simulation projects in se europe with ansys software tools
TRANSCRIPT
PRACE Autumn School 2013 - Industry Oriented HPC Simulations, September 21-27, University of Ljubljana, Faculty of Mechanical Engineering, Ljubljana, Slovenia
Simulation Projects in SE Europe
with ANSYS Software Tools
Dimitrios Sofialidis
Technical Manager, SimTec Ltd.
Mechanical Engineer, PhD
26 Sep. 2013 1
• Simulation in SE Europe: History & Trends.
• Major Simulation Fields – Multiphysics.
• Categories of Simulations by Application Area.
• Presentation of SimTec Simulation Projects.
• Presentation of SimTec Customers Projects.
Presentation Outline
26 Sep. 2013 2
• When SimTec was established in 2001, only a few
companies in SE Europe were conducting simulation.
High cost (& for hardware) – many applications not solvable.
Not a "mature" tool in many areas.
"Research culture" & "evidence proof" not fully deployed.
Lack of a "reliable solution" in the region.
• SimTec is proud for being a pioneer for more than 10
successful years and helped in the creation of an
industrial community that uses simulation methods today
as a standard tool for the design and optimization of
products and processes.
Simulation in SE Europe – History
26 Sep. 2013 3
• SimTec has trained +300 (mostly) engineers in +50
seminars, for the ANSYS software packages.
Almost half of the trained continue today to use the software as
commercial or academic users, supported technically by SimTec on a
continuous basis.
Many were/are students, which had/will soon be recruited by companies
with research activities to employ mathematical modeling with ANSYS.
At SimTec itself, Dimitris Papas is employed for 4 years now; he was
trained in Fluent as a student originally in 2002.
Simulation in SE Europe – The People
26 Sep. 2013 4
• Today:
Few companies have introduced simulation in their daily routine.
A significant number of companies have used simulation services at
some certain time in the past.
A lot of companies have shown interest in acquiring a permanent or
occasional simulation solution, either in-house or out–sourced
(consulting service).
Almost all productive companies of the region recognize that today
simulation can offer a significant competitive advantage for products and
services of high value–to–cost ratio.
Simulation in SE Europe – Trends
26 Sep. 2013 5
• Industrial simulation in engineering is divided today in the
following major categories:
CSM (Computational Structural Mechanics) or more commonly as FEA
(Finite Element Analysis).
CFD (Computational Fluid Dynamics).
EMag (ElectroMagnetic) Analysis.
• Each field has various categories: E.g. some categories of CSM are: o Static linear/non–linear analysis.
o Transient analysis.
o Modal analysis.
o Harmonic analysis.
o Static or Transient Thermal analysis.
o Fatigue & failure analysis.
o Explicit analysis.
Major Simulation Fields
26 Sep. 2013 6
• The last years significant progress and application are
observed for simulations thatr cover more than one
physical areas (multiphysics). And this because of the:
Complexity of the real physical processes.
Available computing power.
• All ANSYS solvers and supporting tools are ported in the
same simualation environment: ANSYS Workbench.
Support of Multiphysics capabilities, between all available solvers.
ANSYS Workbench is parametric, and supports persistent modeling,
reproducibility and scalability.
Live parametric connection to all major CAD systems.
Statistical tools for automatic optimization.
Multiphysics
26 Sep. 2013 7
• Aerospace & Defense.
• Automotive.
• Power Generation & RES.
• Chemical and Process.
• Industrial Equipment.
• Consumer Goods.
• Turbomachinery.
• Food & Beverages.
• Pharmaceutical & Biomedical.
• Building Environment & Constructions.
• Electronics & Semiconductors.
• Electric Motors.
• Telecommunications.
• ………..
Categories of Simulations by Application Area
26 Sep. 2013 9
2005. INSTA Consultants & Engineers. Greece.
CFD Model for the Smoke Extraction System in the National Museum of Modern Art in
Athens.
