A GRAVITATIONAL VORTEX WATER TURBINE ASSEMBLY
Field of the invention
The invention relates to a water turbine for converting kinetic and potential energy from a water flow into mechanical force, and subsequently into electrical energy through a generator. It concerns in particular a gravita¬tional vortex water turbine assembly, wherein the energy is converted from a vortex which is formed by the water flow under the influence of gravity.
State of the art
Such gravitational vortex water turbine assembly is, for example, known from WO2004/061295. The vortex water turbine assembly includes a rec-tangular basin surrounded by four side walls, with an inflow opening in one of said side walls. The basin further includes a horizontal bottom with a round, central outflow opening for inducing a stable vortex in the water flow under the influence of gravity. A water turbine is mounted in the basin coaxially with the vortex. The water turbine comprises a turbine rotor hav¬ing vertical turbine blades. The tangential component of the water flow of the vortex acts on these turbine blades, causing them to rotate. The water flow of the vortex further flows ring-shaped, axially downwards through the turbine rotor. The water turbine is, for example, coupled to an electrical generator and to subsequently generate electrical energy.
Such a gravitational vortex water turbine assembly is beneficial in situa-tions where the height difference in the water flow is too low for some oth¬er types of water turbine assemblies to work efficiently. The gravitational water vortex turbine makes use of the energy that is accumulated in the vortex under the influence of gravity and is therefore less dependent on the kinetic and/or potential energy which is present in the source of the water flow.
A similar gravitational vortex water turbine assembly is furthermore also known from WO2015/017881. In order to stimulate the efficient formation of a vortex, this water gravitational vortex turbine assembly comprises a cylindrical basin, which is, for example, provided with side walls with spiral fins. Furthermore, also an inflow channel and an inflow opening is provid¬ed in the side wall of the basin which substantially tangentially supplies the water flow near the side wall of the cylindrical basin so as to achieve a more efficient formation of a vortex.
It is clear that further water turbine assemblies are known from for exam-ple US4076448, US5921745, US2015/233340, AT412363B, CH699133B1, US2013/022456. Most of these systems make use of inter-mediate guide vanes which extend in and/or upstream and/or downstream of the inlet opening of the basin. These intermediate guide vanes increase viscous losses thereby reducing efficiency of the turbine assembly, reduce robustness of the turbine assembly against debris and reduce fish friendli¬ness.
There continues to exist a need to further optimize such a gravitational vortex water turbine assembly. It is an object to realize a larger electrical power without the need for a higher flow rate, larger height difference and a larger installation for the gravitational vortex water turbine assembly.
Summary of the invention
For this object, according to a first aspect of the invention, there is provid-ed a gravitational vortex water turbine assembly, comprising:
- a spiral-shaped vortex basin configured to induce a vortex in a water flow under the influence of gravity, having a substantially verti¬cal central axis, the vortex basin comprising a side wall with a tan¬gential inflow opening for supplying the water flow to the vortex and a bottom with a central outflow opening for discharging the water flow of the vortex ,
-a water turbine, disposed under the basin, coaxially with the
central axis of the vortex, comprising a turbine housing, coupled to
the central outflow opening and a turbine rotor,
wherein the turbine rotor comprises a central rotor hub and rotor blades attached thereon, and wherein the rotor blades:
-at an upstream end have a smaller angle relative to the central axis than the angle at the downstream end;
-at a radially inward end have a larger angle relative to a plane according to the central axis than at a radially outward end; and
-at a radially inward end have a smaller angle relative to a plane perpendicular to the central axis than at a radially outward end,
such that the rotor blades are configured to absorb the tangential, axial and radial component of the water flow of the vortex..
It is clear that the central outflow opening is situated at the centre point of the spiral-shaped vortex basin. The central outflow opening thereby com-prises, for example, a substantially circular cross section of which the cen¬tral point substantially corresponds to the centre point of the spiral-shaped vortex basin, as well as the central axis of the induced vortex. In this man¬ner, the water flow with which the vortex is formed in the basin, is pro¬cessed more efficiently, such that the maximum flow rate to flow through the turbine can be increased. Since the water turbine is no longer posi¬tioned in the basin, but underneath the basin, the formation of the vortex in the basin can be accomplished in a consistent manner, without any impact of the water turbine, and is the vortex used as a means to create addition¬al height difference over the turbine. By positioning the rotor at this place, full use is also made of the tangential as well as the axial and radial veloci¬ty.As will be explained further, this means, for embodiments wherein the wa¬ter turbine assembly makes use of a diffuser, that the turbine rotor is dis¬posed in a turbine housing which forms the transition between the basin and this diffuser. Furthermore, it is also clear that the inflow opening is lo¬cated at the wider end of the geometrical progression of the spiral-shaped side wall of the basin. Additionally, the spiral shape of the basin ensures a more efficient and stable formation of the vortex in the basin. In order to stimulate the efficient formation of a vortex, the gravitational vortex water turbine assembly can have a basin having a spiral shape which substan¬tially corresponds with an Archimedes spiral or a logarithmic spiral, such as, for example, a Fibonacci spiral or a Bernoulli spiral. The origin, or the centre point of this spiral shape is then situated preferably near the outflow opening in the bottom of the basin. Preferably, the side walls of the basin are for the most part arranged vertically, which allows for a simple produc¬tion. Near the bottom of the basin, the side walls may preferably be transi¬tioned into the bottom of the basin by means of a rounding as, in this manner, this will achieve a good conduction of the flow of liquid and will also allow, in the event that a mould is used in the production of the basin, to obtain a good release of this mould.
In this manner, the gravitational water vortex turbine can fully make use of the vortex to create, already at low height difference, a uniform flow of liq¬uid wherein the energy can be extracted at high efficiency. In this manner, a larger and slower, rotating liquid flow is advantageously, relative to alter¬native types of water turbine assemblies, gradually accelerated to the cen¬tre of the vortex and towards the outflow opening. The positioning of the water turbine beneath the outflow opening, and the accompanying oc¬curred acceleration of the water flow also allows the use of smaller turbine rotors. Furthermore, this principle also brings the speed of rotation of the turbine rotor to a high enough speed to use a cheaper generator. Howev¬er, this can be done in an ecologically and environmental friendly manner, as the relative speed difference between the water flow in the vortex, as well as all the debris and animals in this flow of liquid, and the turbine rotor of the water turbine is limited. Both namely rotate more or less synchro¬nized around the centre point of the vortex.
It is thus clear that the vortex water turbine differs from prior art system as it comprises a turbine which cannot be classified as a pure impuls turbine, nor as a pure reaction turbine, but comprises a turbine which is able to make use of all force components of the vortex as identified above and which is able to make use of the pressure difference developed by the tur¬bine assembly between the inlet and the outlet. In this way the turbine as¬sembly enables a reduction of the dimensions of the assembly and an in¬crease in efficiency at a larger flow rate for a predetermined height differ¬ence of the water flow, thereby leading to a reduced installation cost and complexity for a predetermined power rating. This is especially advanta¬geous when the vortex water turbine assembly is applied at locations where there is a relatively large ratio between the flow rate and the height difference of the flow. It is further clear that the energy potential of such a water turbine assembly is larger. Due to the dimensioning of the impel-lerhub it is ensured that a pressure drop can be realized over the impeller height in order to obtain a further energy gain from this pressure differ¬ence. As a result, the turbine is functioning well in an environment with a free outlet, as well as in an environment in which the outlet is located be¬low the downstream water level. Also, the impeller design makes it possi¬ble to send flow & head via the impeller speed for optimal energy produc¬tion. Further the use of an outlet below the downstream water level allows for an increased use of the acceleration of the water flow and the use of the pressure difference over the turbine, thereby allowing for a turbine ro¬tor with smaller dimensions.
According to an embodiment the water turbine includes an electrical gen¬erator, or the water turbine is coupled to an electrical generator for gener¬ating electrical energy. It goes without saying that also alternative embod-

