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OPEN Cylindrical orifice testing in laminar

flow with the orifice diameter ratio
β = 0.5
Anna Golijanek‑Jędrzejczyk 1* & Andrzej Mrowiec 2

The paper presents the results of an experimental study of a cylindrical orifice with the orifice diameter
ratio β = 0.5 and the flow opening length-to-diameter ratio L/d = 1, with hydraulic oil flowing in the
DN50 measuring channel. The measurements of the values characterising the oil flow were made in
the laminar flow regime, for the Reynolds numbers ranging between Re = 100 to 950. Based on the
experimental tests, standard flow characteristics were created for four kinematic viscosity values in
the range of 13.4–33.3 cSt, for which the average value of the discharge coefficient C in the tested flow
rate range of qv < 0.5 ­dm3/s was determined.

Abbreviations
D Pipe diameter [m]
d Orifice diameter [m]
L Length of the flow hole in the orifice [m]
T Fluid (oil) temperature [°C]
a Slope [–]
Re Reynolds number [–]
b Intercept ­[dm3/s]
qv Volumetric flow ­[dm3/s]
C Discharge coefficient [–]
ε Expansion coefficient, for oil ε = 1
Δp Difference pressure [Pa]
α Proportionality coefficient ­[m4/(kg·m)0.5]
β Orifice diameter ratio [–]
γ Power coefficient [–]
ρ Fluid density [kg/m3]
ν Kinematic viscosity [cSt = ­mm2/s]
u(a) Standard uncertainty of determination of parameter a
u(b) Standard uncertainty of determination of parameter b

The volumetric flow rate is the amount of fluid flowing through the cross-section of a hydraulic flow channel
per unit of time. The parameters affecting the physical properties of the fluid (including viscosity and density)
are pressure and temperature. They are measured directly in the flow channel, which allows for determining the
viscosity and density of the flowing fl ­ uid1.
Based on both the authors’ experience from simulation and experimental studies and the available literature
on the s­ ubject2–4, the centric orifice method is the most popular and versatile method for measuring fluid flow,
which has been described and standardised in d ­ etail5. It is estimated to be the most widely used method in indus-
trial measurement (it has captured more than 40% of the m ­ arket2) in industries such as oil and gas, chemical,
nuclear and power generation. For example, in China’s oil and gas industry, flowmeters of this type account for
about 95% of all flowmeters used in industrial i­ nstallations2.
In this method, the flow rate is proportional to the root of the measured static pressure difference upstream
and downstream of the orifice.
The standard orifice centric flowmeter is cheap to manufacture, inexpensive to operate and reliable for meas-
uring the flow rate of flowing fluid in industrial a­ pplications6,7.

1
Faculty of Electrical and Control Engineering, Gdańsk University of Technology, 80‑233 Gdansk,
Poland. 2Polytechnic Faculty, Calisia University, 62‑800 Kalisz, Poland. *email: anna.golijanek-jedrzejczyk@
pg.edu.pl

