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i n t e r n a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 2
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Release characteristics of highly pressurizedhydrogen through a small hole
Sang Heon Han a,*, Daejun Chang a,*, Jong Soo Kim b
aDivision of Ocean System Engineering, Korea Advanced Institute of Science and Technology, 373-1 Guseong-dong, Yuseong-gu,
Daejeon 305-701, South KoreabKorea Institute of Science and Technology, 39-1 Hawolgok-dong, Seongbuk-gu, Seoul, South Korea
a r t i c l e i n f o
Article history:
Received 18 September 2012
Received in revised form
13 November 2012
Accepted 16 November 2012
Available online 23 January 2013
Keywords:
High pressure hydrogen leakage
Jet dispersion
Small hole
Mass flux
* Corresponding authors. Tel.: þ82 42 350 157E-mail addresses: [email protected] (S.H
0360-3199/$ e see front matter Copyright ªhttp://dx.doi.org/10.1016/j.ijhydene.2012.11.0
a b s t r a c t
A hydrogen supplying system for hydrogen fuel cell cars is anticipated to utilize highly
pressurized hydrogen gas at pressures up to 700 bar. In this highly pressurized environ-
ment, large amount of hydrogen can be leaked from a relatively small hole caused by
material and mechanical defects. A leaked hydrogen jet can reach very far in distance and
the size of the leak plays an important role in determining the safety of hydrogen recharge
facilities. This study numerically investigated the concentration distribution and the mass
flux of hydrogen leaked from a highly pressurized source through a hole whose size is less
than 1.0 mm. Numerical analysis was performed in axisymmetric coordinates on the
assumption that the hydrogen jet has a huge Froude number and that buoyancy forces can
be negligible. The predicted hydrogen concentration along the centerline of a hydrogen jet
was compared with experimental data for verification of the numerical analysis and it
satisfied the hyperbolic decay characteristics and matched the experiment well. The mass
fluxes for the various hole lengths of this study were found to be 5%e20% less than those
predicted using an isentropic flow assumption.
Copyright ª 2012, Hydrogen Energy Publications, LLC. Published by Elsevier Ltd. All rights
reserved.
1. Introduction carbon energy strategy is significantly more costly than the
Transportation, which accounts for approximately 20% of CO2
emission from by fossil fuel combustion in typical industri-
alized countries, is the third major CO2 emission sector,
following the power and industry sectors. However, formu-
lating a CO2 reduction strategy for the transportation sector is
muchmore difficult becausemotor vehicles are nonstationary
and extremely small CO2 emission sources, emitting about
one millionth of the amount of large scale coal power plants
and blast furnaces. Consequently, in the Energy Technology
Perspectives 2008 [1], the International Energy Agency (IEA)
recommended a non-carbon energy strategy, i.e., employing
hydrogen or electricity to power motor vehicles. This non-
4; fax: þ82 42 350 1510.. Han), [email protected] , Hydrogen Energy P71
CCS (CO2 Capture and Storage) strategy applicable for the
power and industry sectors, in that the marginal CO2 abate-
ment cost for the transportation sector range from 200e500$/
tCO2, whereas those for the power and industry sectors range
from 50e100$/tCO2 and 100e200$/tCO2, respectively. Never-
theless, a non-carbon energy strategy is still necessary to
achieve a deep CO2 reduction from the transportation sector
to stabilize the atmospheric CO2 level by 2050. The IEA-BLUE
Map scenario, developed with a specific target to CO2 stabili-
zation by 2050, calls for a 50%CO2 emission reduction globally,
which can be translated into an 80% CO2 emission reduction
for typical industrialized countries and a 90% CO2 emission
reduction for the USA.
u (D. Chang).ublications, LLC. Published by Elsevier Ltd. All rights reserved.