iments are conceivable, wherein the water turbine is also used for a me¬chanical drive of all kinds of devices, such as, for example, a mechanical drive of a water purification plant.
According to an embodiment, a water turbine assembly is provided, char-acterized in that the side wall extends downstream around the central axis from a first side up to an opposite second side of the inflow opening, wherein the distance between the side wall and the central axis thereby decreases from a maximum radius near the first side to a minimum radius near the second side according to a downstream direction.
This form of the side wall of the basin ensures an increase in efficiency of the gravitational vortex water turbine assembly as it induces a vortex in a more efficient manner than, for example, a basin with a cylindrical side wall. It is clear that the spiral-shaped side wall thereby extends substantial¬ly completely around the central axis, for example, by an angle in the range of 330° to 390°. It is clear that in assistance for interpretation of the feature that the side wall extends downstream around the central axis this could also be thought of as for example the side wall unwinding around the central axis.
It is further clear that the decrease in the distance between the side wall and the central axis according to some embodiments could be continuous, however it is clear that alternative embodiments in which a more discrete decrease is realised are also possible, for example in which this distance is decreased for a plurality of intervals of the side wall of the side wall, for example intervals of the side wall which extend around the central axis over a respective angle in the range of 30° to 180°, for example 90°, and in which for example each of these intervals of the side wall comprises a section with a predetermined constant bending radius. This thus means for example a side wall with two, three, four, five, ... such intervals of the side wall, each of these intervals comprising a predetermined constant bending