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It is estimated that among all fluid flow measurements, orifice measurements still account for about 50%.
Standard ISA orifices with sharp edges at the inlet have already been tested and standardised. For large Reynolds
numbers (Re > 10,000) and the pipeline diameter D ≥ 50 mm, the value of the discharge coefficient C is practically
constant and is usually presented in the form of tables (standard) or from the empirical Reader–Harris/Gallagher
formula recommended by the s­ tandard5.
The discharge coefficient C is a parameter characterising the ratio of the actual value of the flow rate of a
liquid flowing through a measuring orifice to the corresponding value calculated from a theoretical flow model.
The numerical value of C is related to the shape of the orifice (its type) but also depends on the parameters of the
orifice, the fluid flow conditions, the measuring instruments and the hydraulic installation.
In the range of Reynolds numbers smaller than 10,000, standard sharp-edged centric orifices are charac-
terised by a significant variation of the discharge coefficient C as a function of Reynolds number, thus posing
significant metrological problems and cannot be used in this case. In Ref.8,9, the authors attempted to determine
the discharge coefficient C for low Reynolds number values, showing its non-linearity depending on the orifice
diameter ratio β in this range of numbers Re.
This has motivated the researchers to develop new non-standardised orifices which, although requiring indi-
vidual calibration, will be characterised by a constant discharge coefficient C in the viscous fluid flow r­ ange10–12.
The oil viscosity, which changes with temperature, leads to relatively low Reynolds numbers characteristic of
laminar and developing turbulent fl ­ ows13,14.
An orifice with a conical inlet, for which the discharge coefficient remains constant in low Reynolds numbers
(Re > 80), is handy for industrial flow rate measurements of viscous fl ­ uids15,16.
Another orifice allowing flow measurements at low Reynolds numbers (Re > 250) is the quadrant orifice, in
which the radius of the rounding is related to the orifice diameter ratio β17.
Based on the symmetrical orifice with sharp-edges encountered in metrology (the so-called boundary orifice),
which allows flow measurement in both directions, it was decided to use its thickened version as a cylindrical
orifice for the study.
Despite its use in measurement systems, there are still a small number of publications in the scientific
­literature18 on cylindrical nozzles (elongated sharp-edged cylindrical orifices). The results presented therein
mainly relate to turbulent flows, where only gas or water is used as the medium. That is why another orifice solu-
tion has been developed that allows the measurement of fluid flow rate at low Reynolds numbers, in the area of
laminar and developing turbulent flows.
One example application is in the pharmaceutical industry, where the effect of the size of the flow of diluents
through cylindrical orifices (in a tabletting matrix) as a function of their length and diameter was investigated
using modelling dependent on the adopted calculation a­ lgorithm19.
In the l­ iterature20, the results of numerical tests can be found for low Reynolds numbers in a cylindrical orifice,
in which the flow opening length-to-diameter ratio is L/d ≤ 15. Further experimental results have confirmed the
results of the simulation tests.
However, for fluid flow measurement, the first cylindrical orifices were developed in 1938 for a pipeline with
an internal diameter of D = 40 mm and an orifice diameter ratio β of 0.1–0.721. Experimental flow tests were
carried out for them, showing the distribution of the discharge coefficient characteristics as a function of the
Reynolds number 270 > Re > 550,000.
On the other hand, p ­ ublication22 presents the range of applicability of the cylindrical orifice and flow t­ ests23
with a variation of the orifice diameter ratio β = 0.3–0.8 in pipelines with internal diameters D equal to 15, 25,
32 and 40 mm for Reynolds numbers Re > 1500.
Thus, in ­paper18, the author, based on his own research and that of other ­researchers19,21, presented empirical
formulae for calculating the discharge coefficient C at different values of Reynolds number (Re > 500), depending
on the adopted value of the orifice diameter ratio β in the range 0.1–0.7.
The ­paper24 estimated discharge coefficient magnitudes from numerical tests for air and water flowing through
thin and thick (cylindrical) orifices with sharp edges.
Meanwhile, in the ­paper25, the tests performed for cylindrical orifices with small flow orifice diameters and
the L/d ratio in the range of 1–50 have shown that the discharge coefficient C is correlated with the Reynolds
number values.
The authors ­in26 compared the results of the discharge coefficient obtained from experimental tests and
CFD numerical simulations for cylindrical damping holes in hydraulic oil dampers. They presented an analysis
allowing the theoretical calculation of this coefficient to be improved and refined by about 17% in flow-damping
systems.
In Ref.27, based on numerical and experimental studies of orifices with the ratio L/d = 2, it was demonstrated
that additional corrections taking into account the occurrence of cavitation should be introduced to the theoreti-
cally determined discharge coefficient C in a high-pressure flow to achieve greater accuracy of this parameter.
However, it is more common in the literature to find publications analysing the issue of cavitation supported
by experimental studies with the fluid flowing in the cylindrical orifice area for low or high-pressure ­values28,29.
Another example of this type of research can be found in experimental s­ tudies30, which evaluated the effect
of the inlet geometry of elongated orifices (sharp-edged and chamfered) of rocket engine injectors in fluid flow.
The ­paper30 assessed the impact of orifice diameter and thickness on the formation of cavitation phenomena in
turbulent flow, improving liquid fuel atomisation in the combustion chamber.
To summarise, several older articles (more than 40 years old) deal with studies similar to those carried out
by the authors. However, it should be mentioned that, first of all, there are only a few of them, and, secondly,
there are still no results concerning flow tests carried out in an oil installation with a pipe diameter of ø 50. The
published ­research21,23 was performed for installations with a water medium and only up to a maximum pipeline
diameter of ø 40.

