2.1. Proposed Concept
As stated before, the heat generation of PEMFCs is unavoidable since the conversion process from chemical power to electrical power results in a significant amount of heat. This is depicted in
Figure 1, where the occurring process heat can be identified and split into two different shares. The proportion that is not removed by the cooling system, i.e., losses in the form of radiation and convection of the FC, is mainly in the form of heat expelled via the exhaust system. The second share must be removed via a cooling system for i.e., a liquid cooling circuit that absorbs the FC heat and transports it to an HX. The exFan project intends to utilize this share of heat absorbed by the cooling system to achieve additional thrust. This is indicated as the purple line in the Sankey diagram of
Figure 1.
The concepts found in the literature, which focus on reducing flow velocity, are extended in this work by adding a fan upstream of the HX as shown in
Figure 2. The reason for this is the increase in pressure ratio achieved by the fan, which goes beyond the ramjet effect. This increase in the pressure ratio should result in an increase in process efficiency, as the pressure ratio has a direct effect on the thermal efficiency of such a process.
Figure 2 illustrates the whole design of a ducted propulsor equipped with an HX positioned downstream of the fan stage, which for this paper is called the exFan. The configuration shown is divided into segments, beginning with an inlet (Segments 1–2) designed to diffuse the incoming airflow, thus reducing the internal flow velocity while increasing the static pressure of the working fluid.
Following the inlet, the fan stage (Segments 2–3) further increases the total pressure of the working fluid. In the transition duct (Segments 3–4), the flow velocity is further decreased with a slight increase in static pressure. Segments 4–5 locate the HX, which raises the working fluid temperature, thereby increasing its enthalpy. Between Segments 5 and 7, space is reserved for potential future advancements in the project. Finally, in the nozzle (Segments 7–8), static pressure is converted into dynamic pressure to generate thrust.
A well-known application in aviation, utilizing solely the forward motion for compression by using a diffuser followed by a combustor for heat addition, is the ramjet [
15]. An idealized representation of the ramjet process is shown as a dashed line in the enthalpy–entropy (h-s) diagram in
Figure 3. The exFan concept differs from this approach by incorporating an additional fan stage (Segments 2–3) to increase the pressure ratio of the system. This is shown in
Figure 3 as a solid line. This enhancement elevates the static pressure beyond what can be achieved relying only on dynamic pressure as in the conventional ramjet principle.
Differently from the ramjet process, where a combustion process is used to increase the working fluid temperature, exFan uses the rejected heat of an FC to increase the enthalpy of the working fluid. The different heat addition via an HX compared to a combustion process has one major drawback, which is the often greater pressure loss in the working fluid due to the HX. If the pressure losses exceed the benefit of the process, drag is created instead of additional thrust. In
Figure 3, this would result in
becoming smaller than
.
With increasing flight velocity, the available dynamic pressure to be converted into static pressure rises, resulting in higher compression ratios. Since the exFan concept is intended for flight velocities below Mach 0.8, this effect is limited. The incorporated fan stage allows to further increase this compression ratio, resulting in higher thermal efficiencies [
16].
Figure 4 shows the thermal efficiency according to Equation (
1) plotted versus the
with the flight Mach number
as a parameter. The parameter
represents the ram effect, while the
stands for the compression by the fan stage. To evaluate the upper limit of the thermal cycle efficiency, the dynamic pressure is fully recovered to a static pressure rise. As shown in
Figure 4, there is a benefit to the higher dynamic pressure, represented by higher flight speeds and an increase in
. For an intended flight speed close to Mach 0.8, the cycle efficiency is approximately 0.12 and can be further enhanced with an increase in
.
With an increase in
, the specific work supplied to the working fluid rises. As illustrated in
Figure 3, the fan compression raises the enthalpy level, which requires work from the fan by converting mechanical power. The fan is driven by electric motors connected through a transmission gearbox, with the motor drawing its power from the FC. The result is a direct relation between fan compression and the heat from the FC to be dissipated via the HX since the working fluid is not solely used to provide thrust but also to serve as a heat absorbent in the HX.
Figure 5 shows the energy flow path to transfer electric power from the FC via the power converter to the electric motor, where the electric power is converted to mechanical power. This mechanical power can be transmitted to the fan, which converts it and adds energy to the working fluid.