radius, in which the constant bending radius of a subsequent downstream interval is smaller is then the preceding upstream interval. It is clear that variations are possible in which each of the intervals comprise a substan¬tially constant bending radius, which remains within a predetermined toler¬ance of for example 2% to 15% of a predetermined average, median or mean predetermined bending radius for this respective interval of the side wall. Such embodiments are particularly advantageous when combined with an embodiment in which the side wall comprises a plurality of seg¬ments. Each of these segments then comprising such a respective prede¬termined bending radius, such that when assembled a subsequent down¬stream segment of the side wall comprises a corresponding predetermined bending radius which is smaller than that of a preceding upstream seg¬ment of the side wall. It should further be clear that such a side wall com¬prising such intervals and/or segments as described above, could in gen¬eral be usefull when comprised in any suitable gravitational vortex water turbine assembly comprising a spiral-shaped vortex basin configured to induce a vortex in a water flow under the influence of gravity, having a substantially vertical central axis, the vortex basin comprising a side wall with a tangential inflow opening for supplying the water flow to the vortex and a bottom with a central outflow opening for discharging the water flow of the vortex. This thus means irrespective of the specific configuration and positioning of for example turbine rotor assembly of the water turbine assembly, etc. As this leads to clear advantageous with respect to the production and transport of such a side wall of the turbine assembly.
According to a further embodiment, a water turbine assembly is provided, characterized in that the minimum radius is in the range of 50% to 85% of the maximum radius.
This decrease of the side wall of the spiral-shaped basin ensures that the incoming water flow flows into the vortex in an optimum manner through the inflow opening in the substantially spiral-shaped basin. It is thereby

understood that the incoming water flow flows preferably substantially tan-gentially to the spiral-shaped basin through the inflow opening in the side wall. That is to say, in a way the water flow near the inflow opening follows the inner wall of the side wall, for example at an angle in the range of 0° to 20°, relative to the plane of the side wall.
According to a further embodiment, a water turbine assembly is provided, characterized in that the course of the distance of the sidewall to the cen¬tral axis between the maximum radius and the minimum radius occurs ac¬cording to:
- a logarithmic spiral; or
- an Archimedes spiral.
The logarithmic spiral can be carried out, for example as a Fibonacci spiral or a Bernoulli spiral. Alternative embodiments are possible, such as for example a plurality of sequential arcs comprising a decreasing arc radius.
Such a shape increases the maximum flow rate which can flow through the water turbine assembly and the efficiency with which the vortex is in-duced. Moreover, this also allows to dimension the course of the shape of the side wall in a simple manner since the shape of the side wall is almost equivalent to a simple, mathematically defined spiral shape. It is clear this effect is caused by the impeller and impeller hub design in addition to the shape of the basin.
According to a further embodiment, a water turbine assembly is provided, characterized in that the side wall includes a plurality of segments. Accord¬ing to further embodiments these segments comprise a different diameter, such as described in more detail below.
The use of segments allows for easy transport of the basin after which the predefined shape of the basin can be installed at the site as a kind of pre-