Page 2
Nomenclature
A coefficient in Eq. (21)
a, b coefficients of line in Eq. (23)
CD discharge coefficient
Cp,k specific heat of k-th species, J/(kg K)
d diameter of hole, m
dps pseudo diameter of abrupt expansion, m
e!z; e!
r unit vectors, m
k turbulent kinetic energy or decay coefficient
h specific enthalpy, J/kg
L length of hole, m_m mass flux, kg/m2 s
Pr Prandtl number
p pressure, N/m2
r radial coordinate, m
R gas constant, J/(kg K)
Sc Schmit number
T temperature, K
uz, ur velocity components, m/s
XH2 hydrogen concentration
Yk mass fraction of k-th species
z axial coordinate, m
Greek symbols
3 turbulent dissipation
m, mt, meff molecular viscosity, turbulent viscosity, and
effective viscosity, kg/s m
r density, kg/m3
g ratio of specific heats
F dissipation function
Subscripts
k index for element or species
s isentropic
LFL lean flammability limit
i n t e rn a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 23504
At this moment, it is unclear which will emerge as the
dominant non-carbon energy source for the transportation
sector among hydrogen and electricity. To win the competition
to become the dominant non-carbon transportation energy
system, it is necessary to develop not only the hydrogen or
electric vehicle technologies into a system capable of supplying
power in as large a quantity as that of gasoline engine vehicle,
but more importantly the corresponding energy infrastructure
from the energy producers to the terminal users. In this regard,
the hydrogen energy system is at a significant disadvantage
because it has yet to be built and the safety of the hydrogen
energy system needs to be fully addressed. In particular,
hydrogenfillingstationsareunder strict public scrutinybecause
it iswhere theenergysystemcomes intocontactwith thepublic.
Hydrogen is one of the most reactive compounds. On the
other hand, hydrogen has a very low volumetric energy
density and a great tendency to buoyantly disperse away from
a leaking source. Consequently, the safety of hydrogen filling
stations can be greatly improved by promoting the dispersion
of leaking hydrogen before exposure to an ignition source.
When developing the hydrogen station safety code that will
guarantee the safety for such station operators as well as for
the public, better quantified hydrogen jet characteristics will
enable us to maximize the safety potential by specifying
guidelines to promote the dispersion and dilution of the highly
reactive hydrogen. Therefore, it is the objective of this present
study to quantify the characteristics of hydrogen leaking from
a high pressure system through a small rupture hole.
Birch [2] demonstrated that the mean centerline concen-
tration profiles for various natural gas jets can be collapsed
into a single curve if the longitudinal distance from a virtual
point source is non-dimensionalized by a virtual diameter
derived from the mass balance. Birch’s approach for natural
gas jets was later extended to hydrogen jets by Ruffin et al. [3].
The concentration profile of hydrogen jets, established by
leakagewith constant pressures at up to 25 bar, wasmeasured
by Shirvill et al. [4] with an oxygen sensor. Takeno et al. [5]
measured the transient hydrogen concentration of a hypo-
thetical scenario for a large scale leakage from a pipeline.
Houf and Schefer [6,7] carried out experimental studies on the
dispersion of hydrogen jets arising from leakage with low
pressures.
Numerical studies on the release of highly pressurized
hydrogen have been performed in two ways. The first and
major concern of this study [8e14] is performed by analyzing
the dispersion of the hydrogen jet into ambient air in view of
safety. The domain sizes of theseworks are very large, such as
factory fields or urban sections. In this case, the precise
characteristics of the abrupt hydrogen expansion just after
exit through the cracked hole are neglected because of
numerical inappropriateness. The mass flow rate for the inlet
boundary is calculated using an isentropic flow assumption.
The second way [15,16] focuses on the abrupt expansion
characteristics of the jet. This way explores the expansion
length, pseudo diameter, and normal shock e essential data
for the Birch approach.
This study directly calculates both the mass flux and the
dispersion characteristics of a hydrogen jet leaked from
a highly pressurized source using numerical analysis. The
mass flux can be obtained by calculating the flow field inside
a source reservoir, which is almost stagnant, and a cracked
hole, which is being choked. The typical velocity and length
scales for high pressure hydrogen leakage are assumed to be
u w 1500 m/s, corresponding to the hydrogen sound speed,
and d w 1 mm, respectively. The resulting Froude number,
defined to be u2/gd, is on the order of 108, so that the buoyancy
effect, which is capable of bending the hydrogen jet upward, is
negligible and two dimensional axisymmetricity can be
assumed to significantly reduce numerical efforts.