Figure 5 illustrates that the components in reality experience losses. While these losses could be incorporated into the model, they are intentionally excluded, as they fall outside the scope of this paper. Consequently,
,
and
are set to zero, treating the components as ideal (loss-free) for the purposes of this analysis. Therefore,
is set equal to
. This assumption enables a direct relation of the specific fan work and the associated specific FC power output. It allows to calculate the heat generated in the FC per kilogram of working fluid compressed by the fan, under different operating conditions (temperature, pressure) and set parameters (flight speed,
). The approach enables the estimation of the share of heat generated by the FC based on its efficiency
. The specific amount of heat converted by the FC is marked as
in
Figure 5 and indicates that the heat is transferred from the FC to the HX.
The parameter
shown in Equation (
2) defines the total pressure ratio of the fan. Equation (
2) combined with Equation (
3) results in Equation (
4), which enables to calculate the total temperature after the fan if the total temperature before is known. These values can be used in Equation (
5) to calculate the specific isentropic fan work
needed for certain
s in an idealized fan stage:
The unit of the specific amount of FC heat can be expressed as , referring to the compressed working fluid that is used as the heat absorbent. When the power needed for compression increases due to higher values, an increased specific amount of heat is available in the HX for a given overall efficiency value of the FC.
For a simplified and idealized representation, a constant fuel cell efficiency of 50% following [
4,
14] is assumed. As Sazali et al. outline in [
14], around 80% of the heat must be removed by the cooling system. For simplicity, this work assumes that in the FC, hydrogen is either converted into electricity or heat, which is dissipated via the HX. This assumption is reflected by Equation (
6):
In
Figure 6, the assumption stated in Equation (
6) is depicted, and the relation of the fan work and the associated specific amount of heat to be dissipated in the HX is shown.
describes the pressure recovery in the inlet (Segments 1–2), resulting in an increase in static pressure for an isentropic intake diffuser. Three variants of
, namely
for low
compression,
for medium
compression, and
for high
compression, are marked in
Figure 6 for the fan stage. The process is depicted for the three
cases, and it is observed that an increase in
results in a theoretically more efficient and more effective Brayton cycle. The reason for this lies in the higher compression that results in a higher thermal cycle efficiency and in a rise in the working potential due to the direct interconnection of compression and the rise in addable heat. Therefore, process-wise
should be maximized to drive the process efficiency and effectiveness up. So far, this assumption is valid because there is no specification for the temperature level of the available heat. In
Section 3.2, the influence of the temperature level is further discussed.
The amount of heat that is available to be transferred to the working fluid is not solely dependent on the
but is also the result of the fuel cell efficiency that affects the ratio of heat to electrical energy output. If the FC efficiency changes, it results in an increase (lower
) or decrease (higher
) in the available heat. The amount of heat available influences the working potential of the cycle.
Figure 7 graphically demonstrates the influence on the heat conversion of a low-efficiency FC (
) in orange, a medium-efficiency FC (
) in blue and a high-efficiency FC (
) in red, deriving from the associated
. The working potential increases with the specific amount of heat available for the exFan process. The influence of the temperature level of the occurring heat is not considered in these assumptions.
2.2. Propulsor Model with an Idealized Heat Exchanger
A MATLAB R2023b model of the exFan propulsor is set up to obtain information about the process and to understand its possible benefits. A rubberized model is used, allowing for flexible sizing based on specified parameters rather than fixed dimensions. The turbomachinery approach to calculate the specific thrust over a range of
s and flight speeds for various air properties is selected. The system components are modeled with appropriate parameters for the intake diffuser, fan, and nozzle. The values of the parameters can be found in
Table 1. The idealized HX model in this section does not consider the pressure losses occurring in the HX.
