end{equation*}$

The meaning of the terms in these equations should be appreciated, i.e.,

(15) $\begin{equation*} \overbrace{\varrho \Big( \underbrace{ \frac{\partial \vec{V}}{\partial t}}_{ \begin{smallmatrix} \text{Local}\\ \text{(unsteady)}\\ \text{acceleration} \end{smallmatrix}} + \underbrace{\vec{V} \bigcdot \nabla \, \vec{V}}_{ \begin{smallmatrix} \text{Convective} \\ \text{acceleration} \end{smallmatrix}}\Big)}^{\text{Inertial terms}} = \overbrace{\underbrace{-\nabla p}_{ \begin{smallmatrix} \text{Pressure} \\ \text{gradients} \end{smallmatrix}} + \underbrace{\mu \nabla^2 \,\vec{V}}_{\text{Effects of viscosity}}}^{\text{Stress terms}} \end{equation*}$

the stress terms are normal compressive stresses like pressure and viscous shear. Note that the normal compressive stresses in terms of the bulk viscosity do not appear in the incompressible form of the equations.

These equations can also be expanded in terms of their scalar components, giving

(16) $\begin{eqnarray*} \mbox{$x$ component:} \quad \quad \varrho \left(\frac{\partial u}{\partial t} + u \frac{\partial u}{\partial x} + v \frac{\partial u}{\partial y} + w \frac{\partial u}{\partial z}\right) & = & -\frac{\partial p}{\partial x} + \mu \left(\frac{\partial^2 u}{\partial x^2} + \frac{\partial^2 u}{\partial y^2} + \frac{\partial^2 u}{\partial z^2}\right) \\[8pt] \mbox{$y$ component:} \quad \quad \varrho \left(\frac{\partial v}{\partial t} + u \frac{\partial v}{\partial x} + v \frac{\partial v}{\partial y}+ w \frac{\partial v}{\partial z}\right) & = & -\frac{\partial p}{\partial y} + \mu \left(\frac{\partial^2 v}{\partial x^2} + \frac{\partial^2 v}{\partial y^2} + \frac{\partial^2 v}{\partial z^2}\right) \\[8pt] \mbox{$z$ component:} \quad \quad \varrho \left(\frac{\partial w}{\partial t} + u \frac{\partial w}{\partial x} + v \frac{\partial w}{\partial y}+ w \frac{\partial w}{\partial z}\right) & = & -\frac{\partial p}{\partial z} + \mu \left(\frac{\partial^2 w}{\partial x^2} + \frac{\partial^2 w}{\partial y^2} + \frac{\partial^2 w}{\partial z^2}\right) \end{eqnarray*}$

Two-Dimensional, Steady Flow

For a two-dimensional flow (assumed in the $x$ – $y$ plane), there are just two scalar components, i.e.,

(17) $\begin{eqnarray*} \varrho \left(\frac{\partial u}{\partial t} + u \frac{\partial u}{\partial x} + v \frac{\partial u}{\partial y}\right) & = & -\frac{\partial p}{\partial x} + \mu \left(\frac{\partial^2 u}{\partial x^2} + \frac{\partial^2 u}{\partial y^2} \right) \\[8pt] \varrho \left(\frac{\partial v}{\partial t} + u \frac{\partial v}{\partial x} + v \frac{\partial v}{\partial y}\right) & = & -\frac{\partial p}{\partial y} + \mu \left(\frac{\partial^2 v}{\partial x^2} + \frac{\partial^2 v}{\partial y^2} \right) \\ \end{eqnarray*}$

Expanding out the first and last set of terms in each case gives

(18) $\begin{eqnarray*} \varrho \frac{\partial u}{\partial t} + \varrho u \frac{\partial u}{\partial x} + \varrho v \frac{\partial u}{\partial y} & = & -\frac{\partial p}{\partial x} + \mu \frac{\partial^2 u}{\partial x^2} + \mu \frac{\partial^2 u}{\partial y^2} \\[8pt] \varrho \frac{\partial v}{\partial t} + \varrho u \frac{\partial v}{\partial x} + \varrho v \frac{\partial v}{\partial y} & = & -\frac{\partial p}{\partial y} + \mu \frac{\partial^2 v}{\partial x^2} + \mu \frac{\partial^2 v}{\partial y^2} \\ \end{eqnarray*}$

and assuming steady flow, then

(19) $\begin{eqnarray*} \varrho u \frac{\partial u}{\partial x} + \varrho v \frac{\partial u}{\partial y} & = & -\frac{\partial p}{\partial x} + \mu \frac{\partial^2 u}{\partial x^2} + \mu \frac{\partial^2 u}{\partial y^2} \\[8pt] \varrho u \frac{\partial v}{\partial x} + \varrho v \frac{\partial v}{\partial y} & = & -\frac{\partial p}{\partial y} + \mu \frac{\partial^2 v}{\partial x^2} + \mu \frac{\partial^2 v}{\partial y^2} \\ \end{eqnarray*}$

Simplifications

If the boundary layer is thin compared to the dimensions of the problem (i.e., for an airfoil $\delta \ll c$ where $c$ is the chord) and also that the streamline curvature is slight (i.e., small such than $v \ll u$ ), then each of the corresponding terms in these two latter equations can be examined and perform an expected relative magnitude comparison.

For the first convective term:

(20) $\begin{equation*} \varrho u \frac{\partial u}{\partial x} > \varrho u \frac{\partial v}{\partial x} \end{equation*}$

For the second convective term:

(21) $\begin{equation*} \varrho v \frac{\partial u}{\partial y} > \varrho v \frac{\partial v}{\partial y} \end{equation*}$

For the first viscous stress term:

(22) $\begin{equation*} \mu \frac{\partial^2 u}{\partial x^2} > \mu \frac{\partial^2 v}{\partial x^2} \end{equation*}$

For the second viscous stress term:

(23) $\begin{equation*} \mu \frac{\partial^2 u}{\partial y^2} > \mu \frac{\partial^2 v}{\partial y^2} \end{equation*}$

In other words, all the terms in the $x$ component of momentum are more important than the corresponding terms in the $y$ component. It is reasonable to conclude in this case, therefore, that

(24) $\begin{equation*} \bigg| \frac{\partial p}{\partial y} \bigg| < \bigg|\frac{\partial p}{\partial x} \bigg| \end{equation*}$

i.e., the pressure gradients normal to the surface of the airfoil will be much weaker than the pressure gradients along the airfoil’s chord. Indeed, it is reasonable to conclude that for a thin boundary layer that develops over the surface of an airfoil in the boundary layer that

(25) $\begin{equation*} \frac{\partial p}{\partial y} = 0 \end{equation*}$

This outcome means that the pressure gradient (normal to the surface) within the boundary layer can be neglected, a result also verified experimentally for low-speed (subsonic) flows. This assumption, however, is not such a good one for high-speed flows where significant compressibility effects are present.