2005. LDK Consultants & Engineers. Libya.
CFD Model of the Ventilation/Cooling of a Power Generation Engine Hall.
2008. LDK Consultants & Engineers. Greece.
CFD Simulation of the Ventilation of the Publicly–Used Spaces of a Mall in the City of
Ioannina.
2009–2011. AKTOR. Qatar.
CFD Simulation of the Ventilation & Air–Conditioning of the Heavy–Maintenance
Hangar Bay of the New Doha International Airport.
CFD Simulation of the Foam Spraying System of the Light–Maintenance Hangar Bay
Floor of the New Doha International Airport.
2011. J&P AVAX. Cyprus.
CFD Model of the Ventilation of the Steam Turbine Hall of Vassilikos Power Plant.
2011. MELAMIN. Slovenia.
CFD Simulation of the Mixing Process Inside a Batch Reactor.
2011. TERNA Energy. Greece.
Wind Power Production Evaluation in an Existing Wind Farm.
2012. ELPEN. Greece/Germany.
CFD Simulation of the Air Flow and Particle Tracks Inside Elpenhaler DPIs.
1. Finished Consulting Projects by SimTec
26 Sep. 2013 10
1a. Smoke Propagation in N.M.M.A.
26 Sep. 2013 11
1a. Smoke Propagation in N.M.M.A.
• 7–storey old brewery. Six fire scenarios. Only public
spaces.
• Transient gases, heat and smoke release.
• Sprinkler activation and fire–suppression.
• Evacuation modeling through change of BCs.
• Pressurization modeling (temperature increase and
gases release).
• Modeling of the smoke extraction system (supply
and sucking of air from dedicated vents).
• Turbulent flow, temperature-dependent properties,
buoyant forces.
• Calculation of visibility, lethality due to poisonous
gases and heat stroke.
• Calculation of smoke propagation.
26 Sep. 2013 12
1a. Smoke Propagation in N.M.M.A.
γραμμικό στόμιο
Δ.Ε.4
Δ.Ε.1
Ι.S.2
H.Ε.2
I.Ε.2
στόμια τύπου jet
γραμμικό στόμιο
Δ.Ε.4
Δ.Ε.1
Ι.S.2
H.Ε.2
I.Ε.2
στόμια τύπου jet
χαραμάδες
Ι.S.2
χαραμάδες
Ι.S.2
1 42 3
5 86 7
9 1410 11 12 13
15 2116 17 18 2019 25242322 2726 2928
30 3531 32 33 34 3736 3938
40 4541 42 43 44 4746
1 42 3
5 86 7
9 1410 11 12 13
15 2116 17 18 2019 25242322 2726 2928
30 3531 32 33 34 3736 3938
40 4541 42 43 44 4746
26 Sep. 2013 13
1a. Smoke Propagation in N.M.M.A.
0.00
0.50
1.00
1.50
2.00
2.50
3.00
3.50
4.00
0 200 400 600 800 1000
t [s]
Q(t
) [M
W]
εκλυόμενη
απορροφημένη από τα αέρια
-0.15
-0.10
-0.05
0.00
0.05
0.10
0.15
0.20
0.25
0.30
0.35
0.40
0 200 400 600 800 1000
t [s]
Μα
ζικ
ή Π
αρ
αγ
ωγ
ή [
kg
/s]
τοξικά αέρια
αέρας
σύνολο
Stoichiometry (molar) CnHmOo ΔΗc [MJ/kg] - net (complete) AW [kg/kmol] N2-to-O2 molar ratio of air
C (n): 6 17.5 C: 12 3.76
H (m): 10 H: 1
O (o): 5 O: 16 CO--> CO2 [MJ/kmol]
N: 14 282.99
CO--> CO2 [MJ/kg]
% of C conversion to CO2 F (=CO/CO2 molar) MW [kg/kmol] 10.11
80 0.2500 CnHmOo 162
O2 32
N2 28
Reactants (molar) Reactants (mass) 1129.50 per 1 [kg] fuel Vol. Fract. Mass Fract. CO2 44
CnHmOo 1.25 CnHmOo 202.50 1.0000 - - CO 28
O2 6.75 O2 216.00 1.0667 0.2100 0.2330 H2O 18
N2 25.39 N2 711.00 3.5111 0.7900 0.7670
Products (molar) Products (mass) 1129.50 (yields)
CO2 6.00 CO2 264.00 1.3037 0.1533 0.2337
CO 1.50 CO 42.00 0.2074 0.0383 0.0372 "gases" PROPERTIES
H2O 6.25 H2O 112.50 0.5556 0.1597 0.0996 MW [kg/kmol] 40.80
N2 25.39 N2 711.00 3.5111 0.6487 0.6295
ΔΗc [MJ/kg_fuel] - net (incomplete)
15.4038
ΔΗc [MJ/kg_O2] - net (incomplete)
14.4410
CO yield [kgCO/kg_fuel]
0.2074
CO/gases [kgCO/kg_gases]
0.1373
"gases" yield [kg"gases"/kg_fuel]
1.5111
Fire Combustion Model
26 Sep. 2013 14
1a. Smoke Propagation in N.M.M.A.