2. Mathematical formulation
2.1. Isentropic approach
Fig. 1 depicts the hydrogen jet leaked from a source, which can
be a storage vessel or a flow line. When hydrogen is released
through a hole created in a high pressure vessel or flow line,
Page 3
INFINITRESERVOIR
Fig. 1 e Schematics of abrupt expansion (Ref. [2]).
i n t e r n a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 2 3505
the flow is choked near the exit of the hole. Neglecting viscous
dissipation and introducing an adiabatic wall assumption
inside the hole, the flow is isentropic. At the choking point, all
the flow variables can be obtained by combining the chocking
condition and the isentropic flow assumption:
P2;s ¼ P0
�2
gþ 1
�g=g�1
; T2;s ¼ T0
�2
gþ 1
�; r2;s ¼
P0
RT0
�2
gþ 1
� 1g�1
(1)
u2;s ¼ c2;s ¼ffiffiffiffiffiffiffiffiffiffiffiffiffiffigRT2;s
p ¼ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiRT0
�2g
gþ 1
�s(2)
The flow velocity is sonic velocity at the choking point. The
mass flux can be determined with the flow variables calcu-
lated at the choking point:
_ms ¼ CDr2;su2;s ¼ CDP0ffiffiffiffiffiffiffiffiRT0
p�
2gþ 1
� 1g�1
ffiffiffiffiffiffiffiffiffiffiffiffi2g
gþ 1
s(3)
Leaving the hole, the flow experiences an abrupt expansion
as shown in Fig. 1. The abrupt expansion is completed in
a very short distance (z10d), and it ends with a normal
shock. The flow becomes incompressible after the normal
shock. If the entrainment of air is neglected during the abrupt
expansion, the hydrogen concentration follows the mean
axial concentration hyperbolic decay rule after the normal
shock:
XH2¼ kdps
zþ z0
�rair
rH2
�12
¼ kdzþ z0
�rair
rH2
�12
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiCD
�2
gþ 1
�ðgþ1Þ=2ðg�1Þ P0
Pair
s(4)
The derivation of Eq. (4) is described in Ref. [2]. In Eqs.
(1)e(4), z, z0, k, dps, g, CD are coordinates along the jet center-
line, virtual origin, decay coefficient, pseudo-diameter, ratio of
specific heats and the discharge coefficient, respectively.
2.2. Governing equations for flow, energy, and species
The numerical problem is formulated by simultaneously
solving for a high-pressure hydrogen reservoir, a choked
cracked hole and a hydrogen jet into the atmosphere. The
axisymmetric continuity, momentum, turbulent kinetic
energy and eddy dissipation rate equations governing the
thermo-fluidic characteristics can be written as:
v
vzðruzÞ þ 1
rv
vrðrrurÞ ¼ 0 (5)
v
vzðruzuzÞ þ 1
rv
vrðrruruzÞ ¼ �vp
vzþ vszz
vzþ 1
rv
vrðrsrzÞ (6)
v
vzðruzurÞ þ 1
r
v
vrðrrururÞ ¼ �vp
vrþ vszr
vzþ 1
r
v
vrðrsrrÞ � sqq
r(7)
v
vzðruzkÞþ1
rv
vrðrrurkÞ¼ v
vz
��mþmt
sk
�vkvz
�þ1rv
vr
�r
�mþmt
sk
�vkvr
�þG�r 3
(8)
v
vzðruz 3Þ þ 1
rv
vrðrrur 3Þ ¼ v
vz
��mþ mt
s 3
�v 3
vz
�þ 1
rv
vr
�r
�mþ mt
s 3
�v 3
vr
�
þ C 31G3
k� C 32r
32
kð9Þ
where
u ¼ uz e!
z þ ur e!
r (10)
meff ¼ mþ mt; mt ¼ rCm
k2
3(11)
G ¼ mt
��vuz
vzþ vur
vr
�2
þ2
�vuz
vz
�2
þ2
�vur
vr
�2
þ2�ur
r
�2�
(12)
szz ¼ meff
�2vuz
vz� 23V$u
�(13)
srr ¼ meff
�2vur
vr� 23V$u
�(14)
szr ¼ srz ¼ meff
�vuz
vrþ vur
vz
�(15)
sqq ¼ meff
�2ur
r� 23V$u
�(16)
The values of the model parameters are C1 3 ¼ 1.44,
C2 3¼ 1.92, Cm ¼ 0.09, sk ¼ 1.0 and s 3¼ 1.3. The conservation
equations of energy and species equations are as follows:
v
vzðruzhÞ þ 1
rv
vrðrrurhÞ ¼ v
vz
��m
Prþ mt
sh
�vhvz
�þ 1
rv
vr
�r
�m
Prþ mt
sh
�vhvr
�
þF�V$
�r
�12juj2þk
�u
�ð17Þ
v
vzðruzYiÞ þ1
rv
vrðrrurYiÞ ¼ v
vz
��m
Scþmt
ss
�vYi
vz
�þ1rv
vr
�r
�m
Scþmt
ss
�vYi
vr
�(18)
where:
h ¼Xk
Ykhk ¼Xk
Yk
ZT
Tref
Cp;kðTÞdT (19)
F ¼ v
vzðuzszz þ urszrÞ þ 1
rv
vr½rðuzsrz þ ursrrÞ� (20)
