A Novel Passive Method to Control the Swirling Flow with Vortex Rope from the Conical Di ﬀ user of Hydraulic Turbines with Fixed Blades

: In this paper, we introduce a novel passive control method to mitigate the unsteadiness e ﬀ ects associated to the swirling ﬂows with self-induced instabilities. The control method involves a progressive throttling cross-section ﬂow at the outlet of the conical di ﬀ user. It adjusts the cross-section area with a diaphragm while maintaining all positions of the circular shape centered on the axis. It improves the pressure recovery on the cone wall while the pressure ﬂuctuations associated with the self-induced instability are mitigated as it adjusts the cross-section area. It can adjust the diaphragm in correlation with the operating conditions of the turbine. We investigated the passive control method on a swirl generator, which provides a similar ﬂow as a hydraulic turbine operated at a partial discharge. The plunging and rotating components are discriminated using the pressure ﬂuctuation on the cone wall to provide a clear view of the e ﬀ ects induced by this passive control method. As a result, the novel proof of concept examined in this paper o ﬀ ers valuable beneﬁts as it fulﬁls a good balance between the dynamical behavior and the hydraulic losses.


Introduction
Nowadays hydropower is perceived as a mature technology but it has to face to new requirements more challenging than ever: the stochastic nature of renewable energy sources (wind, solar), irregular market requirements for energy, climate changes, constraints and environmental concerns [1]. Therefore, the hydraulic turbines have to operate over a wide range [2,3] under a fast change of the parameters to compensate the fluctuating part delivered in the electrical grid by the renewable energies. Several times, these requirements implied transient phenomena (e.g., load acceptance, load rejection, start-stop, emergency shutdown, spin no load, total load rejection) in operation [4][5][6][7]. Along the upstream passage of the hydraulic turbine, the potential energy of the water available in the upper tank is converted into kinetic energy. Then, this hydraulic energy available at the runner inlet is converted by the mechanical energy at the turbine shaft. The flow energy which is not converted by the runner is ingested by the drat tube of the hydraulic turbines [8]. A fraction of this residual energy is converted back into potential energy along to the draft tube [9].
Over 50-75% of this residual energy is recovered in the first part of the draft tube, which is called the discharge cone. Therefore, the hydraulic efficiency of the medium-to-low head turbines is significantly affected by performing the draft tube on a wide range operation [10].

Swirling Flow Apparatus and Experimental Setup
The experimental investigations are performed on the test rig available at Politehnica University Timisoara. The hydraulic circuit presented in Figure 2 contains the swirl apparatus with two parts: (i) the swirl generator and (ii) the convergent-divergent test section. The swirl generator delivers a swirling flow configuration similar to one determined in a Francis runner operated at 70% partial discharge [31]. At this regime, the vortex rope generates the largest pressure fluctuations.

Swirling Flow Apparatus and Experimental Setup
The experimental investigations are performed on the test rig available at Politehnica University Timisoara. The hydraulic circuit presented in Figure 2 contains the swirl apparatus with two parts: (i) the swirl generator and (ii) the convergent-divergent test section. The swirl generator delivers a swirling flow configuration similar to one determined in a Francis runner operated at 70% partial discharge [31]. At this regime, the vortex rope generates the largest pressure fluctuations.