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The experimental investigations described in this paper aimed to determine the discharge coefficient for a
selected cylindrical orifice with the orifice diameter ratio β = 0.5 and the flow opening length-to-diameter ratio
L/d = 1 in pipeline DN50. The measurements were carried out in the laminar range of the hydraulic oil flow
(100 < Re < 1000) for different viscosity values determining the flow characteristics. As the available literature
lacks metrological analyses and experimental tests for flows of fluids with a viscosity higher than that of water,
the presented test results will supplement this knowledge, thus confirming the novelty of the conducted tests.

Research object
When designing the orifice for testing, it was assumed that the oil Hydrol L-HL 22 with an average density of
ρ = 864 kg/m3 flows through the pipeline with an inner diameter of ø 50 mm. This oil will flow with the maximum
flow rate qv ≤ 0.5 ­dm3/s, and the pressure drop Δp at the orifice will not exceed 1.2 kPa.
Based on the above defined criteria, a cylindrical orifice has been designed which, according to the literature,
can be used to measure viscous fluid flows at low Reynolds n ­ umbers18. For the designed orifice with the flow
section length of 25 mm, the orifice diameter ratio β was assumed to be equal to 0.5.
Figure 1a shows the longitudinal cross-section of the cylindrical orifice with geometrical dimensions allowing
its fabrication and the assumed roughness values on its critical surfaces.
A prototype of the above orifice was made of stainless steel, as shown in Fig. 1b.

Experimental stand
The flow rate measurements intended to determine qve = f(Δp) characteristics for different values of oil kinematic
viscosity were conducted on a modified test stand (HYDAC hydraulic power pack).
The oil flow rate in the hydraulic system was changed smoothly using an inverter controlling the speed of
the electric motor within the range of 435–2750 rpm. The motor (M) was connected via a claw coupling to an
internal gear pump with a maximum capacity of qv = 0.5 ­dm3/s at nominal speed.
Figure 2 shows the schematic of the hydraulic measuring system. As can be seen, the oil first flows through
the measuring system with the cylindrical orifice under test and then enters the oval flowmeter NC4.
In the hydraulic system shown, the NC4 flowmeter was adopted as the standard for measuring the flow rate
of the flowing oil. Changes in the kinematic viscosity of the oil were controlled by changing its temperature.
­ m3 was the base of the entire hydraulic system
A massive steel oil tank with a capacity of approximately 250 d
of the test stand. A UTU-2 water ultra-thermostat located on the test bench was used to stabilise the set tem-
perature of the flowing oil. It was connected to a tubular heat exchanger, made in the form of a copper heating
coil immersed in the oil filling the tank.
The oil temperature in the tank was measured continuously using a Pt100 resistance temperature sensor in a
steel case with a terminal head connected to an AT-2-type temperature transmitter. The temperature transmitter
was programmed for a measuring range of 0–80 °C, with a standard output signal of 4–20 mA DC.
As the reference standard for measuring the oil flow rate, an oval wheel flowmeter type NC4 was used.
This flowmeter has the limiting error of the measured value equal to Δqv ≤ 0.25% in the measuring range of
qv = 0.003–0.83 ­dm3/s. The differential pressure Δp arising at the orifice was measured in a point-differential
manner using a differential pressure transmitter type APR-2000/ALW. Its limiting error Δp ≤ 0.15% was pro-
grammed for the differential pressure measurement range Δp = 0–1.2 kPa, with the standard output current
signal of 4–20 mA.

