This model combines two
AirDuctModels with a
MembraneModel to form a model of a membrane-based counter-flow
enthalpy exchanger.
Usage
Here will follow some hints for parametrization of the model.
- Heat and mass transfer are resolved locally by defining the
paramter n.
The higher the number of segments are, the better the accuracy, but
also the higher the simulation time.
Please note, that using a highly distributed air duct the Nusselt/
Sherwood number needs to be calculated locally (see parameters for
heat and mass transfer).
- By using the parameter nParallel a parallel arrangement
of several membrane and air ducts can be realized.
- The air ducts in membrane-based enthalpy exchangers are normally
divided in width by webs that provide mechanical stability.
This subdivision influences the heat and mass transfer. This is
represented by the parameter nWidth. If this effect should be
neglected set nWidth
to one.
- Two correlations are implemented to describe the convective heat
and mass transfer. By setting the parameter recDuct to false a
correlation for a flat gap according to Stephan [1] is used. Else a
correlation for rectangular Ducts according to Muzychka et. Al. [2]
is used.
- The membrane model summarizes the complete membrane structure
consisting of the thin membrane layer and the supportive layer as
producers normally declare the overall thickness.
Therefore, reasonable values for the parameter thicknessMembrane lie in between
10 to 300 μm.
- The permeability describes the water transport through the
membrane. It is given in the unit Barrer. Values in the order
of 1E5 till 1E8 are reasonable. You can choose between
a constant pemerability (default) or a variable permeability which
can be set from outside.
- The enthalpy exchanger is modelled for a counter-flow
arrangement. By setting the parameter couFloArr to false the
cross-flow portion will be calculated by a heat and mass flow
reduction based on the Efficiency-NTU-Method (see Publications).
References
[1]: Stephan, K.: Waermeuebergang und Druckabfall bei nicht
ausgebildeter Laminarstroemung in Rohren und ebenen Spalten.
Chemie-Ing.-Techn. Vol. 31, no. 12, 1959 pp. 773-778
[2]: Muzychka, Y. S.; Yovanovich, M. M. : Laminar Forced Convection
Heat Transfer in the Combined Entry Region of Non-Circular Ducts ;
Transactions of the ASME; Vol. 126; February 2004
Publications
- Kremer, M.; Mathis, P.; Mueller, D. (2019): Moisture Recovery - A
Dynamic Modelling Approach. E3S Web Conf., Volume 111, p.01099. DOI:
10.1051/e3sconf.
Assumptions
Please note, that the heat and mass transfer models implemented in
this model only provide accurate transfer models for laminar flow,
which is common for enthalpy exchangers.
Contents
Name | Description |
---|
Medium | medium in the air ducts |
- October 13, 2020 by Martin Kremer:
Deleting heat capacitor for housing due to errors in heat transfer
caused by heat capacitor.
- April 23, 2019, by Martin Kremer:
Adding heat capacitor for the housing of the enthalpy exchangers.
- January 16, 2019, by Martin Kremer:
Redeclaring sub model parameters as final. Enabling air duct models
for changes on top level.
- November 23, 2018, by Martin Kremer:
Adding model for adsorption enthalpy. Adding humidity sensor needed
for adsoprtion model.
- November 20, 2018, by Martin Kremer:
Changing mass transfer calculation: Now using permeability and
thickness of membrane instead of permeance.
- November 5,2018 by Martin Kremer:
Correcting error in calculation of heat and mass flow with cross
flow coefficient.
- August 21, 2018, by Martin Kremer:
First implementation.
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