Air Average Space Temperature
23
25
27
29
31
33
35
37
39
41
43
0 50 100 150 200 250 300 350 400 450 500 550 600 650 700 750
χρόνος [s]
Θερ
μο
κρ
ασ
ία [
οC
]
IΣ
HM
1os
2os
3os
4os
0.000
0.005
0.010
0.015
0.020
0 50 100 150 200 250 300 350 400 450 500 550 600 650 700 750
χρόνος [s]
Συ
γκ
έντρ
ωσ
η [
kg
/m3
]
IΣ
HM
1os
2os
3os
4os
Average CO2 & CO Concentration
8000
9000
10000
11000
12000
13000
14000
15000
16000
17000
18000
0 50 100 150 200 250 300 350 400 450 500 550 600 650 700 750
χρόνος [s]
V [
m3
/h]
ΔE4
Air Flow at Exhaust Vents
23
25
27
29
31
33
35
37
39
41
0 50 100 150 200 250 300 350 400 450 500 550 600 650 700 750
χρόνος [s]
θ [
oC
]
IE2
HE2
ΔE1
ΔE4
Temperature at Exhaust Vents
23
25
27
29
31
33
35
37
39
41
0 50 100 150 200 250 300 350 400 450 500 550 600 650 700 750
χρόνος [s]
θ [
oC
]
IE2
HE2
ΔE1
ΔE4
Temperature at Exhaust VentsAir Temperature at Exhaust Vents
26 Sep. 2013 15
1a. Smoke Propagation in N.M.M.A.
26 Sep. 2013 21
1b. CFD for the Ventilation of Public Spaces of a Mall
26 Sep. 2013 22
• Modes: A/C (summer) and Underfloor
Heating (winter).
• Calculation of heating/cooling loads for
the public spaces.
• Calculation of solar load at the model
envelope.
• Radiation modeling.
• Thermal loads from the shops, mall
entrances and visitors.
• Turbulent flow, temperature-dependent
properties, buoyant forces.
shop
shopcorridor
tend
2.2
[m]
3.5
[m]
6.0
[m]
7.5
[m]
4.2
[m]
5.0
[m]
0.2 [m]
door
girder
glass
roof slab & insulation
10 [m]
1b. CFD for the Ventilation of Public Spaces of a Mall
26 Sep. 2013 23
+1.0 [m] +1.5 [m]
[W/m2] Cooling Mode
1b. CFD for the Ventilation of Public Spaces of a Mall
26 Sep. 2013 24
+1.0 [m] +1.5 [m]
[W/m2]
Heating Mode
1b. CFD for the Ventilation of Public Spaces of a Mall
26 Sep. 2013 25
1c. CFD for Ventilation & A/C of HVH of NDIA
Dimensions:
Length=220 [m]
Width=120 [m]
Height=45 [m]
Volume
~1.1×106 [m3]
26 Sep. 2013 26
• Steady Thermal Conditions.