fab construction. This allows to ensure the desired shape of the basin with greater precision and allows a more efficient installation. We define the shape before we are going to install. In this manner, a side wall can be produced of which the shape can be adjusted afterwards during the instal¬lation according to specific parameters of the water flow, such as, for ex¬ample, the flow rate, the height difference, etc., as these parameters of the river, for example, would change substantially.
According to a further embodiment, a water turbine assembly is provided, characterized in that the central outflow opening of the bottom has a radi-us which is smaller than or equal to the minimum radius of the side wall; and the inner radius of the turbine housing, near the turbine rotor, is in the range of 20% to 45% of the maximum radius of the side wall.
In this manner, the portion of the vortex with a maximum angular velocity is enlarged near the outflow opening, and subsequently in the water tur-bine which is connected to this outflow opening. If you move from the out¬side to the inside along the radius of the vortex, then the vortex speed will first increase exponentially, and after reaching a maximum speed will then decrease linearly to zero in the absolute centre point of the vortex near the central axis. Alternatively, such a vortex thus comprises a core zone, in which the angular velocity of the water flow increases linearly up to a cer¬tain maximum angular velocity at an increase of the distance to the central axis, after which, outside of this core zone, the angular velocity decreases again with an increase of the distance to the central axis. With such a range for the radius of the central outflow opening and the adjoining inner wall of the turbine housing, the portion of the core zone of this vortex is maximized near the turbine rotor. A limited exceeding of the core zone, for example with a maximum of 20%, may be desirable, but a too great ex¬ceeding results in a water flow with a decreasing angular speed which ad¬versely affects the efficiency of the turbine rotor. It is further clear that preferably also the central part of the vortex is not covered by the impeller,

such that this low speed part does not reduce the average speed of the vortex acting on the impeller blades as described in further detail below with respect to Figure 19.
According to a further embodiment, a water turbine assembly is provided, characterized in that the downstream end of the turbine housing comprises a diffuser configured to guide the water flow flowing in a direction having a component radially away from the central axis.
In this manner, the diffuser ensures that near the outflow opening of the housing of the water turbine there is less risk of a turbulent disturbance of the flow in the water turbine itself. Moreover, such a diffuser creates a cer-tain degree of axial counter-pressure in the water turbine such that the risk of cavitation is reduced. Such a radial diffuser also allows for the diffuser, and therefore also the associated water turbine, to be kept compact with regard to the build-in depth. Finally, such a radial diffuser also facilitates the production, since the diffuser can be produced with two simple shapes that only during the installation have to be joined together.
According to a further embodiment, a water turbine assembly is provided, characterized in that the diffuser is further configured to guide the water flow from a lowest position back upwards.
In this manner, a constant and higher axial counter pressure is created that reduces the risk of cavitation, as well as reduces a turbulent disturb-ance of the flow in the water turbine. Furthermore, such an embodiment also ensures that, even when the outflow opening of the water turbine would be located above the water surface, the risk is reduced that an air-flow would mix with the water flow through this outflow opening of the wa¬ter turbine, which would reduce the efficient operation of the water turbine.