This latter result is significant because it exposes two things. First, the local static pressure in the flow will only be a function of $x$ (not $x$ and $y$ ), hence simplifying the solution. Second, the local static pressure about the body or airfoil will not depend on the boundary layer. The pressure depends on the external flow field above the boundary layer (essentially inviscid), i.e., it will only depend on the edge velocity, $V_e$ , and the corresponding pressure, $p_e$ . Finally, if the streamline curvature is low, then the viscous stresses from the $x$ gradients will also be low so that

(26) $\begin{equation*} \mu \frac{\partial^2 u}{\partial x^2} < \mu \frac{\partial^2 u}{\partial y^2} \end{equation*}$

and so these terms can also be neglected.

Thin-Layer Boundary Layer Equations

Therefore, the reduced or simplified form of the Navier-Stokes equations under these thin-layer boundary layer assumptions becomes

(27) $\begin{eqnarray*} \varrho u \frac{\partial u}{\partial x} + \varrho v \frac{\partial u}{\partial y} & = & -\frac{d p_e}{d x} + \mu \frac{\partial^2 u}{\partial y^2} \\[8pt] \frac{\partial p}{\partial y} & = & 0 \end{eqnarray*}$

where the $\partial p/\partial x$ term has been replaced by $dp_e/dx$ in that the pressure now depends only on that in the $x$ direction and the external pressure, $p_e$ , at that. The pressure is related to the flow velocity using the Bernoulli equation (actually the unintegrated form using Euler’s equation, i.e., $dp = -\varrho V dV$ ) so that

(28) $\begin{equation*} -\frac{\partial p}{\partial x} = - \frac{dp_e}{d x} = \varrho V_e \frac{d V_e}{dx} \end{equation*}$

Therefore, these latter equations are usually written in the form

(29) $\begin{eqnarray*} \varrho u \frac{\partial u}{\partial x} + \varrho v \frac{\partial u}{\partial y} & = & \varrho V_e \frac{d V_e}{d x} + \mu \frac{\partial^2 u}{\partial y^2} \\[8pt] \frac{\partial p}{\partial y} & = & 0 \end{eqnarray*}$

and with the addition of the conservation of mass (continuity) equation, i.e.,

(30) $\begin{equation*} \frac{\partial u}{\partial x} + \frac{\partial v}{\partial y} = 0 \end{equation*}$

they are collectively called the incompressible form of the boundary layer equations. If time dependence is included, then

(31) $\begin{eqnarray*} \varrho \left( \frac{\partial u}{\partial t} + u \frac{\partial u}{\partial x} + v \frac{\partial u}{\partial y} \right) & = & \varrho V_e \frac{d V_e}{d x} + \mu \frac{\partial^2 u}{\partial y^2} \\[8pt] \frac{\partial p}{\partial y} & = & 0 \\[8pt] \frac{\partial u}{\partial x} + \frac{\partial v}{\partial y} & = & 0 \end{eqnarray*}$

These latter equations will apply to all types of incompressible boundary layers that are laminar, turbulent, or even transitional. However, they will not apply to flows that are separated from the surface, such as on stalled airfoils or in the wakes behind bluff bodies such as circular cylinders.

In practice, although a significantly reduced subset of the Navier-Stokes equations, the boundary layer equations are still challenging to solve, partly because they are a set of nonlinear equations because of the convective acceleration terms. So, they are usually solved utilizing numerical methods, i.e., finite-difference approaches, but in some cases, exact solutions may be possible. In all cases, the equations must be solved by specifying initial and boundary conditions.

Laminar Boundary Layer: Blasius Solution

A classic solution in this latter category is the Blasius solution^[1] for the laminar boundary layer development over a flat plate in a zero pressure gradient, a classic exemplar in fluid dynamics and an essential check case for CFD and measurement methods.

The Blasius problem of determining the velocity profile and other characteristics of a boundary layer developing over a flat plate.

The flow away from the plate has a uniform velocity of $V_e = V_{\infty}$ . The downstream distance is measured in terms of $x$ , and the plate’s leading edge is at $x$ = 0. At the leading edge, there is a stagnation point. The boundary layer develops from zero thickness at that point and gets thicker, moving further downstream along the plate. This problem had been studied experimentally in the laboratory by the time Blasius tackled the theoretical solution, so Blasius had some additional physical insight into the problem that influenced the development of his theory.

Boundary Layer Equations in Zero Pressure Gradient

The boundary layer equations in a zero pressure gradient are

(32) $\begin{equation*} \frac{d p_e}{d x} = 0 \end{equation*}$

so these equations become

(33) $\begin{eqnarray*} u \frac{\partial u}{\partial x} + v \frac{\partial u}{\partial y} & = & \nu \frac{\partial^2 u}{\partial x^2} \\[10pt] \frac{\partial p}{\partial y} & = & 0 \label{two} \\[10pt] \frac{\partial u}{\partial x} + \frac{\partial v}{\partial y} & = & 0 \label{three} \end{eqnarray*}$

Notice that the first of the set (Eq. 33) is in terms of the kinematic viscosity $\nu$ , i.e., $\nu = \mu/\varrho$ . These latter equations are sometimes known as Prandtl’s equations because Prandtl was the first to cast the more general momentum equations into this simplified form.