Figure 1.  The cylindrical orifice with orifice diameter ratio β = 0.5: (a) geometrical dimensions, (b) view.

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Figure 2.  Schematic of the hydraulic measuring system.

Results of measurements
The following parameters were recorded during the experimental tests: the volumetric rate qv of the hydraulic
oil flow through the orifice, the pressure difference Δp across the orifice, and the fluid temperature T.
Each averaged result of a given parameter was calculated from 300 individual results of this parameter,
measured with the sampling step of 3 s.
Based on the equation:

4 · qv · 1 − β 4
C=  (1)
2·�p
π · ε · d2 · ρ

the discharge coefficient C of the tested cylindrical orifice was calculated for each sample, taking into account
the average density of the flowing oil at the test temperature.
The results of the performed experimental measurements and calculations are given in Table 1.
The above results made the basis for creating flow characteristics qve = f(Δp) for the cylindrical orifice tested.
The obtained characteristics are shown in Fig. 3, along with the base points used for their creation.
The two extreme curves of the flow characteristics for kinematic viscosities of 13.37 m ­ m2/s and 33.25 m ­ m2/s
within the flow rate range below qv < 0.5 ­dm3/s are marked as continuous trend lines, while the two other point
trend lines situated between them characterize the intermediate kinematic viscosities for which the measure-
ments were also made, as shown in Table 2.
The potentiated trend lines shown in Fig. 3 can be described algebraically by the general relation:
qve = α · �pγ (2)
Table 2 summaries the trendline parameters as a function of the averaged values of kinematic viscosity
of the flowing oil represented by measurement points (qv, Δp), together with the corresponding values of the
determination coefficient R2.
It can be seen from the trendline parameter values shown in Table 2 that the parameters are strongly depend-
ent on the viscosity of the hydraulic oil flowing in the measurement system.
Equation (2) shows that as the kinematic viscosity value increases, the value of the proportionality coefficient
α decreases and the value of the power exponent γ increases. The value of the power exponent differs significantly
from the theoretical value of γ = 0.5. It was, therefore, decided to fit another function with a power exponent
γ = 0.5 (theoretical value)5 with the smallest possible error to the flow characteristic determined by the trend line
with a kinematic viscosity of 13.37 cSt, (the power exponent is γ = 0.5323).
These flow values for this function were calculated using the iterative method by adapting a theoretical power
function with exponent γ = 0.5. For this new function, the proportionality coefficient has the value α = 0.626.
Between the experimental curve (α = 0.6462; γ = 0.5323) and the determined new theoretical power function
(α = 0.626; γ = 0.5), the fit error does not exceed 0.9% at the measured backpressure at the orifice in the range of
Δp = 0.1–0.6 kPa.
Based on the power function determined in this way, the theoretical values of the mass flow rate qvo as a
function of Δp were calculated, for which the theoretical value of the discharge coefficient was determined from
Eq. (1), where C is 0.8036.
Using the results obtained in experimental tests with flowing oil for four different kinematic viscosities
(Table 1), the discharge coefficient C values will be calculated. Its distribution as a function of Reynolds numbers
is shown in Fig. 4. For each point creating the graph C = f(Re) in Fig. 4, a tolerance area expressed by an error
bar of 2% was added. This value was estimated based on the literature on standardised and non-standardised
­holes31: with a conical and quadrant inlet and based on our own research on determining the uncertainty of the
flow coefficient for a multi-hole32.
It can be observed in the plot shown in Fig. 4 that starting from Re = 550, the curved fit line to the discharge
coefficient values calculated from the experiment begins to straighten, which makes it more flat.