According to a further embodiment, a water turbine assembly is provided, characterized in that the water turbine is positioned at its downstream end under the water surface.
In this manner, the pressure in the water flow near the water turbine is maintained and there is no risk that an air stream mixes with the outflowing water.
According to a further embodiment, a water turbine assembly is provided, characterized in that the turbine rotor comprises a central rotor hub and rotor blades attached thereon, wherein the number of rotor blades is in the range of two to ten, inclusive.
A limited number of rotor blades as well as a corresponding greater dis-tance between the rotor blades ensures that the water turbine is fish-friendly and less susceptible to interference by dirt or silting. Preferably, the turbine rotor also rotates at a relatively low speed, such as, for exam¬ple 300 revolutions per minute or less, for example 100 revolutions per minute or less.
According to a further embodiment, a water turbine assembly is provided, characterized in that the rotor blades are configured such that they absorb the tangential, axial and radial component of the water flow of the vortex. Additionally a pressure difference is created between the turbine inlet and outlet which allows for an increased level of energy which can be extracted from the flow.
It is clear that the rotor blades of the water turbine are mounted on a rotat-able central hub, which is coaxially mounted with the central axis of the vortex. This means that the axis of rotation of the hub of the turbine rotor substantially coincides with the central axis of the vortex. The axis of rota¬tion of the turbine rotor is substantially vertical.
Known gravitational vortex water turbine assemblies, wherein the turbine rotor is positioned in the basin, make use of vertical rotor blades. In this manner, only the tangential component of the water flow of the vortex is captured by the rotor blades. The axial and radial component of the water flow of the vortex is not disturbed by such known systems to minimize the risk that the vortex in the basin is disturbed. This embodiment, wherein the water turbine is positioned under the outflow opening in the bottom of the basin, allows to capture all of the components of the water flow of the vor¬tex near the water turbine, without the risk that the vortex is disturbed in the basin. This allows a greater efficiency of energy to be extracted from the water flow by the turbine rotor.
According to a further embodiment, a water turbine assembly is provided, characterized in that the rotor blades:
-at an upstream end have a smaller angle relative to the central axis than the angle at the downstream end;
-at a radially inward end have a larger angle relative to a plane according to the central axis than at a radially outward end; and
-at a radially inward end have a smaller angle relative to a plane perpen-dicular to the central axis than at a radially outward end.
In this manner, rotor blades can be realized which absorb both the tangen¬tial, axial, and the radial component of the water flow of the vortex.
According to a further embodiment, a water turbine assembly is provided, characterized in that the angle relative to the central axis at the upstream end is in the range of 0° to 45°, and in that the angle at the downstream end is in the range of 45° to 80°.
Preferably, these angles, at the rotational speed of the rotor for an optimal load of an associated generator, are substantially transverse to the tan- gential, radial and axial angles of the velocity vector of the water flow, such that an optimum impact of the water flow on the turbine blades is realized.
According to a further embodiment, a water turbine assembly is provided, characterized in that the maximum radius is in the range of 1.5 m to 10 m, inclusive. The maximum radius of the outflow opening in the bottom of the basin, as well as the turbine housing, is preferably in the range of 0.5 m to 3 m.
Such a water turbine assembly is compact and can be installed without major activities in, next to or in the vicinity of an existing watercourse.
According to a further embodiment, a water turbine assembly is provided, characterized in that the water turbine assembly further includes:
- an electrical generator, coupled to the water turbine, or mounted in the water turbine;
- a control unit, coupled to the generator, wherein the control unit is con-figured to control the rotational speed and the load of the generator and the therewith coupled turbine rotor of the water turbine during operation such that a Maximum Power Point Tracking Control is achieved.
In this manner, the electrical power which can be generated through the water turbine assembly can be maximized by optimizing the rotational speed and the load of the turbine rotor by the control unit of the electrical generator.
According to a further embodiment, a water turbine assembly is provided, characterized in that the water turbine assembly further includes:
- an electrical generator, coupled to the water turbine, or mounted in the water turbine;
- a control unit, coupled to the generator, configured to control the rota-tional speed and the load of the generator and to control the coupled tur-

bine motor of the water turbine during operation such that a relative maxi-mum velocity difference between the turbine blades and the water flow in the vortex does not exceed a predetermined maximum value.
In this manner, a fish-friendly water turbine assembly is realized with a minimal environmental impact, which reduces the need to provide for addi¬tional measures in order to prevent, for example, that fish swim into the water turbine, or in order to make it possible for fish to migrate past the water turbine.
According to a further embodiment, there is provided a water turbine as¬sembly, wherein the number of rotor blades is in the range of two to ten, inclusive.
According to a further embodiment, there is provided a water turbine as-sembly, wherein:
- the radius of the turbine central rotor hub is larger than a predetermined
minimum radius, the minimum radius being determined:
- as a percentage in the range of at least 10%, for example in the
range of 15% to 50%, for example in the range of 20% - 30%, of the radius of the turbine rotor and/or of the turbine rotor hous¬ing;
- as a percentage in the range of 10% to 65%, for example in the
range of 15% to 50%, for example of the radius of the forced vortex zone of the vortex; and/or
- such that the rotor blades cover an annular section around the cen-
tral axis of the vortex which does not exceed the core zone of the vortex by more than 25%, and preferably does not exceed the core zone of the vortex by more than 20%. a water turbine; and/or
- The water turbine assembly further comprises an outlet, which is locat¬
ed below the water surface and is directed downstream;