• Transient coolling of an Α380 aircraft
after hours under the desert sun.
• Thermal comfort conditions, sufficient
air penetration through the large height.
• Solar load calculation at the building
envelope (2.9 [MW]). Worst day/hour, air
temperature 46 οC.
• Radiation modeling.
• Heat released by Α380 (1.5 [MW]),
lighting, equipment, personnel (0.55
[MW]).
• Turbulent flow, temperature-dependent
properties, buoyant forces.
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 27
• Fabric ducts (D=2.1 [m]). Cooling air
106 [m3/h]. Recirculation air 1.8×106
[m3/h]. Entrainment air 0.15×106 [m3/h].
• Momentum sources to reproduce the
(measured by the duct manufacturer)
air velocities at various radial
distances.
• 4 large extract vents (return air to
AHUs).
• The Α380 was "naturally" modeled as
solid body with reference to the
individual properties (density, Cp,
thermal conductivity) of fuselage/wings
and engines.
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 28
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 29
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 30
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 31
1c. CFD for Ventilation & A/C of HVH of NDIA
26 Sep. 2013 32
1d. CFD of Floor Fire Suppression of HVH of NDIA
26 Sep. 2013 33
1e. CFD Model for Ventilation of Steam Turbine Hall
26 Sep. 2013 34
• Expansion of Phase III, in the same building
(PhaseIV).
• Confirmation of temperatures &
overpressure.
• Solar load calculation at the building
envelope.
• Specific weather conditions (38 οC).
• Heat release from equipment (turbines,
generators, etc.) of 307 [kW].
• Cool air supply from 24 nozzles at low
height, extraction by 14 roof fans and 9 free
vents at the floor level.
• Turbulent flow, temperature-dependent
properties, buoyant forces.
1e. CFD Model for Ventilation of Steam Turbine Hall
26 Sep. 2013 35
1e. CFD Model for Ventilation of Steam Turbine Hall
26 Sep. 2013 36
1e. CFD Model for Ventilation of Steam Turbine Hall
26 Sep. 2013 37
1e. CFD Model for Ventilation of Steam Turbine Hall
26 Sep. 2013 38
1f. CFD Analysis of a Batch Reactor
• Scale–Up of an existing reactor 10 [m3]
to one of 30 [m3].
• Evaluation of 3 alternative impellers for
faster mixing.
• Fluid injection into a water solution from
the top. Injection duration 20 [s].
• Free surface modeled as symmetry
plane. Injection modeled as mass and
momentum sources.
• Rotation speed 44 [rpm].
• Turbulent flow, mixture of 2 liquids
(equivalent to water).
• Simplification of the solution by 4
solution stages.
3 Blades in 90o Staggered
Configuration
26 Sep. 2013 39
Impeller #1 Impeller #2 Impeller #3
2.2M cells 2.1M cells 3.0M cells
26 Sep. 2013 40
Impeller #3
1f. CFD Analysis of a Batch Reactor
26 Sep. 2013 41
Impeller #1 Impeller #2
Impeller #3
0.0
0.2
0.4
0.6
0.8
1.0
1.2
1.4
1.6
1.8
2.0
2.2
0 50 100 150 200 250 300
Un
ifo
rmit
y
Time [s]
Max
Min
time [s] Min Uniformity Max Uniformity
20 0.0000 301.3778
40 0.2691 2.3427
60 0.8759 1.3261
80 0.9489 1.1261
100 0.9643 1.0281
120 0.9866 1.0063
140 0.9970 1.0014
160 0.9996 1.0008
180 0.9997 1.0004
0.0
0.2
0.4
0.6
0.8
1.0
1.2
1.4
1.6
1.8
2.0
2.2
0 50 100 150 200 250 300
Un
ifo
rmit
y
Time [s]
Max
Min
Torque 8.3 [Nm] Torque 8.0 [Nm]
Torque 6.6 [Nm]
C
)t(CC1)t(U
Uniformity
1f. CFD Analysis of a Batch Reactor
26 Sep. 2013 42
Impeller #1 Impeller #2 Impeller #3
Red: U=0.95 Green: U=0.97 Blue: U=1.00
1f. CFD Analysis of a Batch Reactor
26 Sep. 2013 43
1g. Power Assessment of an Operating Wind Farm.
