Proceedings of the 7th World Congress on Mechanical, Chemical, and Material Engineering (MCM'21)
Prague, Czech Republic Virtual Conference – August, 2021
Paper No. HTFF 138
DOI: 10.11159/htff21.138

Numerical Simulation of Innovative Air Capture Systems Based On
Bladeless Technology
Maurizio Carlini1, Andrea Mennuni1, Mirko Rotondo2, Stefano Morelli2
CIRDER, University of Tuscia, 01100 Viterbo, Italy
maurizio.carlini@unitus.it; andrea.mennuni@unitus.it
2
DEIm, University of Tuscia, 01100 Viterbo, Italy
mirko.rotondo@unitus.it; stefano.morelli894@gmail.com
1

Abstract - This work focuses on the feasibility study of a new suction hood model that allows the complete disposal of the fumes
produced during cooking. The originality of this study lies in the conception of a new functional geometry meant to reduce consumption,
focusing on the increase of both efficiency and aspiration efficiency. The new technology is based on the Coandă effect applied on two
innovative air capture systems of hood model. On one hand the air flow amplifier, a system that, starting from a low inlet flow rate,
allows 10 times increasing of the output flow rate. On the other hand, the bladeless fan, which is usually implemented in newest bladelessventilation systems. A simulation campaign has been conducted with COMSOL Multiphysics software to validate the simulation
scenarios comparing the experimental results with respective references. For the post-validation step, the parametric sweep function has
been used to study the system behaviours to every change of velocity, flow rate and extension of the ejector. The obtained results show
the feasibility of these new suction systems, which present lower consumptions than other modern ventilation systems for kitchens. The
computed results show that the perimeter velocity is in accordance with European standards. The perimeter velocity for air flow amplifier
geometry allows a suction capacity range between 460 m3/h and 3600 m3/h. In the bladeless fan case, the suction capacity is in a range
between 325 m3/h and 2500 m3/h. Therefore, the two geometries can be installed for both domestic and commercial kitchens.
Keywords: Bladeless technology; Coandă effect; air capture system; extractor hood; COMSOL Multiphysics; CFD analysis;

multiparametric analysis.

1. Introduction

In order to reduce pollution emissions, innovative technologies are growing in accordance with current EU standards interms of energy efficiency, in coupling with the renewable sources.
Hoods for fumes extraction are present in all homes, inside industries and in catering environments. Their main function,
especially in the kitchen environment, is to extract the cooking fumes, improving the air quality where the device is installed[1]. Clearly, the position is a crucial consideration, since an incorrect placement leads to fumes and pollutants stagnation
inside the dwelling [2]. For a correct ejection of the produced fumes, a fan must be installed to allow and guarantee a sufficient
prevalence and flow rate, managing to overcome the load losses generated by the presence of the filter (to remove solid
particles and liquids of grease and steam contained by the fluid crossing the hood) [3]–[5].
The design of the aspiring systems must be provided in accordance with different European standards and requirements.
Moreover, the size and type (professional or domestic) of the installation environment have to be considered. The
fundamental parameter is the calculation of the right suction flow for the disposal from the surrounding environment, of themain cooking fumes pollutants, in order to avoid the spread of contaminants inside the housing structure [6]–[9]. Proper
design finds the right compromise between the aspirated flow rate that allows the disposal of all pollutants and the higher
energy efficiency [10], [11], always in accordance with EU directives [12]. In fact, the world is moving to sustainable
principles by means of known technologies optimization, such as for the building sector [13], [14], for the photovoltaic
system [15], [16], for the biological conversion [17]–[19] using different input biomasses [20]–[22] and for the geothermal
field [23], [24]. The study of these technologies can be extended by a simulation software, allowing the development of
numerical campaigns on virtual prototypes [25], [26], reducing the production costs in the meanwhile [27], [28].
This work aims to define the velocity field of n. 2 hood models with bladeless technology through COMSOLMultiphysics software, validating the simulation scenarios with the reference data. Then, a parametrization is used to change

HTFF 138-1

the geometry (ejectors), velocity and flow rate, observing the feasibility and the behavior of the systems. The various
advantages of the installation of the bladeless technology are the absence of moving parts in the suction area (vibrations are
not produced), reduced cleaning and maintenance, low noise, high suction capacity, reduced weight and consumption.