- The radius of the turbine housing is smaller than the maximum radius of the central outflow opening, and preferably the transition between the turbine housing and the central outflow opening comprises a curved shape, such as for example a conical shape or hyperbolical shape with a rounded transition to straight ends; and/or
- The turbine rotor comprises a radially outward cylindrical shroud cou¬pled to the rotor blades, such that the cylindrical shroud is rotated co-axially with the rotor blades during rotation of the turbine rotor.
According to a further embodiment, there is provided a water turbine as-sembly according to one or more of the claims 2 to 13, wherein:
- the side wall comprises a movable section at the second side of the inlet
210, configured to allow for a modification of the distance between the second side of the inlet and the central axis of the turbine rotor, such that the alignment of the central axis of the turbine rotor and central axis of the vortex is modified, preferably such that the align-ment of the central axis of the turbine rotor and the central axis of the vortex is increased; and/or
- no intermediate guide vanes are positioned in or upstream of the inlet
opening.
Several of these embodiments allow for an improved stabilizing and alignment of the central axis of the vortex with the central axis of the tur-bine rotor, thereby increasing efficiency of the rotor, reducing wear and aging effects on the components of the water turbine assembly. This fur-ther increases the flow rate and lowers the viscous losses in the free vor-tex in the basin, see for example Figure 17 versus the prior art solution of Figure 18, in which it is clear that the flow of a tailor vortex 21 of Figure 17 causes less viscous losses than that shown in Figure 18 for the prior art solution without a conical transition between the outlet opening and the turbine housing. Such a shroud for example allows for a larger rigidity of

the rotor, reducing undesired losses due to vibrations and an increased efficiency of the turbine assembly.
According to a second aspect of the invention, a method for the manufac-ture of a turbine rotor for use in a water turbine assembly is provided ac-cording to the first aspect of the invention, characterized in that the method comprises the following steps:
- simulation of the vortex on the basis of the turbine assembly;
- determination of the axial, tangential and radial components of the vortex near the water turbine;
- automatic generation of a shape for the rotor blades on the basis of the axial, tangential and radial components of the vortex such that a minimum boundary layer separation occurs near the rotor blades ;
- manufacturing the generated shape of the rotor blades by means of addi¬tive manufacturing techniques, for example, three-dimensional printing.
This production method allows to efficiently produce an optimum turbine rotor.
According to a third aspect of the invention, a device and a method is pro-vided for controlling a water turbine assembly according to the first aspect of the invention, when coupled to an electrical generator and associated control unit. It is clear that the electrical generator may be coupled to the rotor of the water turbine by means of a shaft or other suitable mechanical coupling. Alternatively, the generator may also be integrated into the water turbine, wherein, for example, the rotor of the generator is mounted in the turbine rotor and the stator of the generator is mounted in the turbine housing. The control unit of such a coupled generator preferably makes use of an MPPT or Maximum Power Point Tracking algorithm that by means of the control electronics may impose a variable load to the genera¬tor, and thus also the turbine rotor. By means of these variable load and speed of rotation of the turbine rotor, the impact velocity of the water flow

on the turbine rotor can be controlled, and for the turbine rotor virtual, vari¬able blade angles for the fixed turbine blades may be set, as it were.
This allows to further optimize the efficiency for the generation of electrical energy by means of the water turbine assembly. Preferably by making use of control electronics and/or software. Preferably the generator is integrat¬ed into the hub, the corresponding larger diameter of the hub then allows for a reduced use of the slow speed central part of the vortex, thereby in¬creasing efficiency. Preferably, such a generator is a low rotational velocity generator. Alternatively or optionally the generator could comprise or be coupled to a suitable transmission.
According to a fourth aspect of the invention some embodiments of the previous aspects of the invention could also be applied in a more general for different embodiments of a vortex water turbine assembly. For this ob-ject, a gravitational vortex water turbine assembly according to the fourth aspect of the invention is provided , comprising:
- a spiral-shaped vortex basin configured to induce a vortex in a water flow under the influence of gravity, having a substantially vertical central axis, the vortex basin comprising a side wall with a tangential inflow opening for supplying the water flow to the vortex and a bottom with a central outflow opening for discharging the water flow of the vortex, in which the water turbine assembly preferably further comprises:
- a water turbine, preferably disposed under the basin, coaxially with the central axis of the vortex, comprising a turbine housing, coupled to the central outflow opening and a turbine rotor.
Brief Description of the Figures
By way of example, some embodiments of the invention will be described with reference to the Figures in which:

Figure 1 schematically shows a partial cross-section in a perspective view of an embodiment of a gravitational vortex water turbine assembly;
Figure 2 schematically shows a top view of the embodiment of Figure 1;
Figure 3 schematically shows a perspective view of the embodiment of Figure 1;
Figure 4 schematically shows a partial cross-section in a side view of the embodiment of Figure 1;
Figures 5 to 7 respectively schematically show a top view, side view and perspective view of an embodiment of a turbine rotor for use in a water turbine assembly.
Figures 8 and 9 respectively schematically show a side view and a top view of an alternative embodiment of a turbine rotor;
Figure 10 schematically shows an installation of water turbine assemblies in or near a watercourse;
Figure 11 schematically shows the course of the water flow and the vortex for a water turbine assembly according to an embodiment of Figures 1 to 4;
Figures 12 and 13, respectively show a side view and a cross-section in side view of an alternative embodiment of a water turbine assembly;
Figures 14 and 15 schematically show a comparison of the efficiency and the power of various embodiments of the invention with respect to known water turbine assemblies;

Figures 15B - 22 show further clarifications and/or embodiments of a grav¬itational vortex water turbine assembly.
Detailed Description of the Figures
Figures 1 to 4 schematically show a gravitational vortex water turbine as¬sembly 1 according to a first embodiment of the present invention. The water flow 10 enters the assembly 1 via the inlet 210. This inlet is therefore preferably as far as possible oriented in the upstream direction such that a maximum amount of water can flow through the inlet 210 into the assem¬bly 1. The inlet 210 then guides the water 10 to the inflow opening 60 which forms the transition between the inlet 210 and the spiral-shaped vor¬tex basin 40. In this basin 40, the actual vortex 20 is induced around the vertical central axis 22.
The upright sidewall 50 of the spiral-shaped basin 40 starts at the outside or first side 62 of the inlet 210 near the inflow opening 60. From this side 62 the side wall further extends around the central axis 22 up to the inner or second side 64 of the inlet 210 near the inflow opening 60. For an opti¬mal formation of the vortex 20, the spiral-shaped side wall 50 preferably extends around the central axis 22 at an angle in the range of 330° to 390°.
The outer side 62 and, consequently, the inflow opening 60 preferably tangentially connects to side wall 50. As a result, the incoming water flow 10 through the inflow opening 60 near the side wall will flow substantially tangentially into the spiral-shaped basin 50. With other words, the water flow 10 near the inflow opening 60 will follow the inner wall of the side wall 50. In order to achieve this, the angle between the plane of the outer side 62 and the plane of the inside of the side wall 50 near the inflow opening 60 is in the range of 0° to 20°.

Due to the spiral-shaped shape and the connection of the side wall with both the outer side 62 and the inner or second side 64 of the inlet 210 to the inflow opening 60 the distance between the central axis 22 of the in-duced vortex 22 and the side wall 50 will decrease gradually. With other words, the side wall 50 will describe in the downstream direction a curve with decreasing radius. Near the first side 62 or at 0° of range the radius 42 will be at a maximum. After this, the radius will gradually decrease to radius 44 at 90°, to radius 46 at 270° and, finally, to radius 48 at 360° at the inner side 64 near the inflow opening 60. The ratio between the maxi-mum radius 42 and the minimum radius 48 defines thereby the size of the inflow opening 60 relative to the basin 40. This ratio is important for the overall efficiency of the assembly 1 and therefore, preferably, the minimum radius 48 is in the range of 50% to 85% of the maximum radius 42 .
Furthermore, the side wall 50 may describe a spiral. Preferably, this is a logarithmic spiral or Archimedes spiral. In this manner, the efficiency of the induced vortex 20 is increased while the shape of the side wall is easy to dimension.
The side wall 50 may further consist of one piece, or alternatively may comprise a plurality of segments. This allows to alter the course of the side wall 50 during or after the construction of the assembly 1 taking into ac¬count the specific parameters of the water flow 10, such as, for example, the flow rate, the height difference, etc.
The basin 40 further comprises an outflow opening 80 for discharging the water flow 10 of the vortex 20. This opening 80 is applied circular-shaped to the bottom 70 of the basin 40. Hereby, the central point of the opening coincides with the central axis 22. The radius 82 of the opening 80 is fur-thermore smaller than the minimum radius 48.