Stream Function & Boundary Conditions

To solve these equations for the flow field in the boundary layer, a set of boundary conditions are needed, which, in this case, are: 1. The no-slip condition at the surface, i.e., $u = v = 0$ at $y = 0. 2$ . The conditions at infinity (a uniform flow in this case), i.e., $u = U_{\infty}$ as $y \rightarrow \infty$ . Using the stream function, $\psi$ , is a useful way of reducing the number of variables, and this was the approach used by Blasius in his analysis of the boundary layer problem. His goal was to reduce the governing partial differential equations (which, in this case, are in terms of $x$ and $y$ ) into one ordinary differential equation for a single transformed variable. Remember that in terms of the stream function, $\psi$ , the velocity components are

(34) $\begin{equation*} u = \frac{\partial \psi}{\partial y} \mbox{\quad and \quad} v = -\frac{\partial \psi}{\partial x} \end{equation*}$

Notice that the continuity equation is automatically satisfied, i.e.,

(35) $\begin{equation*} \frac{\partial u}{\partial x} + \frac{\partial v}{\partial y} = \frac{\partial}{\partial x}\left(\frac{\partial \psi}{\partial y} \right) - \frac{\partial}{\partial y} \left(\frac{\partial \psi}{\partial x}\right) = \frac{\partial^2 \psi}{\partial x \partial y} - \frac{\partial^2 \psi}{\partial x \partial y} = 0 \end{equation*}$

Equation 33 now becomes

(36) $\begin{equation*} \frac{\partial \psi}{\partial y} \left( \frac{\partial^2 \psi}{\partial x \partial y}\right) - \frac{\partial \psi}{\partial x} \left( \frac{\partial^2 \psi}{\partial y^2} \right) = \nu \frac{\partial^3 \psi}{\partial y^3} \end{equation*}$

which is now a new governing equation. It is important to note that the mathematical definitions of the physical boundary conditions will also change. 1. The no-slip boundary condition now becomes $\psi = 0$ at $y = 0$ . 2. The boundary conditions at infinity now become $\partial \psi / \partial y \rightarrow V_{\infty}$ as $y \rightarrow \infty$ .

Similarity Solution

Blasius’s next step was to express the solution for the velocity in the boundary layer as a self-similar solution, i.e., where the boundary layer profile can be consistently scaled as a function of downstream distance. Blasius examined the measurements of the boundary layer profile for different downstream distances, $x$ , when they were plotted in terms of $u/V_{\infty}$ versus $y/\delta$ , with $\delta$ being the thickness of the boundary layer. The results proved to be self-similar, which means that the velocity profile at any value of $x$ is a scaled version of the velocity profile at any other distance $x$ . When the velocity profiles were plotted as $u/V_{\infty}$ versus $y/\sqrt{x}$ then they all collapsed into a single profile, i.e., that they exhibit a self-similarity when the profile is expressed in terms of these quantities.

George Stokes had already shown that for a boundary layer, the flow velocity at a distance $y$ from the surface would depend on $V_{\infty}$ , the kinematic viscosity $\nu$ , and the distance from the leading edge of the plate $x$ , and the boundary layer thickness, $\delta$ , grew according to

(37) $\begin{equation*} \delta \, \propto \, \sqrt{ \frac{\nu x}{V_{\infty}}} \end{equation*}$

Dividing both sides by $x$ , then

(38) $\begin{equation*} \frac{\delta}{x} \, \propto \, \sqrt{ \frac{\nu}{x V_{\infty}}} \end{equation*}$

so the developing thickness of the boundary layer becomes a function of the Reynolds number based on downstream distance, i.e.,

(39) $\begin{equation*} \frac{\delta}{x} \, \propto \, \sqrt{\frac{1}{Re_{x}}} \end{equation*}$

Solution of the Velocity Profile

The primary goal remains, however, which is to determine the actual theoretical shape of the boundary layer profile that will satisfy the governing boundary layer equation to find $u$ as a function of $y$ , i.e.,

(40) $\begin{equation*} \frac{u}{V_{\infty}} = f \left( \frac{y}{\delta} \right) \end{equation*}$

where $f$ is the desired functional relationship. From this point, Blasius defined a transformed variable, $\eta$ , as

(41) $\begin{equation*} \eta = \frac{y}{\sqrt{\displaystyle{\frac{\nu \, x}{V_{\infty}}}}} = \sqrt{\frac{V_{\infty}}{\nu \, x}} y \end{equation*}$

so that now

(42) $\begin{equation*} \frac{u}{V_{\infty}} = f ( \eta ) \end{equation*}$

A stream function is then defined as

(43) $\begin{equation*} \psi = \sqrt{ \nu V_{\infty}} x \ f( \eta ) \end{equation*}$

In terms of the transformed variable, then

(44) $\begin{equation*} u = V_{\infty} \frac{df}{d\eta} = V_{\infty} f^{\prime} \end{equation*}$

and

(45) $\begin{equation*} v = \frac{1}{2} \sqrt{\frac{\nu V_{\infty}}{x}} \left( \eta \frac{df}{d\eta} - f \right) = \frac{1}{2} \sqrt{\frac{\nu \, V_{\infty}}{x}} \big( \eta f'- f \big) \end{equation*}$

The governing equation, i.e., Eq. 36, now becomes

(46) $\begin{equation*} \frac{d^3 f}{d\eta^3} + \frac{1}{2} f \bigg( \frac{d^2 f}{d\eta^2} \bigg) = 0 \quad\quad \mbox{or} \quad\quad f''' + \frac{1}{2} f \ f'' = 0 \end{equation*}$

The boundary conditions in terms of the transformed variables become $f = f'= 0$ as $\eta = 0$ , i.e., the no-slip boundary condition, and $f' \rightarrow 1$ as $\eta \rightarrow \infty$ , i.e., the conditions at infinity, as summarized in the table below.

Transformation of boundary conditions form physical to similarity coordinates.
Physical coordinate	Similarity coordinates
$u$ = 0 at $y$ = 0	$\dfrac{df}{d\eta}$ = 0 at $\eta$ = 0
$u$ = 0 at $y$ = 0	$f = 0$ at $\eta$ = 0
$\dfrac{\partial u}{\partial y}$ = 0 as $y \rightarrow \infty$	$\dfrac{df}{d\eta}$ = 1 as $\eta \rightarrow \infty$

Notice that the transformed governing equation, i.e., Eq. 46, is still a third-order nonlinear differential equation, but it is now an ordinary differential equation, which is easier to solve. Therefore, Blasius’s approach converted a system of two partial differential equations into one ordinary differential equation. However, solving Eq. 46 for the function $f$ still cannot be done in closed form and requires a numerical method, for which several approaches are possible. Blasius did this using a Taylor series expansion for which the coefficients of the series were numerically derived using recursive relationships, and much of his paper is about finding this numerical solution. However, other numerical methods can also be used to solve the equation.