2. Materials and methods

2.1. Experimental Characterization
The study involves the collection of bibliographical data that will be used as a reference for numerical simulations.
Two different geometries are analyzed, a first geometry called Air flow amplifier, basically an air amplifier, and a second
one called Bladeless fan. Both of these models take advantage of the Coandă effect which leads to an increase in terms of
output flow, which is even 10 times higher than the inbound one. In particular, for the Air flow amplifier, several elaborations
concerning optimization and CFD simulation (Computational Fluid Dynamics) have been reported by [29], [30], while for
the Bladeless fan the main reference has been provided by the engineering company BW Engineering © and the company
Dassault Systèmes ®, developer of the Abaqus software and CAD software SolidWorks ®. For both models, given the highcomplexity, CAD-based software has been used to extrapolate the correct measurements. Therefore, several papers havebeen analyzed for the Bladeless fan [29], [30]: for both geometry [31]–[33] and simulation conditions the geometry a tutorial
by the engineering company BW Engineering has been chosen [34].
2.2. Main Physical Phenomena Identification and Implementation
The Coandă effect indicates that a flow flowing over a surface is influenced by two simultaneous forces. The global
effect is a deviation of the fluid layers near the surface, as such layers show a tendency to adhere to the same surface[35]. Multiple applications have been developed about Coandă effect, leading to significant improvements both inaeronautics [29] and in medicine [36], [37].
The analysis is carried out through COMSOL Multiphysics (CM), a multiphysical simulations software which provided
a multidisciplinary approach to the physics and phenomena to implement within the scenario. CM resolution approach isbased on the Finite Element Method (FEM) to solve physical models and engineering problems [38]–[40]. Several papers
have been consulted to understand the phenomenon before its implementation in CM [41]–[43]. In this particular case,axisymmetric 2D geometry is chosen as a spatial dimension and the CFD module is used for physics. By means of the CFD
module, as provided by CM, it is possible to model in the same scenario environment both the heat transfer to solids or fluids
and reagent flows. In this study, the "Turbulent Flow" interface of the "Single-Phase Flow" model contained within
COMSOL Multiphysics's "Fluid Flow" module is selected [44].
2.3. Simulation Campaign
The strategy of the simulation campaign is based on the reference data obtained by bibliography. The full geometry isdefined in CM as shown by Fig. 1a and Fig. 1b for the Airflow amplifier and Bladeless fan, respectively.

(a)

(b)

Fig. 1: The whole geometry of: a) Air flow amplifier; b) Bladeless fan.

HTFF 138-2

Once the geometry is designed, it is possible to pass through the materials selection and assignment. In this case thematerial that needs to be selected is air. The boundary conditions made for the study of turbulent flow k – 𝜀𝜀 are the following:
wall (No slip), inlet where the mass flow (𝑚𝑚𝑖𝑖𝑖𝑖 = 0,25 kg/s) is inserted for the Air flow amplifier model while the conditionof velocity (𝑣𝑣𝑖𝑖𝑖𝑖 = 2 m/s) is implemented for the Bladeless fan model, outlet by using the pressure condition for bothgeometries and open contour to identify the boundary where incoming and outcoming fluxes are possible. Then, the modelis meshed and calculated by means of a stationary approach. The simulation output is the 2D velocity across the wholegeometry. Once the scenarios have been validated, a parametric sweep is conducted to carry out a wider analysis. In thiscase, for both geometries a sweep is initialized referring to n. 2 parameters and, for each of them, 4 different values are
considered. It follows that n. 16 scenarios are solved. Referring to the Air flow amplifier scenario, the flow rate (𝑚𝑚𝑖𝑖𝑖𝑖 ) andthe curvature of the arcs (that influences the ejector opening) change, as defined by Table 1. In the case of the Bladeless fan
scenario, the velocity (𝑣𝑣𝑖𝑖𝑖𝑖 ) and the point that defines the ejector opening vary, as defined by Table 1. The different
combinations allow the study of the velocity field of the two systems as the inlet conditions and the ejector opening change.
Then, it is possible to identify which configuration should be used for a specific application.
Table 1: Parametric sweep for the Air flow amplifier.
Air flow amplifier
Bladeless fan

3. Results

Parameterejector [mm]𝑚𝑚𝑖𝑖𝑖𝑖 [kg/s]
ejector [mm]𝑣𝑣𝑖𝑖𝑖𝑖 [m/s]

0,30
0,10
1,00
1,00

0,50
0,15
1,15
2,00

Value

0,55
0,20
1,30
3,00

0,65
0,25
1,40
4,00

3.1. Numerical scenarios validation
The first step is the validation of the scenarios comparing the results obtained by numerical simulation (from COMSOLMultiphysics) with the ones by reference data. The maximum discrepancy of these results has been fixed up to 5.0%, which
follows the scenario validation. The velocity field in the whole geometry is reported by Fig. 2 and Fig. 3 for the Air flow
amplifier and Bladeless fan scenarios, respectively. Calculating the discrepancies in different points, the obtained values
satisfy the discrepancy requirement for both models, therefore the numerical scenarios can be considered validated.