Swirling Flow Apparatus and Experimental Setup
The experimental investigations are performed on the test rig available at Politehnica University Timisoara. The hydraulic circuit presented in Figure 2 contains the swirl apparatus with two parts: (i) the swirl generator and (ii) the convergent-divergent test section. The swirl generator delivers a swirling flow configuration similar to one determined in a Francis runner operated at 70% partial discharge [31]. At this regime, the vortex rope generates the largest pressure fluctuations.  Several details about the swirl generator are available in two benchmark cases: (i) the Timisoara Swirl Generator test case available at the Turbomachinery Special Interest Group (TSIG) [30]; and (ii) the AC6-14 test case included in the ERCOFTAC database [32]. The swirl generator has an upstream annular section with stationary and rotating blades for generating swirling flow ( Figure 2). It has three components: the ogive, the guide vanes, and the free runner. The ogive with four leaned struts has the role to sustain the swirl generator. The main part of the swirl generator is the free runner. Its main purpose is to redistribute the total pressure at the entrance of the cone. The free runner induces an excess of energy near the shroud and a deficit of energy near the hub. Therefore, it acts as a turbine at the hub and as a pump at the shroud having a vanishing total torque. The 10-bladed runner spins freely and ensures the designed output flow configuration. The cone angle of 17 • selected in this case corresponds to modern hydraulic turbines. We performed the unsteady pressure measurements on the cone wall using a set of eight fast response transducers. The transducers are displaced on four levels (labeled L0, L1, L2 and L3) along to the cone. The first level (L0) is located in the throat of the test section. The next three levels are located at 50 mm, 100 mm and 150 mm downstream the throat section. The pressure transducers with an accuracy of ±0.13% within a full range of ±100 kPa are flush-installed on the cone wall. This experimental setup allows us to examine the swirling flows with a single vortex rope as we visualize it on our test rig. We select the time interval of 32 s at a sampling rate of 256 samples per second for data acquisition based on several investigations. At least 10 data sets were acquired for each flow regime to ensure data reliability.
The standard deviation σ is defined according to Equation (1) being around ±1% for all measured values.
We have achieved the measurements for a discharge of Q = 30 L/s corresponding to a Reynolds number of 3.8 × 10 5 . The discharge correspond to a flow rate coefficient of q = 0.23 [33]. A flow meter with an accuracy of ±0.15% within the full range is installed on the test rig, Figure 2. The water temperature from 20 • C to 24 • C is determined during our measurements with no cooling system installed on the test rig. As a result, the uncertainties given by the temperature variations are negligible because of the water volume which is large enough (larger than 4 m 3 ). The entire hydraulic circuit was completely filled with water with no volume of air trapped inside. We perform the experimental investigations considering over-pressure conditions. Only non-cavitating vortex rope was examined in our investigations. Then, a constant value is selected for the water density. The method developed by Bosioc et al. [26] applies to assess the performances of the new proof of a concept. In this way, we compare the results for a new proof of a concept against other control methods (e.g., axial water jet method).

The Passive Control Method with Diaphragm
The main component of this novel control method for taming the vortex rope effects is an adjustable diaphragm. The diaphragm system installed on our swirl apparatus is presented in Figure 2-right side, placed at the cone outlet. The diameter of D = 0.16 m with area of A 0 = 0.0201 m 2 is associated to the cone outlet.
We selected four openings corresponding to different shutter areas of the adjustable diaphragm. The inner diameters of d = 0.134 m, 0.113 m, 0.1 m and 0.088 m and their associated shutter areas of A d = 0.014 m 2 , 0.01 m 2 , 0.0078 m 2 and 0.006 m 2 are considered in this experimental study. These values of inner diameter correspond to the shutter area ratios (A a ) of 30%, 50%, 60% and 70% regarding the cone outlet area A 0 , see Table 1.

Mean Pressure Analysis
The goal of the discharge cone is to convert the kinetic energy into potential energy with minimum hydraulic losses. This energy conversion is expressed by the wall pressure recovery coefficient c p , which it is given in dimensionless form by Equation (2), where p L0 is the mean pressure on the wall at L0 level- Figure 3a, p is the mean pressure measured downstream on the cone wall, = 998 kg/m 3 is the water density, V t is the bulk velocity in the throat and D t = 2R t = 0.1 m is the throat diameter corresponding to L0 level.

Mean Pressure Analysis
The goal of the discharge cone is to convert the kinetic energy into potential energy with minimum hydraulic losses. This energy conversion is expressed by the wall pressure recovery coefficient cp, which it is given in dimensionless form by Equation (2), where L0 p is the mean pressure on the wall at L0 level- Figure 3a, p is the mean pressure measured downstream on the cone wall, ρ = 998 kg/m 3 is the water density, Vt is the bulk velocity in the throat and Dt = 2Rt = 0.1 m is the throat diameter corresponding to L0 level.  The distribution of the pressure coefficient cp along the cone wall against the dimensionless axial coordinate is plotted in Figure 3b. We consider the dimensionless axial coordinate regarding the throat radius Rt displaced at L0 level of the test section- Figure 3a. The wall pressure recovery in the first part of the cone up to L1 level is negligible if it uses the diaphragm. In contrast, a significant improvement of the wall pressure recovery is obtained downstream to L1 level delaying the separation flow on the wall. For instance, the pressure recovery coefficient (at the wall) is practically twice in the middle of the conical diffuser (on L2 level). The distribution of the pressure coefficient c p along the cone wall against the dimensionless axial coordinate is plotted in Figure 3b. We consider the dimensionless axial coordinate regarding the throat radius Rt displaced at L0 level of the test section- Figure 3a. The wall pressure recovery in the first part of the cone up to L1 level is negligible if it uses the diaphragm. In contrast, a significant improvement of the wall pressure recovery is obtained downstream to L1 level delaying the separation flow on the wall. For instance, the pressure recovery coefficient (at the wall) is practically twice in the middle of the conical diffuser (on L2 level).
It is expected when the pressure recovery on the cone wall is improve it will have diminished additional hydraulic losses associated to the vortex rope. However, the hydraulic losses increase on the cone once the diaphragm continues to obstruct the flow. The hydraulic losses cannot be correctly quantified based on the available experimental data.
Tănasă et al. [34] revealed that the hydraulic losses are less than half of the value received for the case with the vortex rope up to the relative shutter area of 50% (d = 0.113 m), and no larger than twice up to the relative shutter area ratio of 70% (d = 0.088 m), respectively.

