Thermoelectric Membrane Distillation System Engineering ...
Transcript of Thermoelectric Membrane Distillation System Engineering ...
49th International Conference on Environmental Systems ICES-2019-117 7-11 July 2019, Boston, Massachusetts
Thermoelectric Membrane Distillation System
Engineering Design Improvement Concepts
Jeffrey M. Lee1 and Lance Delzeit2
NASA Ames Research Center, Moffett Field, CA, 94035, USA
Jurek Parodi3
Bionetics Corporation, Yorktown, VA, 23693, USA
Gregory Pace4
KBRwyle, Houston, TX, 77002, USA
and
Serena Trieu5
Logyx LLC, Mountain View, CA, 94043, USA
All of the membrane distillation technologies that National Aeronatics and Space
Administration (NASA) has examined to date require external heating and cooling subsystems
to drive the distillation and condensation processes. Since energy is added to the system to
change liquid water into vapor, and energy is rejected from the system to convert vapor back
into a liquid, a higher efficiency is achieved when the enthalpy of liquefaction is recaptured
for use in supplementing the enthalpy of vaporization. The Thermoelectric Membrane
Distillation (TMD) system embeds thermoelectric devices acting as heat pumps directly at the
membrane surface into a self-contained device, thereby heating the retentate while
simultaneously cooling the permeate. A flexible testing apparatus has been developed to
quickly validate the TMD concept and to characterize different key performance parameters,
which have been utilized to develop models for the design of engineering prototypes. This
paper describes the validation of our proof-of-concept work and the design improvements
implemented to improve performances, and the degradation of performances observed during
long-duration testing.
Nomenclature
ARC = Ames Research Center
BEB = Brine Evaporation Bag
CAD = computer-aided design
CFD = computational fluid dynamics
CPVC = chlorinated polyvinyl chloride
DAQ = data acquisition
DCMD = Direct Contact Membrane Distillation
DOC = Direct Osmotic Concentration
ESM = equivalent system mass
ID = internal diameter
1 Chemical Engineer, Bioengineering Branch, M/S 239-15. NASA Ames Research Center. 2 Chemist, Bioengineering Branch, M/S 239-15. NASA Ames Research Center. 3 Aerospace Research Engineer, Bioengineering Branch, M/S 239-15, NASA Ames Research Center. 4 Senior Research Engineer, Bioengineering Branch, M/S 239-15, NASA Ames Research Center. 5 Engineer, Bioengineering Branch, M/S 239-15, NASA Ames Research Center.
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IWP = Ionomer-membrane Water Processor
K = kelvin
MD = membrane distillation
NASA = National Aeronautics and Space Administration
NI = National Instruments
PP = polypropylene
PVC = polyvinyl chloride
SGMD = Sweeping Gas Membrane Distillation
T = temperature
TEC = thermoelectric cooler
Tf = final temperature
Ti = initial temperature
TIME = Thermoelectric Integrated Membrane Evaporative Subsystem
TMD = Thermoelectric Membrane Distilliation
TRL = technology readiness level
V = Volts
VMD = Vacuum Membrane Distillation
I. Introduction
URRENT state-of-the-art membrane distillation technologies use bulky external heating and cooling subsystems
to provide the heating and cooling necessary to drive the distillation process, which adds to launch mass, create
heat losses, and are a source of viscous flow losses1. The Thermoelectric Membrane Distillation (TMD) system
eliminates these external subsystems by embedding thermoelectric devices directly at the surface of the membrane.
Membrane Distillation (MD) is driven by water vapor pressure gradients across the two sides of a hydrophobic
membrane, which defines the physical location of the phase interface and mass transport. The membrane is permeable
to water vapor but impermeable to the liquid water phase and to most contaminants present in urine and other
wastewater sources. The use of membranes for phase separation is particularly well suited in microgravity
environments. The innovation behind TMD is to incorporate thermoelectric devices at the membrane surface, which
act as heat pumps by heating the retentate while simultaneously cooling the permeate. Thus, mass transport, energy
transport, and phase separation are achieved into a single, self-contained system with no moving parts that reduces
equivalent system mass (ESM) and increases reliability when compared to state of the art distillation systems.
II. TMD Background
MD uses a hydrophobic membrane that is permeable to water vapor to separate waste water (retentate) from
distilled water (permeate). Heating the retentate and cooling the permeate is usually used to create a water vapor
pressure differential across the membrane, which drives the water vapor flux through the pores of the membrane itself.