Page 4
i n t e rn a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 23506
Here, F denotes source terms of the energy equation due to
dissipation work. In this study, both the turbulent Prandtl
number sh and the turbulent Schmit number ss are taken to be
0.9. The ideal gas law is used for the state equation.
3. Results and discussion
3.1. Comparison between experiment and prediction
KIST (Korea Institute of Science and Technology) measured
the concentration of a released hydrogen jet from a highly
pressurized chamber, representing a high pressure vessel.
The hydrogen concentration was measured along the jet
centerline for three cases of small leak hole diameters
(d ¼ 0.5 mm, 0.7 mm and 1.0 mm). The hole diameters are
chosen in such a way that the hole area increases by
approximately two for each diameter increase. For each
diameter, the measurements are carried out for four cases of
chamber pressures (P0 ¼ 100 bar, 200 bar, 300 bar and 400 bar)
using a gas sampling method. However, KIST failed in
measuring the hydrogen concentration for d ¼ 1.0 mm and
P0 ¼ 400 bar because of the jet duration was too short to
complete the measurement. The concentration of hydrogen
was measured at five locations along the hydrogen jet
centerline e 1.0 m, 3.0 m, 5.0 m, 7.0 m and 9.0 m.
The geometrical model for this study is depicted in Fig. 2. It
has a pressure-inlet boundary at a distance enough far from
the leak hole. A fictitious slip wall is adopted for computa-
tional stability. The fictitious wall should be carefully located
in two reasons. The first reason is that the fictitious wall
should not disturb themain hydrogen jet flow by putting it too
close to the axis. The second reason is that computational
stability cannot be achieved by locating it too far from the axis.
Its location is different for different computational conditions.
In combination with the fictitious wall, an air intake inlet
boundary is added to the computation because it is necessary
to supply fresh air into the main flow. Consequently, the
actual boundary surrounding the jet is divided into the two
boundaries.
Fig. 3 shows the measurement and prediction. The
prediction was achieved by using FLUENT [17]. Both the
experimental and numerical results exhibit a gradual mono-
tonic decrease of the centerline hydrogen concentration with
excellent agreement until the 3rd probe at a 5m distance from
the exit for all diameters. Such an agreement indicates that
the experiment and the numerical simulation were carried
out in a physically reasonablemanner. The experimental data
for d ¼ 0.5 mm begin to show significant deviations from their
numerical counterparts from the 4th probe at a 7 m distance.
In the case of d ¼ 0.7 mm, both results still maintain
ReserviorInlet
Outlet
Axis
Fictitious Wall (Slip Boundary)Air intakeInlet
x
r
Fig. 2 e Geometric model used for the computation.
consistency at the 4th probe, but they show some deviation at
the 5th probe at a 9 m distance. The experimental data from
d ¼ 1.0 mm show some deviation from the 4th probe, but not
as severe as the d ¼ 0.5 mm case. The figure shows that the
downstream characteristics of the experiment aremuchmore
susceptible to disturbances by wind, especially for smaller
hole diameters and lower source pressures.
Among a number of causes contributing to the deviation
far downstream, the following three causes appear to be
outstanding. First, the virtual wall introduced for numerical
stability may have contributed to the over-prediction of the
hydrogen concentrations in the numerical analysis. As the jet
is being developed, the jet diameter becomes wide enough to
be affected by the virtual wall, which prevents the jet from
further expanding. Consequently, the numerical analysis
would over-predict the hydrogen concentration profiles,
particularly in the downstream region. Second, there is
measurement error associated with the alignment of the jet
centerline. The sampling probes might not be placed exactly
along the centerline of the jet exit. Third, because the exper-
iment was performed outside, the effects of wind could not be
totally eliminated. Consequently, such a small discrepancy in
the centerline alignment and wind effect could have resulted
in under-detecting the centerline hydrogen concentrations.