The table below gives calculated numerical values of the similarity function $f$ and its derivatives along the plate carried out until $f'$ approaches 1, i.e., the edge of the boundary layer. The value of the second derivative, $f''$ , is needed to calculate skin friction.

The Blasius similarity function $f$ and its derivatives.
$\eta$	$f$	$f'$	$f''$
0.0	0.0	0.0	0.332
0.5	0.042	0.166	0.331
1.0	0.166	0.330	0.323
1.5	0.370	0.487	0.303
2.0	0.650	0.630	0.267
2.5	0.996	0.751	0.271
3.0	1.397	0.846	0.161
3.5	1.838	0.913	0.108
4.0	2.306	0.956	0.064
4.5	2.790	0.980	0.034
5.0	3.283	0.992	0.016
5.5	3.781	9,997	0.007
6.0	4.280	0.999	0.002
$\infty$	$\infty$	1.0	0.0

Finally, notice that the velocity profile of the laminar boundary layer is just

(47) $\begin{equation*} \frac{u}{V_{\infty}} = \frac{d f}{d\eta} = f' \end{equation*}$

which is the result Blasius set out to obtain in the beginning. This velocity profile is also plotted below. Measurements have shown that the Blasius solution to the velocity profile is in excellent agreement with measurements, which, in this case, were made using particle image velocimetry (PIV).

The Blasius solution compared to measurements made in a laminar flow as it develops on a flat plate.

Other Characteristics

From this result, other information about the characteristics of the boundary layer can be determined, including the boundary layer thickness and the shear stress on the wall. The boundary layer thickness, $\delta$ , is defined as the value of $y$ for which the velocity in the boundary layer approaches 99% of the free-stream value. From the Blasius solution, this condition is obtained for $\eta$ = 5 so that

(48) $\begin{equation*} \delta (x) = 5 \sqrt{ \frac{ \nu x}{V_{\infty}}} \end{equation*}$

or in terms of $Re_x$ , where $Re_{x}$ is the Reynolds number based on “ $x$ ,” which is the distance from the plate’s leading edge, then

(49) $\begin{equation*} \delta (x) = \frac{5 x}{ \sqrt{Re_x}} \end{equation*}$

The displacement thickness, $\delta^*$ , is obtained by integrating the velocity profile, i.e.,

(50) $\begin{eqnarray*} \delta^* (x) & = & \int_0^\delta \left( 1 - \frac{u}{V_{\infty}} \right) dy \\[8pt] & = & \left(\frac{\nu x}{V_e} \right)^{1/2} \int_0^{\infty} \left( 1 - f' \right) d \eta \\[8pt] & = & \left(\frac{\nu x}{V_e} \right)^{1/2} \lim_{\eta \rightarrow \infty} \left( \eta - f \right) \\[8pt] \end{eqnarray*}$

giving

(51) $\begin{equation*} \delta^* (x) = 1.721 \sqrt{ \frac{ \nu x}{V_{\infty}}} \end{equation*}$

where 1.721 is found from the numerical solution. Therefore, the quantity can be written as

(52) $\begin{equation*} \delta^*(x) = \frac{1.721 x}{ \sqrt{ Re_x}} \end{equation*}$

Also, the momentum thickness, $\theta$ , is

(53) $\begin{equation*} \theta (x) = \int_0^\delta \frac{u}{V_{\infty}} \left( 1 - \frac{u}{V_{\infty}} \right) dy = 0.664 \sqrt{ \frac{ \nu x}{V_{\infty}}} \end{equation*}$

or

(54) $\begin{equation*} \theta^*(x) = \frac{0.664 x}{ \sqrt{ Re_x}} \end{equation*}$

It will be apparent that the values of $\delta^*$ and $\theta$ can be expressed in terms of the boundary layer thickness, i.e.,

(55) $\begin{equation*} \delta^*(x) \approx 0.344 \, \delta(x) \end{equation*}$

and

(56) $\begin{equation*} \theta (x)\approx 0.128 \, \delta (x) \end{equation*}$

The shear stress on the surface (the wall stress) is

(57) $\begin{equation*} \tau_w (x) = \mu \left( \frac{\partial u}{\partial y} \right)_{y \rightarrow 0} = \mu V_{\infty} \left( \frac{V_{\infty}}{ \nu x} \right) f''(0) \end{equation*}$

and from the tabulated numerical values given previously then $f''(0)$ = 0.332. Therefore,

(58) $\begin{equation*} \tau_w (x) = 0.332 \, \mu \, V_{\infty} \left(\frac{V_{\infty}}{\nu x} \right) = 0.332 V_{\infty} \left( \frac{\varrho \mu V_{\infty}}{x} \right) = 0.332 \frac{\varrho V_{\infty}^2}{\sqrt{Re_{x}}} \end{equation*}$

As already discussed, it is often preferred to use non-dimensional forms of quantities in aerodynamics, e.g., lift coefficient, drag coefficient, and the like. When dealing with boundary layers, a local non-dimensional shear stress coefficient or skin friction coefficient $c_f$ is used, which is defined in terms of the free-stream dynamic pressure as

(59) $\begin{equation*} c_{f} (x) = \frac{\tau_w(x)}{q_{\infty}} = \frac{\tau_w}{\frac{1}{2} \varrho V_{\infty}^2} \end{equation*}$

The value of $\tau_w$ will be a local quantity because it will vary from point to point across the surface, so the value of $c_f$ will also vary.

The local skin friction coefficient is used with integration to calculate the total drag on an exposed surface from the action of the boundary layer. The drag on a plate of finite length $L$ would be given by integrating the local skin friction along the length of both sides of the plate, i.e.,

(60) $\begin{equation*} C_f = \frac{2}{L} \int_0^L c_f(x) \, dx \end{equation*}$

For an airfoil section of chord $c$ , then

(61) $\begin{equation*} C_d \equiv C_{d_{0}} = \frac{2}{c} \int_0^c c_f \, dx = 1.328 \, Re_x^{-0.5} \end{equation*}$

This latter result is often used as a benchmark in that it would represent the absolute minimum drag on a thin airfoil if the flow were to develop along its length in a fully laminar manner. Therefore, an ideal goal would be to design for laminar flow, but one that is never practically attainable because the flow will always become turbulent at any practical flight Reynolds number.