Adding heat to the warm retentate side vaporizes liquid water that diffuses through the membrane pores to the cold
permeate side, where it then recondenses. Higher temperature differentials have the advantage of creating higher vapor
pressure driving forces. However, higher retentate temperatures increase the permeation of volatile contaminant gases.
NASA has investigated the following types of MD to recover water from urine, urine brine, and hygiene water for
space missions. The Direct Osmostic Concentration (DOC)2 project and the Thermoelectric Integrated Membrane
Evaporative Subsystem3 (TIME) projects both examined the use of Direct Contact Membrane Distillation (DCMD),
which uses a membrane to separate the liquid phases of the permeate and retentate with water vapor transport within
the pores of the membrane. The Brine Evaporation Bag4 (BEB) project investigated the use of Vacuum Membrane
Distillation (VMD), employs a vacuum on the permeate side of the membrane. The Ionomer-membrane Water
Processor5,6 (IWP) investigated Sweeping Gas Membrane Distillation (SGMD), which uses a flowing gas such as dry
air over the permeate side of the membrane. All these MD methods require external subsystems such as pumps,
blowers, chillers, condensers, and heaters to provide the latent heat energy for bringing water from its initial liquid
phase to a gas phase and then back to a final liquid phase. Moreover, recuperative heat exchanges and/or a heat pumps
are needed in order to recover the heat of condensation and increase energy efficiency.
C
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The vapor compression cycle used
in MD is shown in Figure 1. In order
to minimize the amount of work
necessary to drive this process and
thus to use the power available
onboard the spacecraft more
efficiently, the enthalpy of
liquefaction should be recaptured and
used to supply part of the enthalpy of
vaporization.
In TMD, the thermoelectric device
embedded at the surface of the
membrane is used as a heat pump that
simultaneously removes heat of
condensation from the permeate side
and rejects it to the retentate side, thus
incorporating both cooling and
heating in a single, self-contained
system. The heat taken from the cold
side is ideally the enthalpy released by the recondensing water vapor. The heat rejected to the warm side is used to
vaporize the water. The transport of heat from the permeate to the retentate requires some work (electrical in this
case) according to the 2nd law of
thermodynamics. Thus, additional heat is
rejected at the permeate due to this added
electrical work. As a result, the total heat
rejected to the permeate is higher than the
required enthalpy of vaporization and the
additional heat must be rejected to the
environment. Figure 2 shows a diagram of the
main components constituting TMD and the
related mass and energy transport process. In
this configuration, the thermoelectric device
is sandwiched between two membranes, one
separating the hot plate of the thermoelectric
from the retentate, and the other separating
the cold plate of the thermoelectric from the
permeate.
III. TMD Testing
The approach used to validate the TMD technology concept consisted of several iterative rapid prototyping, testing,
and simulation phases that addressed issues observed during each new phase and to gather the information needed to
develop the requirements for a higher technology readiness level (TRL) system. Several test apparatus were
manufactured to test the performance of the TMD technology in different operational scenarios and to quickly generate
critical data. High-fidelity computer aided design (CAD) models for the each test apparatus have been developed and
the outcomes of the respective flow simulation analysis have been compared to the experimental results, which
allowed tuning of the parameters used in the computational fluid dynamics (CFD) tool. A set of flow simulation
analyses were performed to develop future test apparatus with the objective of increasing the performances of the
system. This paper summarizes the experimental results obtained during the proof-of-concept testing of the initial
TMD prototypes and the engineering designs of improvement concepts of the system.
Figure 1. T-s diagram for vapor compression cycle.
Figure 2. Mass and energy transport diagram of TMD with
thermoelectrics sandwiched between membranes.
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Figure 3 shows the diagram of the
first generation of the testing
apparatus, used for a set of batch mode
experiments. This configuration
consisted in a thermoelectric cooler
(TEC) sandwiched between two
coupons of hydrophobic membrane,
all kept in place by two symmetric
assemblies made of plastic fittings.
This resulted in a gap between the two
membrane coupons, requiring water
vapor transport within this gap from
the hot membrane coupon to the cold
one. The main advantage of this
configuration was the easiness to
accommodate the thickness of a
commercially available TEC (4mm)
by using off-the-shelf silicone flange
gaskets and the creation, through the
gap between the two membranes, of a
barrier to heat flow from the hot
retentate to the cold permeate. Each of
the two symmetric assemblies
consisted in a flange connected to an elbow with a hose barb fitting to which is attached a transparent and graduated
column. A CAD cutout of the of one of the assembly with a gasket and the TEC is shown in Figure 4.