3.2. Dispersion of hydrogen jet
Fig. 4 shows (a) pressure distribution, (b) velocity profile, and
(c) temperature profile for the hydrogen jet for the case with
d ¼ 1.0 mm and P0 ¼ 200 bar. Fig. 4(a) shows that a significant
pressure drop occurs only around the hole. The region around
the hole can be divided into three zones e the hole inlet, the
inner region of the hole, and the exit of the hole. The hydrogen
flow experiences a large pressure drop in the inlet zone of the
hole; the strongest pressure drop of the three. The pressure
drops approximately 85 bar in this zone. In the second zone,
the pressure drop continues to meet the chocked conditions
just before the flow exits the hole. At the choking point, the
pressure is 85.0 bar, 20.3 bar less than the isentropic flow
experiences because of the viscosity. The large pressure drop
is completed in the exit zone by an abrupt expansion process,
and its value is almost the same as the pressure drop inside
the hole.
The flow inside the source reservoir remains almost static
until it starts to accelerate near the inlet of the hole as
depicted in Fig. 4(b). The average velocity magnitude of the
pressure inlet boundary of the reservoir is only approximately
0.05m/s but the flow is accelerated up to 200m/s at the inlet of
the hole. The hydrogen flow continues to be accelerated after
passing through the inlet of the hole. Then, the velocity
magnitude reaches sonic velocity just before the flow leaves
the hole and the flow is chocked around the location of 0.95L.
When the high pressure flow is exposed to the ambient air, it
experiences abrupt expansion. This expansion accompanies
a large decrease in the flow density so that flow accelerates
once more. The flow has a maximum velocity magnitude at
a distance of 10d from the hole, and it accelerates up to aMach
number of M ¼ 5.7 at the end of the expansion.
The quick expansion of the flow ends with the normal
shock. In Fig. 4(c), the normal shock is equal to the highly
Page 5
(a) P0 =100 bar (b) P0 =200bar
(c) P0 =300 bar (d) P0 =400bar
Distance(m)
HydrogenConcentration
1 2 3 4 5 6 7 8 9 1010-3
10-2
10-1
100
d=0.5mm
d=0.7mm
d=1.0mm
d=0.5mm
d=0.7mm
d=1.0mm
Distance(m)
HydrogenConcentration
1 2 3 4 5 6 7 8 9 1010-3
10-2
10-1
100
d=0.5mm
d=0.7mm
d=1.0mm
d=0.5mm
d=0.7mm
d=1.0mm
Distance(m)
HydrogenConcentration
1 2 3 4 5 6 7 8 9 1010-3
10-2
10-1
100
d=0.5mm
d=0.7mm
d=1.0mm
d=0.5mm
d=0.7mm
d=1.0mm
Distance(m)
HydrogenConcentration
1 2 3 4 5 6 7 8 9 1010-3
10-2
10-1
100
d=0.5mm
d=0.7mm
d=1.0mm
d=0.5mm
d=0.7mm
Fig. 3 e Comparison between experiment and prediction. (a) P0[ 100 bar, (b) P0[ 200 bar, (c) P0[ 300 bar and (d) P0[ 400 bar.
i n t e r n a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 2 3507
clustered contour lines of temperature. The normal shock is
located approximately 10d from the hole. The temperature,
density, and pressure of the flow are drastically lowered by the
expansion process, whereas the flow has hypersonic velocity.
The flow with a lowered density and hypersonic velocity
recognizes the ambient air as a strong non-moving body and
a normal shock is formed. After experiencing the normal
shock, the flow recovers and the temperature, density, and
pressure rise to that of the ambient air.
The temperature of the hydrogen is kept at 293 K in almost
the entire reservoir. The temperature of hydrogen begins to
change after the flow enters the hole. Hydrogen is heated by
viscous work up to 370 K inside the thermal boundary layer,
which is formed near the wall with the hole. However, the
temperature of the flow outside the thermal boundary layer is
continuously decreased by the acceleration of the fluid flow.
The average temperature of flow at the chocking point is
approximately 245 K, which is slightly larger than the
temperature of the isentropic flow (¼243 K). The temperature
is decreased to 208 K at the exit of the hole. After hydrogen is
emitted from the hole, it experiences abrupt expansion, as
discussed already. The temperature is decreased down to 60 K
by this expansion process. This is the lowest temperature
observed in the flow and soon recovers to the ambient air
temperature through the normal shock.