For Segments 1–2, the inlet total pressure ratio, as defined in Equation (
7), is employed to determine the properties at station 2. The method follows the approach described by Hill and Peterson in [
18] to account for an appropriate reduction in the total pressure in the intake diffuser segment:
In Equation (
8), a defined polytropic efficiency is introduced, which allows to calculate different isentropic efficiencies over a range of
s. This is because the isentropic efficiency decreases with an increase in
as described by Saravanamuttoo et al. in [
19], while the polytropic efficiency stays constant. The paper focuses on low pressure ratios, implying that the isentropic efficiency changes are only minor but are still considered, as even small temperature changes have a relevant influence on the effectiveness of the HX:
Similar to Equation (
4) but including the isentropic efficiency, Equation (
9) can be formulated to calculate the total temperature after the fan:
Combining Equation (
9) with Equation (
5), it is possible to calculate the necessary specific compression work due to the fan incorporating the isentropic fan efficiency. To determine the heat generated in the FC applying a non-idealized fan, the result of Equation (
5) must be applied to Equation (
6).
Located after the fan, the transition duct is placed in Segments 3–4. The Mach number at station 4, the inlet of the HX, is defined as a control parameter in the model but is kept constant throughout this work. The value can be found in
Table 2.
The total pressure
is known and is identical to
, as the transition duct is assumed to be loss-free. The total temperature upstream of the HX
is identical to
, as an adiabatic flow process for the transition duct is assumed following the methods of Saravanamuttoo et al. in [
19].
The HX is described in more detail in
Section 2.3. This allows an idealized view of the concept with component (intake diffuser, fan, and nozzle) losses. In this section, an idealized HX should be described, which does not reduce the total pressure value but increases the total temperature. This is considered with the properties for air, with the heat capacity ratio
and the gas constant
to calculate the specific heat
. The simple approach follows Equation (
10), allowing to calculate the temperature downstream of the idealized HX with a known temperature upstream of the HX, the specific heat of air, and the given amount of heat
from Equation (
6) following [
21]:
The nozzle component efficiency is used in Equation (
11) to calculate the total pressure at station 8, knowing the parameters downstream of the HX at station 5, which are equal to 7, following the methods described in [
18]:
The model considers unchoked and choked nozzle exit flows. With the total pressure and the known ambient pressure, it is possible to check if the nozzle pressure ratio (
), see Equation (
12), exceeds the critical pressure ratio (
) [
16]. If the nozzle pressure ratio is below the critical pressure ratio, the pressure at the nozzle outlet
becomes equal to the ambient pressure
, which is equal to
for aircraft flight conditions. In the case of choked flow,
is calculated using Equation (
13). An iterative approach is required to determine
, as it is not directly available for use in Equation (
11). The nozzle is assumed to be adiabatic, resulting in
being equal to
:
Calculating the static temperature at the nozzle exit for a choked flow follows Equation (
14) and allows to calculate the nozzle exit speed using Equation (
15):
Calculating the static temperature at the nozzle exit for an unchoked flow follows Equation (
16) and allows to calculate the nozzle exit speed using Equation (
17):
With the known nozzle exit properties, it is possible to determine Equation (
18):
The pressure loss in the HX is neglected for this part of the calculation, allowing to investigate the upper efficiency limit of the process. Equation (
23) serves as the fundamental expression to compute the propulsive efficiency, while Equations (
19)–(
22) are employed to derive its specific form. Equation (
19) describes the propulsive power with the net thrust (
) and
as the flight speed. In Equation (
20), the total fan power is calculated with the specific fan work and the mass flow of the working fluid entering the ducted propulsor, which is equal to the mass flow of the nozzle exit. No friction on the shaft is assumed; therefore, the shaft power
is equal to the fan power
. The continuity Equation (
21) allows the mass flow to be calculated from the nozzle outlet area, the nozzle outlet velocity, and the density at the nozzle outlet. Equation (
22) is the momentum equation rearranged to calculate the nozzle exit area for a given
.
The parameters with the index “i” in Equations (
20)–(
23) vary depending on the selected process. There are two processes which are compared: the ducted propulsor and the exFan. The ducted propulsor process, labeled as “no HX”, does not introduce additional heat into the working fluid. In contrast, the exFan process, denoted as “HX”, involves additional heat generated by the FC. To compare these processes, the propulsive power is kept constant, and both are analyzed using a rubberized model approach:
Equation (
23) enables the calculation of the propulsive efficiency based on the flight speed, the ambient pressure, the specific work performed in the fan, the air properties, and velocity at the nozzle exit.