• Operating farm with 18 W/T in operation.
• Available measurements at mast and power
production for 1 year.
• Domain radius=6000 [m], height=4000 [m]. Outer
radial extend=1500 [m].
• First cell at 2 [m], 1.42Μ cells. Automatic
refinement around the W/T.
• Division in 16 sectors (wind directions). Automatic
alignment of W/T with the wind.
• W/T modeled as negative momentum sources. W/T
shadowing effects included.
• Terrain roughness and forest model (porous
medium).
• Atmospheric boundary layer conditions at inlet,
zero or no thermal gradient.
26 Sep. 2013
Data collected at mast
Wind conditions predicted at WTG
Wind data transposition module
44
Transposition Method
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 45
• 64 automatically performed simulations (scripting) for 4 wind speeds (5, 10, 15
& 20 [m/s] at mast top height=60 [m]) and for 16 wind directions.
• Self–correlation of the mast measurements.
• W/T capacity factors were calculated, with reference to the predictions at the 4
mast heights, with statistical projection for the whole year of operation.
• The same procedure was performed without shadowing effect. The difference
of the two calculations is an estimate of the shadowing losses.
Wake Losses
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 46
• Annual and monthly averages for the wind speed at the W/T hub height.
• Annual averages of the capacity factors per wind direction for each W/T.
• Annual averages κfor each wind speed range of the turbulence intensity at the
W/T hub height.
• Wind speed, wind angle, turbulence intensity, shear factor at the W/T hub
height per wind direction and wind speed range
• Power in [kW] in 10 [min] intervals for each W/T for the whole year of operation.
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 47
WT1
Automatic Production of Graphs.
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 48
Contours of critical
terrain (>16.7o) along
the wind direction.
292ο
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 49
Contours of the shear
factor at the W/T hub
height, per wind
speed range and wind
direction.
270ο
15 [m/s]
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 50
Pathlines at W/T hub
height, per wind
speed range and wind
direction.
247ο
10 [m/s]
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 51
Pathlines on the
ground , per wind
speed range and wind
direction.
247ο
10 [m/s]
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 52
All graphs available on GoogleEarth!
247ο
10 [m/s]
1g. Power Assessment of an Operating Wind Farm.
26 Sep. 2013 53
1h. CFD Study of a Drag Inhaler (Elpenhaler)
“Mouthpiece"
"Base"
unused blisters storage
compartment (2 parts)
Double Blister
"Distributor"
"Diaphragm"
"Cone"
separator
CFD modelregion
26 Sep. 2013 54
• Confirmation of efficient operation.
• Further optimization.
• Underpressure from patient's inhaling.
• Turbulent, compressible air flow, which carries
the particles to the exit.
• Very small gaps, mesh of 7.7Μ cells.
• Steady conditions (assumption).
• Particle tracking without effect on the air flow
(uncoupled) for specific size distribution.
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 55
32.71[g/min]
33.05[g/min]
29.76[g/min]
65.76[g/min]
65.76[g/min]
5.00[g/min]
5.19[g/min]
25.81[g/min]
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 56
Turbulence
Intensity
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 57
Results for the
path and fate of
the particles.