Extensions of the basic approach used by Blasius (i.e., similarity solutions) have been made by various authors, including the work of Faulkner & and Skan, who generalized the boundary layer solutions for various external velocity fields and hence allowed for the effects of pressure gradients. However, these laminar solutions tend to be more of academic interest than any actual practical use because the boundary layers on most flight vehicles are inevitably turbulent.

Turbulent Boundary Layers

The principles surrounding the development of a turbulent boundary layer, which is distinctive because this type of flow has more mixing between the fluid layers and a more uniform velocity profile, have already been discussed and shown in the figure below. Recall also that a turbulent boundary layer will be thicker than a laminar one, a point previously made, because of the larger extent of mixing in the flow. However, expressing the structure of a turbulent boundary layer is much more complicated mathematically, and there are no theoretical results like the Blasius solution.

A turbulent boundary layer has been well-studied experimentally, but developing a generalized, functional relationship for the velocity profile remains challenging. However, various approximations for the turbulent boundary layer profile can be used. Among the simplest and the best-known approximations is the power-law profile, which is expressed as
(62) $\begin{equation*} \frac{u}{V_{\infty}} = \left(\frac{y}{\delta}\right)^{1/n} \end{equation*}$
where the value of $n$ is a constant that depends on the Reynolds number. It is found that the value of $n$ tends to increase with increasing Reynolds number to give agreement with measured profiles of turbulent boundary layers. However, using $n = 7$ for many flows is sufficient to represent a turbulent boundary layer profile called the “one-seventh power law,” as shown in the figure below.

The velocity profile of a turbulent boundary layer is much more uniform compared to a laminar boundary layer, except near the wall where there is a laminar sublayer of smooth flow.

However, a disadvantage of the power-law profile is that it cannot be used to calculate the shear stress exactly at the wall (i.e., at $y = 0$ ) in the laminar sublayer because it gives an infinite velocity gradient there. Notice that the laminar sublayer is a thin layer at the wall where the flow is predominantly smooth and may be regarded as a region where $u$ varies linearly with $y$ , i.e.,

(63) $\begin{equation*} \frac{d u}{dy} \approx \frac{V_{\infty}}{\delta_L} \end{equation*}$

where $\delta_L$ is the thickness of the laminar sublayer. Understanding the laminar sublayer is essential in the analysis of turbulent boundary layer flows and must be considered when studying heat transfer and drag forces.

For a turbulent boundary layer development along a flat plate, the boundary layer thickness can be approximated by

(64) $\begin{equation*} \delta (x) \approx \frac{0.37 \, x}{Re_x^{1/5}} \end{equation*}$

This preceding relationship assumes that the flow is turbulent right from the start of its development and that the velocity profiles are self-similar along with the flow in the x-direction. Neither of these assumptions is true for the general turbulent boundary layer case, so care must be exercised when applying this formula to any problems.

Example #2 – Skin Friction from laminar & turbulent boundary layers

Consider two boundary layer profiles at a wall, one laminar and one turbulent. The laminar profile is given by $u/V_e = 2(y/\delta)-(y/\delta)^2$ and the turbulent profile by $u/V_e = (y/\delta)^{1/7}$ where $V_e$ is the edge velocity (external velocity) and $\delta$ is the boundary layer thickness. Calculate the shear stress on the wall in each case where $\delta$ for the turbulent boundary layer is twice that of the laminar boundary layer and explain why they differ.

The shear stress, $\tau_w$ , on the wall in each case is given by

$\tau_w = \mu \left( \frac{du}{dy} \right) = \mu \left(\frac{V_e}{\delta} \right) \left( \frac{d (u/V_e)}{d (y/\delta)} \right)~\mbox{ as $(y/\delta)\rightarrow 0$}$

So, for the laminar boundary layer.

$\frac{d (u/V_e)}{d (y/\delta)} = 2 \left(1 - (y/\delta) \right) = 2~\mbox{ as $(y/\delta)\rightarrow 0$}$

and for the turbulent boundary layer

$\frac{d (u/V_e)}{d (y/\delta)} = (1/7) (y/\delta)^{-6/7} = 53.25~\mbox{ as $(y/\delta)\rightarrow 0.001$}$

In the latter case, the gradient has been evaluated at a short distance from the wall because the gradient would otherwise become infinite as $(y/\delta)\rightarrow$ 0. If $\delta$ for the turbulent boundary layer is twice that of the laminar boundary layer, the latter value will be reduced by about 1.81 to 29.39.

It is clear then that the turbulent boundary layer produces a much higher skin friction coefficient on the wall for given values of $V_e$ and $\mu$ . Hence, it will also have a much higher drag on a body over which such a boundary layer may exist.

Visualizing the Boundary Layer

Boundary layers are typically very thin regions next to a surface, so they are challenging to visualize using measurement techniques. Nevertheless, standard flow visualization methods used in the wind tunnel environment can reveal the signature and perhaps specific boundary layer properties. Flow visualization may be divided into surface flow visualization and off-the-surface visualization. Such methods include, but are not limited to, smoke or other tracer particles, tufts, surface oil flows, liquid crystals, sublimating chemicals, pressure-sensitive paints, shadowgraph, schlieren, etc.

An example illustrating the effects of the two boundary layer states on an airfoil at a low angle of attack and relatively low Reynolds number is shown in the figure below. In this case, the flow was visualized in a wind tunnel using a surface oil flow technique in which light mineral oil is mixed with a white paint powder, and the mixture is applied to the surface with a brush. The shear stress on the oil mixture from the boundary layer creates a pattern, with regions of lower skin friction leaving behind more significant oil accumulations.

Surface flow visualization on an airfoil at a low angle of attack shows the transition from a laminar to a turbulent boundary layer. Eppler 387 airfoil.

For these conditions, the forward 60% of the airfoil can be interpreted to have a laminar boundary layer; the low surface shear stress here allows the oil to accumulate, especially near the mid-chord where the boundary layer approaches the transition point. Downstream of the transition, the boundary layer state is fully turbulent, with higher shear stresses causing more of the oil on the surface to be removed. Notice that the transition region is short where the flow is separated, indicative of a laminar separation bubble. However, it must be remembered that what is observed on the surface does not always indicate what is happening in the external flow.