2.3. The Non-Idealized HX Model with Pressure Loss
This section focuses on the pressure loss in the HX
that is immanent when forcing a fluid through an HX. For a ducted propulsor with HX, this pressure loss occurring within the process causes a reduction in the propulsive efficiency, compared to the model described in
Section 2.2 that neglects the HX pressure loss. The model used in this section is the same as in
Section 2.2 but additionally incorporates the HX as a function with a constant wall temperature (
) as depicted in
Figure 8, and a constant HX inflow Mach number (
). The assumed HX inflow Mach number is proportional to the speed of the working fluid into the HX air channels.
The red square in
Figure 9 marks the area of the HX at station 4 that covers a mass flow rate equivalent of 1
ingested and depends on the parameters at the inlet of the HX. The dotted red square indicates that the necessary area for this specific airflow is not constant, as the model accounts for varying
s and flight Mach numbers, leading to different HX inlet area values at station 4. The model accepts different values for the HX inlet Mach numbers (
) and flight altitude, but both values influence the size of the marked HX inlet area.
The specific ingestion area is referred to as the area to mass flow rate ratio (
) with the unit [
] described in Equation (
24). The chosen triangle side length (
), which is found in
Figure 9, enables to calculate the number of equilateral triangles that cover the computed inlet area (
) and is an essential value to calculate the length (
) of the HX because it defines the wetted area of the HX channels. The triangular channels shall model a plate and fin HX.
For a specific expression of the area that ingests the working fluid, refer to Equation (
21). This equation is reformulated into Equation (
24) to describe the
, which can be calculated with the density and flow velocity of the working fluid at station 4 or with the given inputs shown in
Figure 9 at the inlet, as well as the additionally known air properties (
,
):
The
is used to calculate the Specific Number of Channels (
) and is given by the ratio of
to the area spanned by the equilateral triangle with the specified side length
shown in Equation (
25).
is required to calculate the HX length
using Equation (
30) via the required HX surface area
(Equation (
29)):
The HX function in the model uses the approach of [
12,
22] to calculate the values needed to exchange the amount of specific heat occurring in the FC. Different from the idealized approach, the temperature level of the heat and the working fluid temperature are considered with this function. For simplicity, the HX surface temperature
is assumed to be constant along the length of the HX, representing the temperature at which heat is available for transfer to the working fluid. This approach focuses solely on the heat transfer from the HX surface to the air, disregarding the previous heat transfer from the FC to the HX but acknowledging the amount of heat generated in the FC. An overview of the function is given in
Figure 10 and in the following Equations (
26)–(
30). Important to mention is the fact that Equation (
27) is only applicable to fully developed turbulent flow in ducts and is only partially valid for HXs. The inputs to the function from the heat side are only the wall temperature and the amount of specific heat that must be dissipated. Combining the information about the HX inlet temperature, HX inlet pressure, HX inlet Mach number, and the amount of heat that must be dissipated for the specific amount of mass flow rate yields the averaged HX values of velocity, kinematic viscosity, thermal conductivity, temperature, pressure, and heat transfer coefficient (HTC). The function is not explicitly solvable, and therefore, an iterative approach is set up:
The averaged HTC (
) calculated with Equation (
28) is used to compute the required surface area
for the specific amount of heat
that is specified to be generated by compressing 1
with the fan using Equation (
29). The previous calculated
value, combined with the triangle perimeter value, allows the calculation of the HX length using Equation (
30):
For the computation of the pressure loss through the HX, the explicit approximation of the Colebrook–White equation by Zanke [
23] is chosen, which allows to estimate the friction factor
with Equation (
31) for
> 2300. The calculation of the friction factor requires to define the surface roughness
; this value was set to 0.1 mm. The resulting pressure loss is calculated with Equation (
32), which results in the total pressure after the HX at station 5:
Figure 10 is a schematic that summarizes inputs and outputs used in the HX function. It displays the required inputs in purple, which are “
in” (
), “
in” (
), HX inlet Mach number (
), HX triangle side length (
), HX surface temperature (
), HX friction factor (
) and the heat from the FC
. The constant parameters in orange are the Prandtl number
, gas constant
, and heat capacity ratio
of air, which are implemented in the HX function. The outputs in green are “
out” (
) and “
out” (
). The calculations carried out within the function are highlighted with blue boxes.