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 58
Residual time of
particles vs
diameter
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 59
1h. CFD Study of a Drag Inhaler (Elpenhaler)
26 Sep. 2013 60
2α. Military Technical Institute of Serbia
26 Sep. 2013 61
2α. Military Technical Institute of Serbia
Modeling the Aerodynamic Behavior of a High–Lift Airfoil (HLA)
AOA=10o
Ma=0.14
Flap
leading
edge gap
26 Sep. 2013 62
2α. Military Technical Institute of Serbia
Static Pressure [Pa]
Stream Function [kg/s] Mach Number [–]
Static Temperature [K]
separation
26 Sep. 2013 63
2α. Military Technical Institute of Serbia
Surface Pressure Coefficient Profiles
26 Sep. 2013 64
2a. Military Technical Institute of Serbia
Time–averaged contours from
the transient LES solution.
Static Pressure [Pa]
Velocity Magnitude [m/s]
Static Temperature [K]
26 Sep. 2013 65
2a. Military Technical Institute of Serbia
Static Pressure Stream Function
26 Sep. 2013 66
2b. Bulgarian Ship Hydrodynamics Center
26 Sep. 2013 67
2b. Bulgarian Ship Hydrodynamics Center
Ι. Steady–State Sheet Cavitation over a 2D hydrofoil
Pressure
Coefficient
Cavity
Extent
26 Sep. 2013 68
2b. Bulgarian Ship Hydrodynamics Center
ΙI. Flow about the ITTC Test Screw Propeller No.4119
Thrust & Torque
Coefficients
26 Sep. 2013 69
2b. Bulgarian Ship Hydrodynamics Center
ΙII. Flow about a model 6000t cement carrier
Bow Stern
26 Sep. 2013 70
2b. Bulgarian Ship Hydrodynamics Center
ΙV. Hydrodynamic Study of an UUV
26 Sep. 2013 71
2b. Bulgarian Ship Hydrodynamics Center
V. Store Separation in Water
U=5 [m/s]
Vinit=10 [m/s]
U=5 [m/s]
Vinit=5 [m/s]
26 Sep. 2013 72
2c. Gorenje d.d.
26 Sep. 2013 73
I. Refrigerators – Freezers
2c. Gorenje d.d.
26 Sep. 2013 74
I. Refrigerators – Freezers
2c. Gorenje d.d.
• Target: to reduce the energy consumption for A+ class certification.
• 4 different configuration of evaporator channels were simulated.
• A prediction of 5% energy consumption for the best evaporator design was
confirmed by measurements in the prototype.
26 Sep. 2013 75
I. Refrigerators – Freezers
2c. Gorenje d.d.
• Initial design was exhibiting high temperatures on the surfaces around the
lamp.
• After simulating 3 different designs, the problem was solved.
26 Sep. 2013 76
I. Refrigerators – Freezers
2c. Gorenje d.d.
• The analysis target was to optimize the cold air recirculation in the
refrigerator.
• A few alternative designs were simulated in FLUENT.
• A prototype was constructed and measured.
• Good temperature control was achieved, as well as temperature stability
inside the refrigerator.
26 Sep. 2013 77
II. Cookers
2c. Gorenje d.d.
26 Sep. 2013 78
II. Cookers
2c. Gorenje d.d.
Path Lines Pressure Contours
Temperature (heater) Temperature (blades)
26 Sep. 2013 79
II. Cookers
2c. Gorenje d.d.
26 Sep. 2013 80
2d. EL.K.E.ME.
26 Sep. 2013 81
I. Modeling a Furnace for the Annealing of Aluminum Rolls
2d. EL.K.E.ME.
• Thermal power of 1.2 MW (12 direct U–tube burners).
• Convection heat transfer (N2 flow driven by 2 fans).
• 6 aluminum rolls of different diameter and sheet thickness.
• The burners operate in on/off mode (with pilot) and the fans in two speeds (low/high).
• Anisotropic thermal resistance and thermal conductivity, dependent on the sheet
thickness.
26 Sep. 2013 82
I. Modeling a Furnace for the Annealing of Aluminum Rolls
2d. EL.K.E.ME.