(a)(b)
Fig. 2: Velocity field of the Air flow amplifier scenario: a) whole implemented geometry; b) focus around the ejector.

HTFF 138-3

(a)
(b)
Fig. 3: Velocity field of the Bladeless fan scenario: a) whole implemented geometry; b) focus on the “shovel”.

More in details, once validating numerical scenarios, Table 2 defines the simulation results compared with the reference
data to calculate the discrepancy for the Air flow amplifier and Bladeless fan models.
Table 2. Validation of the models with the reference values for both Air flow amplifier [29] and Bladeless fan [34] scenarios.
Model
Air flow amplifier
Bladeless fan

Valuemaximum velocity
ejector output velocity
velocity on curvature
maximum velocity
queue velocity

Reference data
[𝐦𝐦/𝐬𝐬]281,50200,00 – 210,00
180,0035,09
15,00 – 16 ,00

Simulation result[𝐦𝐦/𝐬𝐬]282,00203,00174,0035,80
15,58Discrepancy[%]
0,18
1,50 – 3,33
3,33
2,02
3,87 – 2,63

3.2. Parametric analysis
Explicit selections are defined through the "Definitions" section of CM. These selections are used to calculate thevelocity at increasing distances from the perimeter edge for the Air flow amplifier and Bladeless fan model, respectively. In
order to understand if a hood could be installed inside a commercial or domestic room, it is very important to consider thevelocity on the perimeter edge. Its value is required to be higher than 0,25 m/s (referring to European standards). In Table 3,
the velocity results are reported depending on the opening of the ejector and the distance from the edge of the hood in
different values of inlet flow rate for the Air flow amplifier. In Table 4, the velocity results are reported depending on the
opening of the ejector and the distance from the edge of the hood in different values of inlet velocity for the Bladeless fan.
Results highlighted in red identify the perimeter velocities that need to be compared with the minimum ones eligible by theEuropean standards.
Table 3: Perimeter velocity values at different heights for different ejector openings and inlet flow rates (Air flow amplifier).

0,30 [mm]0,50 [mm]0,55 [mm]0,65 [mm]Velocity at different heights [m/s]
0 cm 25 cm 45 cm 65 cm 85 cm
0,68
0,66
0,36
0,18
0,09
0,53
0,50
0,31
0,16
0,08
0,48
0,45
0,30
0,15
0,07
0,40
0,38
0,28
0,14
0,07

0,30 [mm]0,50 [mm]

1,45
1,14

AE / Point

𝒎𝒎𝒊𝒊𝒊𝒊 = 0,10 kg/s
𝒎𝒎𝒊𝒊𝒊𝒊 = 0,15 kg/s

HTFF 138-4

1,19
1,02

0,55
0,48

0,28
0,24

0,14
0,12

0,55 [mm]0,65 [mm]

1,05
0,89

0,98
0,91

0,46
0,42

0,23
0,21

0,11
0,10

𝒎𝒎𝒊𝒊𝒊𝒊 = 0,20 kg/s

0,30 [mm]0,50 [mm]0,55 [mm]0,65 [mm]

2,31
1,92
1,76
1,51

1,61
1,38
1,33
1,23

0,75
0,64
0,62
0,57

0,38
0,32
0,31
0,29

0,19
0,16
0,15
0,14

𝒎𝒎𝒊𝒊𝒊𝒊 = 0,25 kg/s

0,30 [mm]0,50 [mm]0,55 [mm]0,65 [mm]

3,08
2,64
2,44
2,14

2,02
1,74
1,67
1,55

0,94
0,81
0,78
0,72

0,47
0,41
0,39
0,36

0,24
0,20
0,19
0,18

Table 4: Perimeter velocity values at different heights for different ejector openings and inlet velocities (Bladeless fan).