Fun experiment – listening to a boundary layer!

How can you listen to a boundary layer? Well, it turns out that is easier than you think! It is necessary to have some pressure taps in the surface connected to a piece of rubber tubing. In the wind tunnel, a special type of tubing called Tygon is used. You can plug it into your ear on the other end of the tube, much like a physician uses a stethoscope. You will soon be able to hear the differences!

You will hear little for a smooth laminar flow over the surface, except for a light swishing noise. For a fully turbulent flow, you will hear much more of a rumbling noise because of the unsteady pressure disturbances caused by turbulence. Finally, you will hear bursts of swishing and rumbling for a transitional flow. Fascinating!

Skin Friction Drag on an Airfoil

Estimating the skin friction drag on bodies with a turbulent boundary layer is an essential problem in aerospace engineering. While the situation is generally complex for a complete airplane or other flight vehicles because of the complex surfaces and the highly three-dimensional boundary layers that subsequently develop, the process can be illustrated for a two-dimensional airfoil. An airfoil is reasonably thin and flat, so at least at low angles of attack, a flat plate can be used to approximate the shape and drag on an airfoil.

The net shear stress drag on the plate with the laminar flow can be found by integrating along the plate’s length or the chord $c$ . For the Blasius result, then the sectional drag coefficient is

(65) $\begin{equation*} C_d = \frac{2}{c} \int_0^c c_f \, dx = 1.328 \, Re_x^{-0.5} \end{equation*}$

where the factor “2” is needed because the plate has upper and lower surfaces; this latter result is plotted for reference in the figure below.

Viscous boundary layer shear stress drag (skin friction drag) of a flat plate compared to the minimum drag coefficients of several airfoils over a range of Reynolds numbers.

For the fully turbulent boundary layer development on a flat plate, the skin friction coefficient $c_{f}$ on one side of the plate is found to conform to an empirical relationship given by

(66) $\begin{equation*} c_{f} = 0.0583 \, Re_{x}^{-0.2} \end{equation*}$

This latter result is obtained by assuming the velocity profile corresponds to a 1/7th power law profile, as given previously. If the plate was to have a fully turbulent boundary layer over its upper and lower surfaces, then by integration (as for the laminar case), it is found that

(67) $\begin{equation*} C_d = 0.1166 \, Re_c^{-0.2} \end{equation*}$

where $Re_c$ is the chord-based Reynolds number. The validity of the latter expression is generally limited to a $Re_c$ range between $10^{5}$ and $10^{9}$ . Below $Re_c = 5 \times 10^{5}$ , the boundary layer can generally be assumed to be laminar, that is, unless the pressure gradients are particularly adverse, which will slow the flow near the wall and cause the boundary layer to separate, perhaps forming a laminar separation bubble.

The results shown in the graph above suggest that the turbulent flat-plate solution is a good approximation to the viscous (shear) drag on many airfoils over a fairly wide range of practical Reynolds numbers found during flight on aircraft, i.e., for $Re_c$ above $10^6$ . In this case, it will be sufficient to assume that

(68) $\begin{equation*} C_d = C_{d_{\rm ref}} \left( \frac{Re_c}{Re_{\rm ref}} \right)^{-0.2} \end{equation*}$

where $Re_{\rm ref}$ is the reference chord Reynolds number for which a reference value of drag $C_{d_{\rm ref}}$ is known for a given airfoil section; not all airfoils will have known (measured) drag coefficients at all Reynolds numbers, but this approach allows the drag coefficient for other Reynolds numbers to be estimated with good confidence.

The empirical drag equation, which McCroskey has suggested for practical use, is

(69) $\begin{equation*} C_d = 0.0044 + 0.018 \, Re_c^{-0.15} \end{equation*}$

offers an improved correlation at the higher chord Reynolds numbers, which will be typical of those found on larger aircraft and at higher flight speeds. The laminar boundary layer separates more readily at very low Reynolds numbers, below $10^5$ . The drag coefficients of typical airfoils are larger than either laminar or turbulent boundary layer theory would suggest.

Airfoil behavior in this Reynolds number regime is essential for many classes of small-scale air vehicles, i.e., UAVs. In this case, it can be seen in the above figure relating drag coefficient to Reynolds number that changing the scaling coefficient from 0.2 to 0.4 in Eq. 68 gives a good approximation (line fit) based on the results shown over a lower range of $Re_c$ . However, the drag of airfoils in this regime tends to be less predictable, especially at other than shallow angles of attack, because the boundary layers are thicker, often with laminar separation bubbles, and the onset of flow separation occurs more readily.

Laminar Separation Bubbles

The name “laminar separation bubble” has been mentioned previously, but what is it? A laminar separation bubble, or LSB, is often found on airfoil sections and at many chord Reynolds numbers. However, they are usually longer and more pronounced on airfoil sections operating at lower Reynolds numbers below 10 $5$ .

The figure below shows a schematic of an LSB. Laminar separation bubbles occur as the initial boundary layer approaches the point of laminar separation, which is at or immediately downstream of the leading edge pressure (suction) peak on an airfoil. After laminar separation occurs, the flow will temporarily leave the airfoil surface but undergo a transition process and immediately reattach as a turbulent boundary layer. It does this because a turbulent boundary layer can more easily withstand a given adverse pressure gradient than a laminar boundary layer. The result is a region (usually relatively small at higher chord Reynolds numbers) of recirculating separated flow of content pressure. At lower Reynolds numbers, a long LSB may be formed. LSBs can also be observed by a slight constant pressure region when the chordwise pressure distribution is measured near the airfoil’s leading edge. With surface oil flow visualization, as previously discussed, the LSB is evidenced by an accumulation of oil.

Laminar separation bubbles are one mechanism of transition from a laminar to a turbulent boundary layer and are common on airfoil sections.

Effects of Surface Roughness

The development of a boundary layer is profoundly affected by pressure gradients and surface roughness. For example, the transition from a laminar to a turbulent boundary layer flow is often caused prematurely by the effects of surface roughness, as shown in the figure below, which acts to enhance the mixing of the flow in the lower layers of the boundary layer and so to produce turbulence more quickly. However, it should be appreciated that a laminar boundary layer is so thin that it takes only a tiny amount of roughness to initiate the transition process. Leading edge roughness on an airfoil will inevitably eliminate any laminar separation bubbles.