Here, the dilution length of a specific hydrogen mole frac-
tion is introduced and is defined as the distance from the hole
to the point of the hydrogen mole fraction along the jet
centerline. In this study, the variables L1LFL, L1/2LFL, and L1/4LFLwill be used for three typical dilution lengths. The variable
1LFL denotes the lean flammability limit which is 0.04,
expressed in mole fraction. The variables 1/2LFL and 1/4LFL
are 0.02 and 0.01, expressed in mole fraction. As seen in Fig. 5,
the dilution length of a specific hydrogen mole fraction is the
longest distance from the hole to the point of a specific
hydrogen mole fraction. Fig. 5 is the 2-D contour plot of the
hydrogen mole fraction for d ¼ 0.5 mm. The incremental step
for the contour plot is 0.01 and the outmost contour line has
Page 6
(a) Pressure
(b) Velocity
(c) Temperature
2.31E51.97E71.14E7
9.46E6
1300 m/s
337K
300K
300K
370K60K
Fig. 4 e Computational results for d [ 1.0 mm and
P0 [ 200 bar.
i n t e rn a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 23508
the value of 0.01. The criteria of setting the fictitious wall
boundary are determined based on these contour results. The
diameter of the fictitious wall has at least two times larger
than maximum diameter of 0.01 contour line.
(a) P0=100
(b) P0=200
(c) P0=300
(d) P0=400
0.010.04 0.02
0.04 0.02
0.040.02
0.040.02
0 1 2 3 4 5
Fig. 5 e Hydrogen concentration
The dilution lengths for 1LFL, 1/2LFL, and 1/4LFL are plotted
in Fig. 6. In the case of d ¼ 1.0 mm, the data for 300 bar and
400 bar are not available because the jet lengths for 1/4LFL
exceed the domain of the experiment and the numerical
simulation. Both the experiment and the simulation give well
matched results for L1LFL and L1/2LFL, which is correlated with
the reasoning explained in Fig. 3. L1LFL�>1=2LFL, dilution length
from 1LFL to 1/2LFL, is almost equal toL1LFL, which well agreed
with the result of hyperbolic decay. Because a point of 1/4LFL
was far beyond the concurrency region where experiment
and simulation were in good agreement, the measured and
predicted L1/4LFL showed large deviation from each other.
3.3. Mass flux of released jet
When the reciprocal of hydrogen concentration is taken from
Eq. (4), the following line equation is obtained:
1XH2
¼
�rH2
rair
�12
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiCD
�2
gþ 1
�ðgþ1Þ=2ðg�1Þs ffiffiffiffiffiffiffiffiffiffiffiffiffiffi
Po=Pair
p�zdþ z0
d
�¼ A
�zdþ z0
d
�(21)
Fig. 7 is the reciprocal plot of the measured data with
respect to z/d for P0 ¼ 300 bar. As discussed above, the data of
the 1st, 2nd, and 3rd probes are well matched with the
computational results. It can be said that the data of 1st, 2nd,
and 3rd probes were cross verified by the experiment and the
prediction. Then, only the data of 1st, 2nd, and 3rd probes
were used in plotting the figures. The line in each graph is the
best fitted line for the measurement data. Each graph again
shows the well matched behavior between the measurement
and the prediction. The hyperbolic decay characteristics are
bar
bar
bar
bar
0.01
0.01
0.01
6 7 8 9 10
m
contours for d [ 0.5 mm.
Page 7
5 mm(a) d=0. (b) d=0.7 mm (c) (c) d=1.0 mm
Pressure(bar)
Dilutionlength(m)
100 200 300 4000.0
2.0
4.0
6.0
8.0
10.0
12.0
14.0
16.0
Pressure(bar)
Dilutionlength(m)
100 200 300 4000.0
2.0
4.0
6.0
8.0
10.0
12.0
14.0
16.0
Pressure(bar)
Dilutionlength(m)
100 200 300 4000.0
2.0
4.0
6.0
8.0
10.0
12.0
14.0
16.0
Fig. 6 e Dilution length for various hole diameters.
mm mm(a) d=0.5 (b) d=0.7
(c) d=1.0 mm
z/d
1/XH2
0 2000 4000 6000 8000 100000
20
40
60
80
100
120Experiment
Prediction(0.5mm)
z/d
1/XH2
0 2000 4000 6000 8000 100000
20
40
60
80
100
120Experiment
Prediction(0.7mm)
z/d
1/XH2
0 2000 4000 6000 8000 100000
20
40
60
80
100
120Experiment
Prediction(1.0mm)
Fig. 7 e Reciprocal of hydrogen concentra for three holes with P0 [ 300 bar.
i n t e r n a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 2 3509
Page 8
i n t e rn a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 23510
valid up to relatively large axial distances. The z/d of the 3rd
probe for the three holes are 5,000, 7,000, and 10,000 in order of
hole diameter.