𝒗𝒗𝒊𝒊𝒊𝒊 = 1,0 m/s

1,00 [mm]1,15 [mm]1,30 [mm]1,40 [mm]Velocity at different heights [m/s]
0 cm 25 cm 45 cm 65 cm 85 cm
1,25
0,15
0,06
0,03
0,01
1,20
0,14
0,06
0,03
0,01
1,13
0,13
0,05
0,03
0,01
1,06
0,12
0,05
0,02
0,01

𝒗𝒗𝒊𝒊𝒊𝒊 = 2,0 m/s

1,00 [mm]1,15 [mm]1,30 [mm]1,40 [mm]

3,10
2,97
2,72
2,52

0,30
0,29
0,26
0,25

0,12
0,12
0,11
0,10

0,06
0,05
0,05
0,05

0,02
0,02
0,02
0,02

𝒗𝒗𝒊𝒊𝒊𝒊 = 3,0 m/s

1,00 [mm]1,15 [mm]1,30 [mm]1,40 [mm]

5,18
5,00
4,63
4,30

0,46
0,44
0,40
0,38

0,19
0,18
0,17
0,16

0,09
0,08
0,08
0,07

0,03
0,03
0,03
0,03

𝒗𝒗𝒊𝒊𝒊𝒊 = 4,0 m/s

1,00 [mm]1,15 [mm]1,30 [mm]1,40 [mm]

7,26
6,96
6,47
6,07

0,61
0,58
0,54
0,51

0,25
0,24
0,22
0,21

0,11
0,11
0,10
0,10

0,04
0,04
0,04
0,04

AE / Point

4. Discussion

The study highlighted the feasibility of the creation of suction hoods with Air flow amplifier and Bladeless fan geometry,
identifying which of the two solutions should be the most suitable to be implemented into domestic or commercial
environments. European standards were consulted for the benchmarks, in particular for the velocity on the perimeter edge ofthe hood, the minimum required value to be considered was 0,25 m/s. The identification of the punctual velocities at different
distances from the perimeter edge of the hood was conducted for n. 5 points. Table 3 shows slightly lower values for distancesfrom the edge of the hood of 65,00 and 85,00 cm, but a correct suction of the fumes remains possible. In fact, the standard
prescribes that the velocity on the perimeter edge of the hood must be equal to or greater than 0,25 m/s and, in the case of
Air flow amplifier geometry, this condition is always respected for all analyzed incoming flows. The choice to evaluate thedevelopment of velocity at different distances from the hood boundary allows to identify which configuration can be installed
as required. In particular, once computed results have been evaluated, it should be possible to identify which solution, withthe same ejector opening, is the most affordable for the consumption while maintaining a correct expulsion of the smokes
produced. The flow rates generated by the system is between 460,00 m3/h and 3600,00 m3/h, so this system could be used

HTFF 138-5

for both kitchens in domestic and commercial contexts. For the collection of Bladeless fan system data, the same steps andtypes of evaluation are performed. Table 4 shows a decreasing trend of velocity as the distance from the edge increases,
reaching very low values at distances of 65,00 cm and 85,00 cm but the velocity on the perimeter edge is still greater thanthe minimum required. In general, with Bladeless fan geometry the reached flow rates are lower than the Air flow amplifier,being between 325,00 m3/h and 2500,00 m3/h. Furthermore, the obtained data for both geometries identify a progressive
velocity decrease while ejector opening increasing.

5. Conclusion

The study highlights the possibility to install both systems in home and commercial kitchen environments using
bladeless technology. Two models have been investigated: the Air flow amplifier and the Bladeless fan. The Air flow
amplifier and the Bladeless fan have been validated comparing the 2D stationary Finite Element Method simulation scenarioswith the reference data in terms of reached velocities. The used method for the validation is the calculation of the discrepancy
between numerical and bibliography data: the values are below the imposed upper limit of 5%. Then, a parametrization of
input values is conducted to study the behavior of the systems and to understand if these models can be work correctly in
different input conditions. The chosen parameters for the Air flow amplifier are the ejector opening and the inlet flow rate
while for the Bladeless fan those parameters are the ejector opening and the inlet velocity. For different opening conditionsof ejector, referring to both models, the velocity on the perimeter edge of the hood is compared with the European standard,
which is imposed at 0,25 m/s. All the collected velocities on the perimeter point overcome the European limit, therefore thestudied geometries could be used. These models have to be slipped into the real case to understand the needs of real field
application. Furthermore, the Air flow amplifier (powered by a compressor) could work correctly even inside larger kitchens,
since the maximum flow rates are greater than Bladeless fan geometry (system powered by an engine with a fan, also
positioned at a distance of 60,00 cm).

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