Surface roughness will cause mixing in the lower layers of the boundary layer and cause a laminar boundary layer to become turbulent prematurely.

As this turbulence develops near the surface, it mixes up through the higher layers in the boundary layer. As a result, it quickly progresses through the entire boundary layer from top to bottom, except immediately near the wall. Surface roughness can be present on a surface for various reasons, including just the “in-service” use of an aircraft, such as average abrasion at the leading edge of a wing, which will increase the drag of that wing. However, in some cases, such as with golf balls, surface roughness can have beneficial effects; the transition to a turbulent boundary layer delays flow separation and reduces the pressure drag on the ball.

Boundary Layer Flow Control

Much ongoing research is into “laminar” flow wings and active flow control technology to improve aerodynamic efficiency. Control over the natural turbulent boundary layer that forms on an aircraft by keeping it laminar could reduce skin friction drag. Such an approach could minimize aircraft drag by up to an order of magnitude and significantly reduce fuel consumption, especially for high-speed aircraft.

NASA has tested a modified F-16 with a porous glove over the wing, as shown in the photograph below. The glove is the black region on the left wing. The glove contained over 10 million tiny holes drilled by lasers and connected to a suction system. This approach removed a portion of the slower part of the boundary layer close to the surface, extending the laminar flow region across the wing. However, there are many challenges in developing practical boundary layer control systems for aircraft, including weight, reliability, maintainability, and costs.

The Supersonic Laminar Flow Control (SLFC) experiment on a modified F-16 aimed to reduce drag using boundary layer suction control.

Thermal Boundary Layers

A thermal boundary layer is a concept used in fluid dynamics and heat transfer to describe the region near a surface where the temperature of the fluid changes rapidly from the temperature at the surface (the wall) to the temperature of the external bulk fluid flow. Heat is transferred when a fluid flows over a wall with a temperature different from that of the fluid. This heat transfer process creates a region adjacent to the wall, known as the thermal boundary layer , where the temperature gradient is significant.

Heat Transfer

Assume that a flow with free-stream temperature $T_e$ starts to flow over a wall with a higher temperature $T_s$ , i.e., $T_s > T_e$ . At the hotter wall, the flow velocity is low and approaches the no-slip condition at the surface, as shown in the figure below. Because there is a temperature difference between the wall and the flow, heat is first transferred across the wall/fluid interface and into the fluid by thermal conduction. Heat is then progressively transferred away from the wall by thermal convection into successive layers of fluid, until at some distance away from the wall the temperature approaches the temperature of the bulk flow. The distance at which $T = 0.99 T_e$ is called the thermal thickness, $\delta_T$ . In general, the rate at which the thermal boundary layer grows is different to the viscous or velocity boundary layer.

A thermal boundary layer is a thin region where the temperature of the fluid changes rapidly from the surface temperature to the temperature of the external bulk flow

The rate of heat conductive transfer from the wall per unit area, also known as heat flux (which has units of energy per unit time per unit area) depends on the temperature gradient at the wall, often called Fourier’s law. In its one-dimensional form, it is expressed as

(70) $\begin{equation*} \overbigdot{q}_w = - k \left( \dfrac{dT}{dy}\right)_{y~\rightarrow~0} \end{equation*}$

where $k$ is known as the thermal conductivity of the fluid (which has units of energy per unit time per length per unit temperature). The minus sign indicates that heat flows in the opposite direction of the temperature gradient from higher to lower, i.e., in accordance with the second law of thermodynamics. The value of the thermal conductivity, $k$ , depends on the type of fluid and its temperature, and is a measured quantity derived from heat transfer experiments.

Nusselt Number

The heat transfer per unit area of the wall can also be expressed in terms of Newton’s law of cooling, i.e.,

(71) $\begin{equation*} \overbigdot{q}_w = h \, \Delta T = h \left( T_s - T_e \right) \end{equation*}$

where in this case $h$ is the convective heat transfer coefficient (expressed on units of energy per unit time per unit area per unit temperature), a value that can also be found from experiments. Because the conductive heat transfer is transferred as convection into the thermal boundary layer, equating Eqs. 70 and 71 gives

(72) $\begin{equation*} \left( \dfrac{dT}{dy}\right)_{y~\rightarrow~0} = h \left( T_s - T_e \right) \end{equation*}$

This latter relationship in Eq. 72 can be non-dimensionalized by using

(73) $\begin{equation*} T^* = \dfrac{T - T_s}{T_e - T_s} \end{equation*}$

and

(74) $\begin{equation*} y^* = \dfrac{y}{L} \end{equation*}$

where $L$ is some characteristic length. Therefore, after some additional steps, then it can be shown that

(75) $\begin{equation*} \left( \dfrac{d T^*}{dy^*}\right)_{y^*\rightarrow~0} = \dfrac{h \, L}{k} \end{equation*}$

which is a dimensionless temperature gradient, the dimensionless grouping $h \, L / k$ being known as the Nusselt number, i.e,

(76) $\begin{equation*} Nu \equiv \dfrac{\mbox{\small Convective heat transfer}}{\mbox{\small Conductive heat transfer}} = \dfrac{h \, L}{k} \end{equation*}$

Recall that $k$ is the conductive thermal transfer of the fluid and $h$ is the convective transfer, so the physical interpretation of the Nusselt number now becomes apparent. In the case of a thermal boundary layer, the reference length for the Nusselt number can be taken as the thermal thickness, $\delta_T$ .

Prandtl Number

In the study of thermal boundary layers, the Prandtl number, $Pr$ , is often used, which is a dimensionless similarity parameter defined as the ratio of viscous or “momentum” diffusivity to thermal diffusivity, i.e.

(77) $\begin{equation*} Pr \equiv \dfrac{ \mbox{\small Rate of viscous diffusion} }{ \mbox{\small Rate of thermal diffusion} } = \dfrac{\nu}{\alpha} = \dfrac{\left( \dfrac{\mu}{\varrho}\right)}{ \left(\dfrac{k}{\varrho \, C_p}\right)} = \dfrac{\mu \, C_p}{k} \end{equation*}$

where $\alpha$ is the thermal diffusivity, which is the heat transfer rate from one point to another, and $C_p$ is the specific heat at a constant pressure. The product $\varrho \, C_p$ is called the volumetric heat capacity, i.e., the ability of the fluid to absorb and store thermal energy. The momentum diffusivity, normally called kinematic viscosity, is a measure of the fluid’s resistance to shear relative to its density.