The membrane used in all TMD experiments is a
high-porosity microporous membrane from Celgard,
named EZ2090. It is composed of a single layer of
polypropylene (PP) material and it is characterized by
a thickness of 20 micron, a porosity of 67%, and an
average pore size of 97 nanometers. Other properties
include stability over a pH range between 2 and 12, a
highly uniform pore structure, and a moisture vapor
transmission rate of 100,000 g/m2/day. It is designed
specifically for applications that require a
hydrophobic but highly breathable barrier such as
membrane distillation. It has been down-selected
among other membrane candidates because of its
higher porosity and pore size and comparable
chemical resistance and mechanical strength.
The TEC used during this first set of experiments
is a commercially available module from TE
Technology, part number CH-109-1.4-1.5. The
dimensions of the module are 40mm x 40mm x 4mm.
It has a hole with a diameter of 13mm in the center.
The minimum and maximum operational
temperatures are respectively 40ºC and 80ºC. At 50ºC
on the hot side, the maximum voltage input is 15.2 V
and the maximum amperage is 6.1 A. The maximum coefficient of performance is function of the input voltage and
of the temperature differential between the cold and the hot side. The module is potted on all sides between the two
ceramic plates to provide waterproofness.
A series of two commercially available high-temperature, silicone flange-gaskets with a third, custom made gasket
of the same material located in the middle are used to secure the TEC and the membranes between the flanges of the
two assemblies, preventing the system from leaking, protecting the ceramic plates of the TEC from excessive
compression (and cracking) when the flanges are connected and tightened together, and allowing the wires of the TEC
out of the system.
Figure 3. Diagram of TMD static testing apparatus.
Figure 4. Cutout drawing of one of the two symmetric
assemblies of the testing apparatus.
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Each side of the system integrates an internal thermocouple that is
inserted inside the assembly through the column so that its probe is in
direct contact with the surface of the membrane. Moreover, each side of
the system integrates an external thermocouple, the probe of which is stick
to the surface of the plastic elbow. A power supply with adjustable current
and voltage output provides the desired power to the TEC during the
experiment.
Initial tests were conducted with deionized water and recording
temperature and static pressure head (water level in the graduated
columns) across the membranes as a function of power input to the TEC.
The general operating procedure was to fill the permeate and retentate
sides until the column levels reached the same initial and equal reference
level. Power to the TEC was then turned on and held constant, generally
until steady state was achieved. At steady state, the power was turned off
and the system allowed to passively dissipate heat until achieving room
temperatures.
Figure 5 shows the first version, consisting in chlorinated polyvinyl
chloride (CPVC) flanges and ¾” CPVC fittings, Buna-N gaskets, and
flexible hoses with ¼” internal diameter (ID) as columns. The results of
the preliminary tests done using the CPVC flanges and fittings showed a
level increase of the water columns on both sides of the TEC, which goes
against the law of conservation of mass. In particular, the trends of the
water column on the cold side of the TEC are consistent with expectations,
growing in function of time, and growing faster at a higher input power,
which corresponds to a higher differential temperature between the two
sides. On the hot side, instead, the water column increased during the
transient phase of the process, independently of the power input,
maintaining the level for a certain time into the steady state phase, only to
start decresing afterwards. This observations indicated that there were
phenomena affecting the behavior of the system. In particular, the
difficulty to fill the two sides of the system suggested that some air
remained trapped within the chambers between the flanges and the hose
barb.
Thus, the testing apparatus was modified to implement transparent flanges and fittings in order to identify any
presence of air bubbles in the chambers at the end of the filling process. The flanges also have capped ports used for
removing excess air bubbles present in the system.
Figure 6 shows the third version of the testing apparatus, which was used for most of the experiments conducted
to characterize the flow rates
across the system in function of
the TEC power. This version is
characterized by clear, custom-
made acrylic flanges, 1 ½” clear
PVC elbows, and clear acrylic
tubes with 3/8” ID as graduated
columns. This configuration
allowed the observation and the
removal of any air bubbles
trapped during the filling of the
system. Moreover, it verified the
position of the thermocouple
probes and reduced the thermal
conductivity between the two
sides of the system. A CAD
section view of the of this
version is shown in Figure 7.
Figure 5. First generation testing
apparatus.
Figure 6. Third generation testing apparatus.
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Several experiments conducted
with this version of the apparatus
and with initial conditions
characterized by the absence of
any visible air bubbles in the
system still showed a rapid
increase of the water column on the
hot side of the TEC during the
transient phase of the experiment.