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Tśr = 48.89 [°C] Tśr = 44.35 [°C]

νśr = 13.37 ­[mm2/s = cSt] νśr = 15.27 ­[mm2/s = cSt]
ρśr = 846.2 [kg/m3] ρśr = 849.3 [kg/m3]
qv Δp Re C qv Δp Re C
[dm3/s] [kPa] [—] [—] [dm3/s] [kPa] [—] [—]
0.1695 0.0824 323.2 0.7576 0.1698 0.0849 283.5 0.7496
0.2208 0.1327 419.2 0.7783 0.2206 0.1362 366.2 0.7688
0.2720 0.1944 518.0 0.7918 0.2725 0.1995 453.1 0.7846
0.3060 0.2426 583.0 0.7973 0.3054 0.2458 510.0 0.7922
0.3397 0.2961 647.3 0.8014 0.3390 0.2992 566.4 0.7970
0.3722 0.3527 709.8 0.8045 0.3734 0.3595 623.1 0.8008
0.4063 0.4182 775.0 0.8066 0.4076 0.4253 681.1 0.8037
0.4415 0.4923 840.6 0.8078 0.4408 0.4945 737.0 0.8061
0.4833 0.5896 922.6 0.8080 0.4832 0.5916 806.9 0.8080
Tśr = 35.10 [°C] Tśr = 25.11 [°C]
νśr = 21.00 ­[mm2/s = cSt] νśr = 33.25 ­[mm2/s = cSt]
ρśr = 855.6 [kg/m ]3
ρśr = 862.5 [kg/m3]
qv Δp Re C qv Δp Re C
[dm3/s] [kPa] [—] [—] [dm3/s] [kPa] [—] [—]
0.1715 0.0932 208.5 0.7251 0.1706 0.1043 121.5 0.6851
0.2212 0.1458 268.3 0.7478 0.2221 0.1611 173.6 0.7207
0.2715 0.2101 328.6 0.7645 0.2724 0.2320 200.5 0.7332
0.3064 0.2613 371.4 0.7736 0.3061 0.2852 229.1 0.7428
0.3403 0.3175 412.2 0.7795 0.3399 0.3424 260.2 0,7529
0.3731 0.3759 451.8 0.7854 0.3735 0.4043 294.5 0.7612
0.4082 0.4431 494.8 0,7916 0.4079 0.4722 329.2 0.7689
0.4426 0.5159 537.6 0.7954 0.4420 0.5467 366.0 0.7742
0.4835 0.6090 588.1 0.7997 0.4836 0.6415 412.4 0.7819

Table 1.  Experimental results.

Figure 3.  Flow characteristics qve = f(Δp) as a function of kinematic viscosity.

Kinematic viscosity α γ R2
13.37 cSt 0.6462 0.5323 0.9996
15.27 cSt 0.6462 0.5388 0.9997
21.00 cSt 0.6392 0.5516 0.9999
33.25 cSt 0.6257 0.5711 0.9999

Table 2.  Parameters of potentiated trend lines.

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Figure 4.  Distribution of discharge coefficient vs Reynolds number.

Discussion
From the literature analysis, a few publications present experimental studies to determine the discharge coef-
ficient C for measured elongated cylindrical orifices. In the published articles, experimental tests were carried
out in pipelines with a maximum diameter not exceeding ­DN4018,21,23 with a flowing water stream.
The verification of these orifices in water flow systems is made possible by tests from low Reynolds numbers
(Re approx. 1400), at which very low pressure drop values across the orifice occur, resulting in increased meas-
urement errors.
Therefore, to increase the accuracy of the measurements made at lower Reynolds number values, the authors
carried out experimental tests in a DN50 measuring channel with hydraulic oil flowing through, the viscosity of
which is several times that of water. This allowed a significant reduction in Reynolds number values at the same
orifice pressure accumulations (or flow rate values) as for water.
In a DN50 channel, an elongated cylindrical flow orifice with an orifice diameter ratio β = 0.5 and a length
(thickness) ratio to the flow orifice diameter L/d = 1 was tested. The Δp and qv results obtained from the experi-
ment were averaged over the measurement series. Based on these, the discharge coefficient C calculations were
made at low Reynolds number values (Re = 100–950), shown in Fig. 4 as dots with the bars of the adopted toler-
ance field of 2%.
The adopted tolerance field in the range of Reynolds numbers Re = 450–950 contains the value of the discharge
coefficient C = 0.8036, which was calculated from relation (1) using the theoretical (engineering) curve described
by a power function (2) for which the exponent of the power γ = 0.5 and the proportionality factor α = 0.626.
However, this calculated theoretical value of the discharge coefficient is 0.55% lower than the value reported
in the literature (C = 0.808) for an elongated cylindrical orifice with an orifice diameter ratio β = 0.5, but with a
larger ratio L/d = 2.12. The above value was determined in a DN 40 pipeline for flowing water at Reynolds number
Re ≥ ­140018,23. For the cylindrical orifice tested, a similar value for the discharge coefficient C was obtained for a
quadrant orifice with an orifice diameter ratio β = 0.5 (C = 0.802)31.
Figure 5 shows the flow characteristics as averaged experimental points for flowing hydraulic oil with a
kinematic viscosity of 13.37 cSt.