Therefore, it will be apparent that the physical significance of the Prandtl number is a relative measure of convective heat transfer relative to conductive heat transfer. For $Pr < 1$ , thermal diffusivity is more important, and for $Pr > 1$ , momentum diffusivity is more important. Notice that the Prandtl number has no length scale, and its value depends solely on the temperature-driven values of the fluid parameters. Its value is usually listed along with other properties such as density, viscosity, and thermal conductivity.

For gases then $Pr < 1$ , e.g., for the laminar flow of air then, $Pr = 0.71$ , which means that thermal diffusivity is more important than viscous diffusion, so $\delta_T > \delta$ . Values of the Prandtl number depend on the fluid but also whether it is laminar or turbulent. In the case of a turbulent flow, it is often assumed that $Pr \approx 0.9$ for air, but this value will depend on the turbulence levels in the flow. For liquids $Pr > 1$ , e.g., for water at ambient temperature conditions then $Pr = 7$ , and for more viscous fluids such as oils, then $Pr > 200$ .

The thickness of the thermal boundary layer, $\delta_T$ , depends on factors such as the flow velocity, specific fluid properties, and the surface temperature. Generally, a thicker thermal boundary layer will have slower heat transfer rates, while a thinner boundary layer allows for quicker heat transfer between the wall and the fluid. Turbulence enhances heat transfer by mixing the fluid near the surface more effectively, bringing more lower-temperature fluid into contact with the hot surface, thereby increasing the thermal gradient and the overall heat transfer rate. Therefore, it will also be apparent that the Prandtl number is related the velocity boundary layer and thermal boundary layer by

(78) $\begin{equation*} Pr \, \propto \, \dfrac{\delta}{\delta_t} \end{equation*}$

Importance of Thermal Boundary Layers

Understanding thermal boundary layers is critical for high-speed flight vehicles to manage aerodynamic heating, select structural materials, and ensure structural integrity. Supersonic and hypersonic flight generates intense aerodynamic heating from compressibility and wall shear. Thermal boundary layers form around the aircraft’s surfaces from this heating, affecting the distribution of temperatures and the thermal stresses experienced by the aircraft structure. For example, the leading edges of Concorde reached temperatures over 130^oC, which is enough to begin to change the material properties of conventional aluminum; to this end, special high temperature “Hiduminium” alloy had to be used. Metals are also very good at conducting heat, so the entire airframe reached relatively high temperatures, which caused it to thermally expand, which was as much as 0.5 ft (0.15 m) from nose to tail. To this end, many parts of the internal structure used pin-jointed and/or sliding elements to alleviate the stresses.

Diagram of the temperature contours on a Concorde supersonic flight vehicle. — Temperature contours over Concorde’s airframe at Mach 2.1

During re-entry into Earth’s atmosphere or when entering the atmospheres of other planets, spacecraft encounter intense heat generation from friction with the atmosphere. Understanding thermal boundary layers is crucial for designing effective heat shields to efficiently dissipate heat and prevent the spacecraft from burning up during re-entry. Heat shields are usually made of an ablative material that breaks down, and pieces are shed off into the flow in layers, enhancing heat transfer. Spacecraft may utilize other thermal protection systems consisting of materials such as silica tiles, ceramics, and other coatings that can withstand high temperatures. These systems often rely on the principles of thermal boundary layers to dissipate heat efficiently and protect the spacecraft’s structure and components.

Summary & Closure

Understanding the characteristics of boundary layers as they develop over solid surfaces is essential for understanding the aerodynamic characteristics of all types of bodies, both lifting and non-lifting. Besides the effects of skin friction, a significant drag source on most flight vehicles, boundary layers can separate from surfaces and cause harmful effects on the resulting aerodynamics. While laminar boundary layers are easier to understand, the reality of most flows about flight vehicles is that their boundary layers are fully turbulent. While studying turbulent boundary layers is a technical field within itself, the essential characteristics of turbulent boundary layers and how they behave are, for example, critical to understanding the aerodynamic characteristics of airfoils, wings, and other shapes.

5-Question Self-Assessment Quickquiz

For Further Thought or Discussion

Consider two fully developed turbulent boundary layers that are otherwise identical, but one has twice the thickness of the other. What will be the relationship between the wall stresses in each case?
Think about quantitatively measuring the wall stress exerted by a boundary layer on a surface, such as on a body tested in a wind tunnel.
How might surface roughness affect the development of a turbulent boundary layer?
Explain why laminar boundary layers are more likely to separate than turbulent boundary layers when experiencing the same adverse pressure gradient.
Write a MATLAB program to calculate the solution to the Blasius profile and plot the thickness, displacement thickness, and momentum thickness for $Re_x$ = 1,000.

Other Useful Online Resources

To learn more about boundary layers, check out some of these additional resources:

Some good information on boundary layers is from Wikipedia.
This a great introductory video on the concept of a boundary layer.
What is a boundary layer? Laminar and Turbulent boundary layers explained.
Fluid Mechanics, The Boundary Layer; SAFL Film No. 56
NASA’s technical information page on boundary layers.
Introductory fluid dynamics video lecture on boundary layers from YouTube.
An excellent old film on boundary layers sponsored by NSF.
YouTube video: Turbulent flow is MORE awesome than laminar flow!
The insane engineering of re-entry – clear and comprehensive video.

Paul Richard Heinrich Blasius, "Grenzschichten in Flgkeiten mit kleiner Reibung,'"which is usually cited in the form of the NACA translation "The Boundary Layers in Fluids With Little Friction," NACA TM-1256. ↵

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Introduction to Aerospace Flight Vehicles Copyright © 2022, 2023, 2024 by J. Gordon Leishman is licensed under a Creative Commons Attribution-NonCommercial-NoDerivatives 4.0 International License, except where otherwise noted.

Digital Object Identifier (DOI)

https://doi.org/https://doi.org/10.15394/eaglepub.2022.1066.n22