Eq. (21) tells that the coefficient A of the isentropic flow is
solely dependent on the source pressure. However, the gradi-
ents of the three lines, A, are slightly different from another in
Fig. 7. The same plots for various source pressures show rela-
tively large differences in the gradients, as shown in Fig. 8, in
which each dashed line is obtained with the isentropic flow
assumption. These two figures reveal that the coefficient A of
the actual flow is also dependent on L, d, and P0. However, the
dependence on L and d is relatively small compared to that of
source pressure. All the coefficients e both measured and
predicted e are listed in Table 1.
The last column in Table 1 is for the coefficient A of the
isentropic flow. The last column of each case is approximately
25% less than the others. This is due to viscous work existing
in the actual flow. Although the concentration of the numer-
ical prediction fulfills the hyperbolic decay rule as well as that
of the measurement, the coefficient A of the numerical
(a) P =100 bar
(c) P =300 bar
z /d
1/X
0 2 0 0 0 4 0 0 0 6 0 0 0 8 0 0 0 1 0 0 0 00
2 0
4 0
6 0
8 0
1 0 0
1 2 0
E xp e rim e n t
C F D ca lcu la tio n
Ise n tro p ic
z /d
1/X
0 2 0 0 0 4 0 0 0 6 0 0 0 8 0 0 0 1 0 0 0 00
2 0
4 0
6 0
8 0
1 0 0
1 2 0
E xp e rim e n t
C F D ca lcu la tio n
Ise n tro p ic
Fig. 8 e Reciprocal of hydrogen concentration for
prediction shows some deviation from that of the isentropic
flowmodel. Because the coefficientA is inversely proportional
to the mass flux (the strength of the jet), this says that the
mass flux of the actual flow is less than that of the isentropic
flow. This is because of dissipation work, which the flow
experiences during passing through a hole. Fig. 4(c) clearly
shows the temperature build-up near the wall of a hole by this
dissipation work.
Two more cases of L, 10 mm and 20 mm, were tested to
investigate the effect of dissipation work on the jet strength
and mass fluxes. When highly pressurized hydrogen flows
through a pipe or a hose between a storage tank and a fueling
tip, its thickness is most likely less than 30 mm because of its
small inner diameter. Then, a thickness less than 30 mm is
more meaningful to take into account. Fig. 9 shows the mass
fluxes for d ¼ 0.7 mm. In case of L ¼ 30 mm, the mass fluxes of
P0 ¼ 100 bar, 200 bar, 300 bar, 400 bar are reduced to 84.1%,
84.8%, 85.3%, 85.4% of those of isentropic flow, respectively.
It is natural that the longer the hole length is, the larger the
reduction is.
(b) P =200 bar
(d) P =400 bar
z /d
1/X
0 2 0 0 0 4 0 0 0 6 0 0 0 8 0 0 0 1 0 0 0 00
2 0
4 0
6 0
8 0
1 0 0
1 2 0
E xp e rim e n t
C F D ca lcu la tio n
Ise n tro p ic
z /d
1/X
0 2 0 0 0 4 0 0 0 6 0 0 0 8 0 0 0 1 0 0 0 00
2 0
4 0
6 0
8 0
1 0 0
1 2 0
E xp e rim e n t
C F D ca lcu la tio n
Ise n tro p ic
various source pressures with d [ 0.7 mm.
Page 9
Table 1e Coefficient A (measurement, prediction),310L3.