Figure 5.  Comparison of flow characteristics for a cylindrical orifice: experimental and engineering.

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The averaged measurement points of flow rate qv and differential pressure Δp through the test hole are plot-
ted against the expanded uncertainty bars of both these values (estimated from the type B uncertainty due to
imperfections in the measuring instruments used to measure these quantities).
The (engineering) flow characteristic was calculated for the theoretically determined discharge coefficient
C = 0.8036 and is shown as points connected by a solid line. It can be seen from the graph (Fig. 5) that this char-
acteristic is within the tolerance range limited by the expanded uncertainty bars of the two values (determined
from the Type B expanded uncertainty of the measurement apparatus used).

Conclusions
The paper presents the results of experimental tests for hydraulic oil flowing in a DN50 flow channel through a
cylindrical orifice with the diameter ratio of β = 0.5 and the flow opening length (thickness)-to-diameter ratio
L/d = 1.
It can be concluded from the presented results of the tests performed on a cylindrical orifice (Fig. 1) for
corner tappings that in the tested range of Reynolds numbers (Re = 450–950), a constant value of the discharge
coefficient C equal to 0.8036 can be assumed, with a theoretical exponent γ = 0.5 and a kinematic viscosity in
the range of 13–15 ­mm2/s (cSt). In this range of Re numbers, this value is within the accepted 2% tolerance for
the C = f(Re) characteristic determined from experimental tests (Table 1).
In industrial practice, (oil) hydraulic systems operate at 40–50 °C. Under such oil flow conditions, an orifice
flow meter with a cylindrical orifice with the orifice diameter ratio β = 0.5 can be used to monitor system opera-
tion—as a cheap and reliable device.
The experimental studies allowed the Reynolds number limit Remin to be reduced from a value of 1­ 40018,23 to
a value of 450 (with an assumed tolerance of 2%), from which a cylindrical orifice with the orifice diameter ratio
β = 0.5 can already be used to measure the flow rate.
Further experimental studies are planned for laminar flow (Re > 1000), including the developing turbulent
flow.

Data availability
The datasets used during the current study are available from the corresponding author on reasonable request.

Received: 7 March 2023; Accepted: 10 September 2023

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Acknowledgements
The research was financed by the National Science Center of the Republic of Poland under the ‘MINIATURA 5’
programme. Project number 2021/05/X/ST8/00151, awarded amount PLN 9,710.

Author contributions
Conceptualization, A.M; data curation, A.G.-J.; formal analysis, A.G.-J and A.M..; investigation, A.G.-J. and A.M.;
methodology, A.G.-J. and A.M.; project administration, A.G.-J.; software, A.M.; supervision, A.G.-J. and A.M.;
validation, A.G.-J. and A.M.; visualization, A.G.-J. and A.M.; writing—original draft, A.M.; writing—review
and editing, A.G.-J. and A.M..; validation, A.G.-J. and A.M. All authors have read and agreed to the published
version of the manuscript.

Competing interests
The authors declare no competing interests.

Additional information
Correspondence and requests for materials should be addressed to A.G.-J.
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