26 Sep. 2013 83
II. Modeling the Heating of a
Metal Slab
in a Furnace of Continuous Flow
III. Modeling of Continuous
Casting of Aluminum/Steel
(Melting/Solidification)
2d. EL.K.E.ME.
26 Sep. 2013 84
2e. HIDRIA d.d.
26 Sep. 2013 85
2e. HIDRIA d.d.
I. Modeling of Axial/Centrifugal Fans for A/C Units
26 Sep. 2013 86
2e. HIDRIA d.d.
I. Modeling of Axial/Centrifugal Fans for A/C Units
0.5 [m]
0.5 [m]
• 1/7th modeled.
• 700k cells.
26 Sep. 2013 87
2e. HIDRIA d.d.
I. Modeling of Axial/Centrifugal Fans for A/C Units
Pressure
26 Sep. 2013 88
2e. HIDRIA d.d.
I. Modeling of Axial/Centrifugal Fans for A/C Units
0
5
10
15
20
25
30
35
40
45
50
0 5000 10000 15000 20000 25000
Flow Rate, Q [m3/h]
To
tal E
ffic
ien
cy [
%]
experiment
FLUENT
0
50
100
150
200
250
300
0 5000 10000 15000 20000 25000
Flow Rate, Q [m3/h]
Sta
tic P
ressu
re D
iffe
ren
ce
[Pa]
experiment
FLUENT
Total Efficiency
Static Pressure Rise
26 Sep. 2013 89
2e. HIDRIA d.d.
IΙ. HVAC Studies
26 Sep. 2013 89
2e. HIDRIA d.d.
IΙ. HVAC Studies
26 Sep. 2013 92
2f. DANFOSS Trata d.o.o.
District Heating Equipment
26 Sep. 2013 93
2f. DANFOSS Trata d.o.o.
District Heating Hydraulic Valve Modeling
• Calculation of flow rate, as a function of valve opening and differential pressure.
• Minimization of cavitation, noise and vibrations.
1.5M cells
26 Sep. 2013 94
2f. DANFOSS Trata d.o.o.
District Heating Hydraulic Valve Modeling
Pressure Velocity
Magnitude
Turbulence
Intensity
26 Sep. 2013 100
2g. DOMEL d.o.o.
Dry
Vacuum
Motors
Wet
Vacuum
Motors
DC Motors
Commutator
Motors
Brushless
Pumps &
Fans
EC Drives
& Fans
26 Sep. 2013 101
2g. DOMEL d.o.o.
Ι. Dry Vacuum Motor CFD Model
600k cells
26 Sep. 2013 102
2g. DOMEL d.o.o.
Ι. Dry Vacuum Motor CFD Model
p [Pa]
ΤΙ [%]
Mach
26 Sep. 2013 103
2g. DOMEL d.o.o.
ΙI. Modeling Smooth (2D) and Twisted (3D) Impellers
2D, 1/9
0.6M cells
3D, 1/9
1.9M cells
26 Sep. 2013 104
2g. DOMEL d.o.o.
ΙI. Modeling Smooth (2D) and Twisted (3D) Impellers
3D
2D
Pressure Wall Shear Stress Temperature
26 Sep. 2013
2h. NV–FLUID d.o.o.
Fuel Tankers
Bitumen/Heavy Oil Tankers
Chemicals TankersLiquified Gases Tankers
Special Tankers
Aircraft Refuelers
106
26 Sep. 2013
2h. NV–FLUID d.o.o.
107
Structural Analysis of a Road Tanker
patch
sides
ribs
ribs
ribs
sides
foot
foot
• Check for ADR2007 certification.
• Combination of loading conditions.
26 Sep. 2013
2h. NV–FLUID d.o.o.