Unsteady Pressure Analysis
In this section, we investigate the Fourier spectra of the unsteady pressure signals acquired on the cone wall for all shutter area ratios. The fundamental frequency associated with the self-induced instability and the equivalent amplitude determined based on Parseval's theorem [35] are obtained for each case. The precessing frequency is written in dimensionless form using the Strouhal number, while the dimensionless amplitude of the pressure pulsation is given as follows, The equivalent pressure pulsation amplitude is √ 2p RMS where p RMS is the root mean square of the unsteady part of the pressure signal according to Parseval's theorem [26]. This value quantifies the level of the flow unsteadiness. The acquired pressure fluctuations (AS), the reconstructed signals (RS) and its Fourier spectra (FT) on all four levels of the cone wall are plotted in Figure 4 for the case with vortex rope (without diaphragm). The Strouhal number Sh~0.39 is associated with the dominant frequency of the helical vortex rope. Here, the maximum equivalent amplitude (EA~0.28) is obtained on L1 level being associated with the largest eccentricity of the vortex filament [36]. The experimental investigation of the unsteady pressure field on the cone wall is performed for all diaphragm openings corresponding to different shutter area ratios. Significant pressure pulsation mitigation is obtained for all cases, with case involving diaphragm in comparison with the case without the diaphragm.
In this paper, the acquired pressure fluctuations (AS), the reconstructed signals (RS) and its Fourier spectra (FT) on all levels of the cone wall for two diaphragm shutter area ratios of 50% (d = 0.113 m) and 70% (d = 0.088 m) are plotted in Figures 5 and 6, respectively. One can observe that the maximum equivalent amplitudes of EA~0.17 were obtained. This value is diminished by over 45% in the case without the diaphragm. A synopsis view over dynamic performances of this new control method is provided in Figure 7. The evolution of equivalent amplitudes on the cone wall for all investigated cases is provided in Figure 7a. In addition, the Strouhal number associated with the self-induced instability for all investigated cases is plotted in Figure 7b. It can be observed that the frequency is changing in a limit of 10% for the case with the maximum shutter area ratio. The Strouhal number is practically unchanged when the shutter area is slightly increased while the maximum equivalent amplitude of the pressure pulsations is mitigated. On the other side, it significantly decreases the maximum equivalent amplitude on all levels, being around the same values for diaphragm cases with shutter area ratios from 50% to 70% (d = 0.113 . . . 0.088 m).
with vortex rope (without diaphragm). The Strouhal number Sh~0.39 is associated with the dominant frequency of the helical vortex rope. Here, the maximum equivalent amplitude (EA~0.28) is obtained on L1 level being associated with the largest eccentricity of the vortex filament [36]. The experimental investigation of the unsteady pressure field on the cone wall is performed for all diaphragm openings corresponding to different shutter area ratios. Significant pressure pulsation mitigation is obtained for all cases, with case involving diaphragm in comparison with the case without the diaphragm.  In this paper, the acquired pressure fluctuations (AS), the reconstructed signals (RS) and its Fourier spectra (FT) on all levels of the cone wall for two diaphragm shutter area ratios of 50% (d = 0.113 m) and 70% (d = 0.088 m) are plotted in Figures 5 and 6, respectively. One can observe that the maximum equivalent amplitudes of EA~0.17 were obtained. This value is diminished by over 45% in   Two snapshots with flow structure captured on the test rig are presented in Figure 8 to support the results. To visualize the flow structures, we introduced air in the rig. One can observe a precessing helical vortex for a swirling flow with no control method in Figure 8a. The bubble-type vortex is visualized at the shutter area ratio of 70% corresponding to the inner diameter of the diaphragm of d = 0.088 m. This vortex shape is less harmful from the dynamic point of view than the helical shape presented in Figure 8b. Zhang et al. [37] visualized a similar helical structure in a draft tube cone of a Francis turbine model operating at part-load conditions. Extensive experimental and numerical investigations have given a comprehensive understanding of the flow structure with various details of the hydrodynamic field [38]. Resiga et al. [39] have shown that the velocity profiles with central recirculation or quasi-stagnation region capture well the velocity field associated to swirling flow in a cone.