This observation led to the
conclusion that the main physical
phenomenon responsible for this
behavior is the volumetric
expansion of water related to the
rapid growth of temperature during
the transient phase. Above 4ºC, the
density of water decreases and its
volumetric expansion coefficient
increases with rising temperatures.
The variation in volume was calculated as:
𝛥𝑉 = 𝑉 ∫ 𝛼𝑉(𝑇)𝑑𝑇𝑇𝑓𝑇𝑖
(1)
where 𝑉 is the initial volume of the water, 𝑇 its temperature, 𝛼𝑉(𝑇) is the volumetric expansion coefficient of water
as a function of temperature 𝑇, and 𝑇𝑖 & 𝑇𝑓 as the initial and final temperatures, respectively. To validate these
adjustments, after the system was cooled down at the end of the experiment and the the water columns reached room
temperature, the corrected and uncorrected values converged. A subsequent reversal of the TEC current to create the
temperature conditions for reversing the permeation was also conducted, and showed that water did flow back as
would be expected.
The graph in Figure 8 summarizes the results obtained during a set of experiments conducted using the system
configuration described above. The graph shows the relationship between the volume of water produced, the
temperature differential between the two sides of the system, the temperature of the permeate, and the flow rate across
the membranes in function of
power. As expected, all four
variables increased with
power. The volumes and flow
rates are corrected for thermal
expansion. Each datapoint in
the graph represents the
average of all the datapoints
collected during the steady
state of each run. In fact, each
run can be divided into two
phases. The first phase is the
transient, during which there is
a rapid increase of temperature
on the hot side of the TEC and
a rapid creation of a
temperature differential
between the two sides of the
system. During this phase, the
level of the permeate does not
show any apparent change
while the level of the retentate
Figure 7. Cutout drawing of the the third version of the testing apparatus.
Figure 8. Summary of experimental results obtained using third version TMD
with 40x40 TEC.
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increases dramatically. In correspondence with the stabilization of the temperatures and temperature differential,
which signals the beginning of the steady state, where the level of the permeate starts to increase while the level of
the retentate decreases linearly. Each run lasts 8 hours; after the power supply is turned off and the system cools down,
both the permeate and retentate reaches the initial temperature and the values of the uncorrected and corrected volumes
converges.
Figure 9 is an example of a flow simulation analysis conducted to investigate the behavior of different parameters
of the system during a run with initial and boundary conditions identical to the values measured during an actual
experiment. The objective
was to determine the
effects of conductivity and
convection on the
temperature profiles
internal to the system.
Figure 9 in particular
shows the results at the
beginning of the steady
state. A comparison with
the actual experimental
data determined that the
flow simulation tool can be
used with a good degree of
confidence to analyze new
configurations and new
engineering concepts. The
main limitation of this tool
were found to be the
impossibility to select
multiple solid materials
with different material
properties and the impossibility to simulate phase changes and mass transport of the water vapor.
A second set of batch mode experiments using the same testing apparatus was conducted using a TEC with a
smaller heating/cooling surface area and a single membrane coupon. The TEC used during this set of experiments is
a commercially available module from TE Technology, part number TE-65-0.6-0.8. The dimensions of the module
are 12mm x 12mm x 2.6mm. The minimum and maximum operational temperatures are respectively 40ºC and 80ºC.
At 50ºC on the hot side, the maximum voltage input is 8.9 V and the maximum amperage is 2.1 A. The module is
potted both on all sides
between the two ceramic
plates to provide
waterproofness. The TEC
is kept in place against the
membrane coupon by a
custom made silicon
gasket flange. In this
configuration, the water
vapor is transported
directly from the retentate
to the permeate across the
membrane pores.
A summary of the
results obtained during this
set of experiments is
shown in the graph in
Figure 10. The graph
compares the volume of
water produced, the
temperature differential
Figure 9. Simulation results at the begininning of the steady state in third version
TMD.
Figure 10. Summary of experimental results obtained using third version TMD
with 12x12 TEC.