P0(bar)
d ¼ 0.5 mm d ¼ 0.7 mm d ¼ 1.0 mm Isentropic
100 (11.34, 10.354) (10.069, 10.320) (10.778, 11.266) (e, 7.781)
200 (7.804, 7.379) (6.965, 7.380) (7.867, 8.257) (e, 5.502)
300 (6.880, 6.113) (5.796, 6.100) (6.155, 6.378) (e, 4.492)
400 (6.050, 5.235) (5.285, 5.266) (e, 5.617) (e, 3.891)
L/dReductionRatio
0 10 20 30 40 50 60 700
0.05
0.1
0.15
0.2
0.25
0.3
0.35
0.4
P0=100bar
P0=200bar
P0=300bar
P0=400bar
Fitted line
Fig. 10 e Reduction ratio RR.
i n t e r n a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 2 3511
At this point, the reduction ratio is introduced to investi-
gate the strength of the mass flux reduction of the actual flow
compared to that of the isentropic flow. The reduction ratio
(RR) is defined as:
RR ¼ 1� _mðmass flux of actual flowÞ_msðmass flux of isentropic flowÞ : (22)
As is expected, the larger the L/d ratio is, the larger the
reduction ratio is. Interestingly, the reduction ratio is not as
sensitive to the source pressure. The sensitivity to the source
pressure is almost zero in case of L/d¼ 10.When the reduction
ratio is plotted with respect to L/d as shown in Fig. 10, it is
almost linearly dependent on L/d:
RR
�Ld
�yaþ b
Ld: (23)
When Eq. (22) is combinedwith Eq. (3) and Eq. (23), themass
flux can be determined with the following equation:
_m ¼�1� RR
�Ld
��� _msðT0;P0Þ
¼ CDP0ffiffiffiffiffiffiffiffiRT0
p�
2gþ 1
� 1g�1
ffiffiffiffiffiffiffiffiffiffiffiffi2g
gþ 1
s �1� a� b
Ld
�(24)
P re ssu re (b a r)
MassFlux(kg/m
s)
1 0 0 2 0 0 3 0 0 4 0 00
5 0 0 0
1 0 0 0 0
1 5 0 0 0
2 0 0 0 0
2 5 0 0 0
Is e n tro p ic
L = 2 0 m m
L = 1 0 m m
L = 3 0 m m
Fig. 9 e Mass fluxes for d [ 0.7 mm.
The variables a and b of the fitted line are 4.707 � 10�2 and
2.361 � 10�3, respectively. The maximum error of the fitted
line is 1.57% at an L/d ¼ 60, and the average error is 0.5%.
4. Conclusions
A 2D axisymmetric simulation was performed to investigate
the characteristics of a hydrogen jet formed by high pressure
release through a small hole. The calculation was performed
for the following experimental cases; a specific hole length
(L ¼ 30 mm), three hole sizes (d ¼ 0.5 mm, 0.77 mm and
1.0 mm) and four chamber pressures (P0 ¼ 100 bar, 200 bar,
300 bar, and 400 bar). In addition to the experimental cases,
calculations were performed for two more hole lengths to
analyze the mass flux characteristics through a small hole.
This study introduced an air intake inlet and a fictitious
wall to ensure the accuracy and stability of the numerical
calculation. This approach gave a good agreement with the
experimental data until the 3rd probe. The measured and
predicted concentration fulfilled the hyperbolic decay char-
acteristics in this concurrency region. However, the
measurement and prediction showed large deviation at two
farthest probe points from the release hole because of
centerline alignment inaccuracy of probes and wind effect.
The dilution lengths of 1LFL (Lean Flammable Limit, 0.04)
and 1/2LFL were obtained for three hole diameters and four
release pressures The dilution length of 1/2LFL was almost
two times longer than that of 1LFL, whichwell agreedwith the
result of hyperbolic decay curve. Because a point of 1/4LFL
was far beyond the concurrency region, the measured and
predicted dilution lengths of 1/4LFL showed large deviation
from each other.
Page 10
i n t e rn a t i o n a l j o u r n a l o f h y d r o g e n en e r g y 3 8 ( 2 0 1 3 ) 3 5 0 3e3 5 1 23512
Although actual hydrogen jet flow well fulfilled the
hyperbolic decay characteristics as described in the Birch’s
work [2], its mass flux showed a large deviation from the
isentropic estimation of mass flux. This is due to dissipation
work which pure hydrogen flow experiences during passing
through the hole. The mass reduction ratio, defined as the
ratio between actual mass flux and isentropic estimation, was
found to be almost linearly dependent on L/d for the range of
source pressures and hole lengths of this study. Then, the
mass flux of the actual hydrogen jet flow can be calculated
with the linear relation of Eq. (24) within the maximum error
of 1.57%.
Acknowledgments
This research was a part of the project titled “Development of
Technology for CO2 Marine Geological Storage” funded by the
Ministry of Land, Transport and Maritime Affairs, Korea.
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