108
Structural Analysis of a Road Tanker
The following loading scenarios were solved:
I. Only the weight of the structure (19 [kN]) & fluid (110 [kN]).
II. Only the gas pressure (18 [bar]).
III. Weight of structure/fluid & gas pressure, i.e. W+P load.
IV. W+P load & accelerating with 2g.
V. W+P load & breaking with 2g.
VI. W+P load & turning with 1g.
VII. W+P load & dropping with 2g.
VIII. W+P load & rising with 1g.
IX. W+P load & accelerating by 2g & temperature 40oC.
X. W+P load & accelerating by 2g & temperature 60oC.
XI. W+P load & breaking by 2g & temperature 40oC.
XII. W+P load & breaking by 2g & temperature 60oC.
26 Sep. 2013
2h. NV–FLUID d.o.o.
109
Structural Analysis of a Road Tanker
Only P W+P & turning (1g)
W+P & dropping (2g) W+P & accelerating 2g
& 40oC
Equivalent Stress
26 Sep. 2013
2h. NV–FLUID d.o.o.
110
Structural Analysis of a Road Tanker
Equivalent Stress
Only P W+P & turning (1g)
W+P & dropping (2g) W+P & accelerating 2g & 40oC
26 Sep. 2013
2i. TŽV–GREDELJ d.o.o.
111
26 Sep. 2013
2i. TŽV–GREDELJ d.o.o.
112
Structural Analysis of a Wagon Base
1/4 of real model (2 symmetries)
solid model, 53k elements
26 Sep. 2013
2i. TŽV–GREDELJ d.o.o.
113
Structural Analysis of a Wagon Base
safety
factor
equivalent
stress
26 Sep. 2013
2i. TŽV–GREDELJ d.o.o.
114
Structural Analysis of a Wagon Base
Equivalent Elastic Strain
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
115
Power Transformers
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
116
I. Modellling of an Oil-Cooled Transformer
• 1/4 of the model simulated, due to symmetry.
• Oil, air & steel materials, with temperature–
dependent properties.
• Heat (3.1 [kW]) is dissipated from the transformer.
• Calculate heat drawn by the oil (buoyant flow).
13M cells.
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
117
I. Modeling of an Oil–Cooled Transformer
Air Pressure Oil Pressure
Air
Velocity
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
118
I. Modeling of an Oil–Cooled Transformer
Oil Temperature
Air Temperature
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
119
II. Structural Modeling of the Frame of a Transformer
• 1/4 of the model simulated, due to
symmetry.
• Shell model.
• Material: Structural steel.
• Load: Vacuum.
• 95k elements.
26 Sep. 2013
2j. KOLEKTOR ETRA d.o.o.
120
II. Structural Modeling of the Frame of a Transformer
Deformation Equivalent Stress
Safety
Factor
26 Sep. 2013
2k. KOLEKTOR LIV d.o.o.
121
26 Sep. 2013
2k. KOLEKTOR LIV d.o.o.
122
CFD Model of a Cavitating Valve
400k cells
26 Sep. 2013
2k. KOLEKTOR LIV d.o.o.
123
CFD Model of a Cavitating Valve
0
200
400
600
800
1000
0.0 0.2 0.4 0.6 0.8 1.0
Pressure Differece, dp [MPa]
Vo
lum
etr
ic F
low
Ra
te [
lt/h
]
FLUENT
EXPERIMENT
• Multiphase flow (liquid–vapor).
• Predict flow rate vs dp.
• Evaluate cavitation rate, as a function
of dp.
Path lines (colored with
time) for dp=8 [bar].
26 Sep. 2013
2k. KOLEKTOR LIV d.o.o.
124
CFD Model of a Cavitating Valve
Pressure Velocity Magnitude Turbulence Intensity
dp=8 [bar]
dp=8 [bar] dp=10 [bar]
26 Sep. 2013
2n. Brodarski Institut d.o.o.
134
I. CFD Analysis of an Azimuth Pushing Type Thruster
26 Sep. 2013
2n. Brodarski Institut d.o.o.
135
II. Modeling the Operation of CO2 Fire Extinguish System
in a Ship Engine Room
t=240 [s]
t=320 [s]
t=190 [s]
26 Sep. 2013
Extending the limits...
141
Unconventional simulations
SimTec 12 Years