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between the two sides of the
system, the temperature of the
permeate, and the flow rate across
the membranes with respect to the
orientation of the TEC and its
power. The first subset of
experiments was conducted with
the cold plate of the TEC facing
the membrane, while the second
subset was conducted with the hot
plate of the TEC facing the
membrane. All four variables
increase with power and the
highest flow rate is achieved in
the former case. Figure 11 shows
the results of the flow simulation
analysis conducted to compare the
temperature profiles inside the
retentate chamber and at the
membrane surface during the two
subset of experiments described
above in a 1g or “normal gravity”
environment. The temperature
gradient at the membrane surface
is higher when the cold plate of
the TEC faces the membrane and this corresponds to a higher flow rate according to experimental data. The membrane
constitutes a barrier to convective flows and to thermal conduction between the retentate and the permeate. Thus, a
higher temperature gradiend and lower average temperature along the surface of the membrane also means a lower
temperature of the permeate and a higher temperature gradient across the membrane itself, which explains the higher
flow rates.
A fourth-generation system was developed to automate the system control and data collection process by
integrating low-pressure transducers on both sides of the apparatus, using clear 1 ½” PVC tees instead of elbows to
integrate the transducers and to achieve a direct view of the surface of the membrane, not subject to diffraction. This
new configuration allowed
a continuous, more precise,
and automated reading of
the static pressure of the
liquid columns using
National Instruments (NI)
data acquisition (DAQ)
hardware with LabVIEW
software. The data from the
LabVIEW program is used
to analyze the pressure and
its correlation from the
temperature readings. Any
pressure variation also
corresponded to a variation
in volume across the TEC,
which was calculated in the
LabVIEW program.
Moreover, the input voltage
and amperage provided to
the TEC is automatically
adjusted to maintain the
desired temperature or
Figure 11. Simulation results of temperature profiles inside the retentate
chamber ans a the membrane surface.
Figure 12. Diagram of last version of static TMD testing apparatus.
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temperature differential between the two sides of the
system. The diagram of this new configuration is
shown in Figure 12 and the system is shown in Figure
13. However, this design had the disadvantage of a
much longer transient phase due to the bigger volume
of the retentate and permeate fluid reservoirs, which
is almost four times higher compared to the ones in
the third-generation TMD.
IV. TMD Engineering Design Improvement Concepts
The observations and experimental results collected with the prototype testing apparatus described above and the
flow simulation analysis conducted to investigate the behavior of different parameters of the system were used to
develop new system configurations and new engineering concepts that would maximise the performances of TMD. A
design that places heating and cooling elements in the vicinity of
the membrane within the diffusion layer reduces thermal losses
when compared to larger system and reduces the need for
turbulent flow to supply heat of vaporization and liquifaction.
Smaller retentate and permeate fluid reservoirs decrease the
transient time and heat losses.
Figure 14 shows the design of system derived from the third-
generation TMD testing apparatus characterized by thinner fluid
reservoirs that integrates the TEC into the membrane itself.
Conductive meshes are attached to the ceramic plates of the TEC
on both the retentate and permeate sides to distribute heat transfer
from the plates to the liquid with more homogeneous temperature
within the reservoirs. This configuration would be more
representative of the conditions found in microgravity. The heat
flux provided by the TEC must be limited by the transport rate
across the membrane since the water cannot reach the point of
boiling. The maximum temperature differential achieved between
the permeate and retentate in this configuration is 63 kelvins (K),
higher compared to values from both experimental and simulation
data of the existing prototypes, while the average temperature
differential across the membrane is 1.56 K with a standard
deviation of 1.88 K. The temperature profile along the vertical
axis of the membrane, centered with respect to the TEC, is shown
in the graph in Figure 15. For comparison, the graph in Figure 16
shows the values for the third generation testing apparatus.
Figure 14. Engineering concept design
improvement.
Figure 13. Fourth generation TMD testing apparatus.
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Figure 16. Temperature profiles along the vertical centerlines on the two sides of the membrane
for the concept design.
Figure 15. Temperature profiles along the vertical centerlines on the two sides of the membrane for the
third generation TMD.
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V. Conclusion
The initial proof-of-concept tests have generated promise for TMD as a new means for membrane distillation.
TMD uses water selective hydrophobic membranes to maintain phase separation, and embeds thermoelectric heat
pumps at the membrane surface. This arrangement allows for a complete, self-contained wastewater distillation system
that has the advantage of eliminating bulky external support systems such as heating and cooling systems, pumps,
blowers, and recuperative heat exchangers. For these reasons, TMD is especially applicable for space missions where
volume and mass are at a premium and where insufficient gravity exists to adequately manage liquid-vapor interfaces.
Proof-of-concept has been validated through experimental demonstration and flow simulation analysis. New
engineering design concepts have been developed and investigated to increase system performances. Future steps are
experimental testing with a representative waste solution, testing of a continuous flow system and engineering designs
that include electrical circuitry printed on membranes and different TEC distribution and size relative to membrane
open area.
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