The helical vortex is wrapped on the central recirculation or quasi-stagnation region with a larger angle than the cone wall, inducing strong pressure fluctuations on the cone wall. Two snapshots with flow structure captured on the test rig are presented in Figure 8 to support the results. To visualize the flow structures, we introduced air in the rig. One can observe a precessing helical vortex for a swirling flow with no control method in Figure 8a. The bubble-type vortex is visualized at the shutter area ratio of 70% corresponding to the inner diameter of the diaphragm of d = 0.088 m. This vortex shape is less harmful from the dynamic point of view than the helical shape presented in Figure 8b Two snapshots with flow structure captured on the test rig are presented in Figure 8 to support the results. To visualize the flow structures, we introduced air in the rig. One can observe a precessing helical vortex for a swirling flow with no control method in Figure 8a. The bubble-type vortex is visualized at the shutter area ratio of 70% corresponding to the inner diameter of the diaphragm of d = 0.088 m. This vortex shape is less harmful from the dynamic point of view than the helical shape presented in Figure 8b. Zhang et al. [37] visualized a similar helical structure in a draft tube cone of a Francis turbine model operating at part-load conditions. Extensive experimental and numerical investigations have given a comprehensive understanding of the flow structure with various details of the hydrodynamic field [38]. Resiga et al. [39] have shown that the velocity profiles with central recirculation or quasi-stagnation region capture well the velocity field associated to swirling flow in a cone.
The helical vortex is wrapped on the central recirculation or quasi-stagnation region with a larger angle than the cone wall, inducing strong pressure fluctuations on the cone wall. Extensive experimental and numerical investigations have given a comprehensive understanding of the flow structure with various details of the hydrodynamic field [38]. Resiga et al. [39] have shown that the velocity profiles with central recirculation or quasi-stagnation region capture well the velocity field associated to swirling flow in a cone.
The helical vortex is wrapped on the central recirculation or quasi-stagnation region with a larger angle than the cone wall, inducing strong pressure fluctuations on the cone wall.
Moreover, Skripkin et al. [36] identify aperiodic pressure pulses on the cone wall because of self-merging and reconnecting of the vortex helix with the formation of a vortex ring.
Sarpkaya [40], Hall [41] and Leibovich [42][43][44] showed that the vortex breakdown is a sudden change in the slender vortex core, evolving downstream into a bubble shape or a helical pattern. Tănasă et al. [45] numerically shows this recirculation region captured inside the cone. As a result, the bubble type is an axisymmetric expansion of the recirculation zone with smaller eccentricity being less harmful than the helical type.
It may be worthwhile to note that the diaphragm inducing an axisymmetric flow forces the transition from a helical type to a bubble shape. A compromise between the pressure pulsation mitigation and the hydraulic losses has to be performed when this method is used. For this reason, the shutter area ratio of a diaphragm between 40-60% is recommended to be operated at part-load conditions to maintain a good balance between the hydraulic losses and the pressure fluctuation mitigation [34]. As a result, the dimensionless equivalent amplitudes on the cone wall obtained for the diaphragm control method with the shutter area ratio of 50% are compared against swirling flow with vortex rope and the method of axial water jet method with 10% discharge, developed by Bosioc et al. [26] (Figure 9). By comparison, when it is used the diaphragm, the amplitudes has lower values than the water jet injection method.
Appl. Sci. 2019, 9, x FOR PEER REVIEW 11 of 17 Moreover, Skripkin et al. [36] identify aperiodic pressure pulses on the cone wall because of selfmerging and reconnecting of the vortex helix with the formation of a vortex ring.
Sarpkaya [40], Hall [41] and Leibovich [42][43][44] showed that the vortex breakdown is a sudden change in the slender vortex core, evolving downstream into a bubble shape or a helical pattern. Tănasă et al. [45] numerically shows this recirculation region captured inside the cone. As a result, the bubble type is an axisymmetric expansion of the recirculation zone with smaller eccentricity being less harmful than the helical type.
It may be worthwhile to note that the diaphragm inducing an axisymmetric flow forces the transition from a helical type to a bubble shape. A compromise between the pressure pulsation mitigation and the hydraulic losses has to be performed when this method is used. For this reason, the shutter area ratio of a diaphragm between 40%-60% is recommended to be operated at part-load conditions to maintain a good balance between the hydraulic losses and the pressure fluctuation mitigation [34]. As a result, the dimensionless equivalent amplitudes on the cone wall obtained for the diaphragm control method with the shutter area ratio of 50% are compared against swirling flow with vortex rope and the method of axial water jet method with 10% discharge, developed by Bosioc et al. [26] (Figure 9). By comparison, when it is used the diaphragm, the amplitudes has lower values than the water jet injection method.

Pressure Pulsations Decomposition
Wahl [46] identifies two types of pressure fluctuations associated with the draft tube surge. First one is the asynchronous (rotating) type of the pressure fluctuation being associated to the precession of the helical vortex. The asynchronous pressure fluctuation is trapped in the discharge cone, according to Wu et al. [47]. The other fluctuation is synchronous (plunging) one. This fluctuations travel as standing waves along to the hydraulic passage being dangerous in operation. Several theories have been advanced to account for synchronous pressure fluctuations [48,49]. Nishi et al. [21] suggested that the interaction between the vortex rope and the draft tube elbow is the source of the synchronous fluctuations. Jacob and Prenat [50] have performed a phase analysis for two simultaneously acquired pressure signals on the discharge cone of a Francis turbine to discriminate between rotating (asynchronous) and plunging (synchronous) oscillations, respectively. In their investigations, the synchronous (plunging) component was lower in amplitude than the asynchronous (rotating) component. However, the synchronous (plunging) pressure pulsations are accepted as the driving mechanism behind most operational problems related to draft tube surging, although there are times when simple vibration and noise caused by the asynchronous (rotating) pulsations can be serious.

Pressure Pulsations Decomposition
Wahl [46] identifies two types of pressure fluctuations associated with the draft tube surge. First one is the asynchronous (rotating) type of the pressure fluctuation being associated to the precession of the helical vortex. The asynchronous pressure fluctuation is trapped in the discharge cone, according to Wu et al. [47]. The other fluctuation is synchronous (plunging) one. This fluctuations travel as standing waves along to the hydraulic passage being dangerous in operation. Several theories have been advanced to account for synchronous pressure fluctuations [48,49]. Nishi et al. [21] suggested that the interaction between the vortex rope and the draft tube elbow is the source of the synchronous fluctuations. Jacob and Prenat [50] have performed a phase analysis for two simultaneously acquired pressure signals on the discharge cone of a Francis turbine to discriminate between rotating (asynchronous) and plunging (synchronous) oscillations, respectively. In their investigations, the synchronous (plunging) component was lower in amplitude than the asynchronous (rotating) component. However, the synchronous (plunging) pressure pulsations are accepted as the driving mechanism behind most operational problems related to draft tube surging, although there are times when simple vibration and noise caused by the asynchronous (rotating) pulsations can be serious.
Synchronous (plunging) pressure fluctuations can produce variations in head, discharge, torque, and output power known in the literature as a power swing [13]. Equations (5) and (6) are applied for two unsteady signals acquired on the same level to discriminate between asynchronous and synchronous components, respectively: As expected, the equivalent amplitudes associated with the rotating component (RC) are larger than the plunging component (PC) for the case without the diaphragm (Figure 10). This means the helical structure of the vortex rope is well developed. The plunging component (PC) becomes dominant regarding the rotating component (RC) when the diaphragm with a shutter area ratio larger than 50% throttles the cone outlet area. In these cases, the flow structure in the cone changes as the cross-section closes, revealing a bubble type for the case with an area ratio of 70%. In addition, the mitigation of pressure pulsations by up to 45% for all diaphragm cases highlighted in the previous section implies a significant decrease of the rotating component (up to 80-90%) correlated with a slight increase (10% to 50%) of the plunging component compared with the case without a diaphragm (note that we investigated the diaphragm method on a surrogate model of swirl generator). However, the goal was to mitigate the rotating part associated to the vortex rope. This conclusion supports our previous recommendation about selecting a diaphragm with a shutter area ratio from 40% to 60% [34]. Synchronous (plunging) pressure fluctuations can produce variations in head, discharge, torque, and output power known in the literature as a power swing [13]. Equations (5) and (6) are applied for two unsteady signals acquired on the same level to discriminate between asynchronous and synchronous components, respectively: R(t)=ST -P 1 (6) As expected, the equivalent amplitudes associated with the rotating component (RC) are larger than the plunging component (PC) for the case without the diaphragm (Figure 10). This means the helical structure of the vortex rope is well developed. The plunging component (PC) becomes dominant regarding the rotating component (RC) when the diaphragm with a shutter area ratio larger than 50% throttles the cone outlet area. In these cases, the flow structure in the cone changes as the cross-section closes, revealing a bubble type for the case with an area ratio of 70%. In addition, the mitigation of pressure pulsations by up to 45% for all diaphragm cases highlighted in the previous section implies a significant decrease of the rotating component (up to 80%-90%) correlated with a slight increase (10% to 50%) of the plunging component compared with the case without a diaphragm (note that we investigated the diaphragm method on a surrogate model of swirl generator). However, the goal was to mitigate the rotating part associated to the vortex rope. This conclusion supports our previous recommendation about selecting a diaphragm with a shutter area ratio from 40% to 60% [34].

Conclusions
The paper introduces a novel passive control approach for mitigating the self-induced instabilities in decelerated swirling flows using an adjustable diaphragm. We performed extensive experimental investigations without and with a diaphragm placed at the cone outlet. Four diaphragm openings with the following shutter area ratios of 30%, 50%, 60% and 70% are selected. The experimental investigations are performed on a swirling flow test rig. The unsteady pressure signals are acquired on the cone wall to assess the performances of the new control method. The pressure recovery on the cone wall is obtained based on mean values while the dynamic behavior is determined from the unsteady part of the recorded signals. Next, both plunging and rotating components are discriminated based on the acquired unsteady pressure signals.
The conclusions are summarized as follows: (i) The pressure recovery on the cone wall is significantly improved using the diaphragm method regarding the swirling flow (e.g., the pressure recovery on the cone wall is more than twice of that on the L2 level, which is located in the middle of the cone). (ii) The diaphragm method decreases the amplitude of the pressure fluctuation up to 45% while the frequency remains practically unchanged. (iii) The bubble-type vortex flow configuration occurs when the diaphragm shutter area ratio of 70% (d = 0.088 m) is selected. This vortex configuration is less harmful than the swirling flow with the helical vortex rope. (iv) The amplitude of the rotating component is significantly diminished when the shutter area of the diaphragm is increased. In contrast, the amplitude of the plunging component is slightly amplified when the diaphragm shutter area is increased. (v) The mitigation of this plunging component is the subject of another research study using a pulsating water jet control method [51].
The dimensionless equivalent amplitudes obtained with this passive control method are compared against an axial water jet control method. The dimensionless equivalent amplitudes associated to the diaphragm method with the shutter area ratio of 50% are smaller than values with axial water method with 10% jet discharge. One can conclude that the novel proof of a concept examined in this paper brings valuable benefits if it fulfils a good balance between the dynamical behavior and the hydraulic losses. The diaphragm method is simple, robust, low-cost, is easy to implement on a real turbine, and is easily operated.
This passive control method can be appropriately adjusted in terms of the operating conditions. We recommend that the diaphragm be operated with the shutter area ratios from 40% to 60% for a swirling flow configuration (as investigated in this paper) to strike a good balance between the dynamical behavior and the hydraulic losses. In addition, we recommend the diaphragm be switched on at the recommended operating conditions, while it should be retracted to the cone wall if the hydraulic turbine operates around the best efficiency point.

Patents
This new method for swirling flow control is patented according to State Office for Inventions and Trademarks-Romania, no. 130075: Title: Method and equipment for controlling the swirling flow through the conical diffuser of hydraulic turbines. Inventors: Susan-Resiga, R.F., Tanasa, C., Bosioc, A.I., Ciocan, T., Stuparu, A., Muntean, S.