A water turbine 100 is coupled under the opening 80, connecting to the bottom 70 of the basin. This turbine 100 further comprises a turbine hous-ing 110 that guides the water flow 10 downwards. The turbine housing 110 has a circular shaped cross-section which may vary across the height of the housing. At the top of the housing 110, the radius of the circular cross-section corresponds to the cross-section of the outflow opening 80 and therefore to radius 82. The central axis of the turbine housing 110 further corresponds to the central axis 22. The turbine 100 further also comprises a rotor 120 coaxial with the central axis 22 which is mounted inside the turbine housing 110. This rotor 120 comprises a central hub 122 with rotor blades 124 coupled therewith. When the water flow 10 is guided through the opening 80, it will continue to be guided through the turbine housing along the rotor blades 124. Due to the tangential movement, the down¬ward or axial movement and the radial movement of the vortex 20 on the rotor blades 124, will rotate the rotor 120. The central hub 122 is rotatably mounted in the water turbine and is further coaxially mounted with the cen¬tral axis 22 of the vortex 20. This means that the axis of rotation 22 of the hub of the turbine rotor substantially coincides with the central axis 22 of the vortex 20. The axis of rotation of the turbine rotor is substantially verti¬cal.
Near the rotor blades 124, the inner radius 112 of the horizontal cross-section of the turbine housing is preferably in a range of 20% to 45% of the maximum radius 42. In this manner, near the outflow opening 80, and subsequently in the water turbine 100 which connects to this outflow open¬ing, the portion of the vortex 20 is increased with a maximum angular ve¬locity. Such a vortex comprises a core zone, in which the angular velocity of the water flow 10 linearly increases to a determined maximum angular velocity at an increase of the distance to the central axis 22, after which, outside of this core zone, the angular velocity decreases again at an in¬crease of the distance from the central axis 22. With such a range for the radius 82 of the central outflow opening and the connecting radius 112 of

the inner wall of the turbine housing 110, the portion of the core zone of the vortex 20 is maximized near the turbine rotor 120. A limited exceeding of the core zone, for example with a maximum of 20% may be desirable, but too large an exceeding delivers a water flow 10 having a decreasing angular velocity that negatively influences the efficiency of the turbine rotor 120.
The assembly 1 further comprises a downstream diffuser 130. This diffus-er is located below the rotor blades 124 and has the function to guide the water flow 10 radially away from the central axis 22 to the outlet 220. The turbine 100 and diffuser 130 are completely surrounded by the outlet 220. Outlet 220 comprises a bottom 140 at the underside of the turbine rotor 120. The top 141 of outlet 220 is located near the opening 80 and the un¬derside of the bottom 70 of the basin 40. As a result, the water flow 10 can rise back up to the level of the outflow opening 80 after leaving the diffuser 130. Outlet 220 further includes an output 142 because the side wall of the outlet 220 is open to one side. The opening 142 is located on the down¬stream side, i.e., on the opposite side of the inlet 210, and thus of the in¬flow opening 60.
Without diffuser 130, the water flow 10 could leave the water turbine 100 in a turbulent manner. This turbulent flow can, however, already occur near the rotor blades 124, and thus disturb the flow in the water turbine 100 it¬self. Due to the diffuser, the water flow is first guided away in a non-turbulent manner from the water turbine such that the risk of turbulence in the water turbine 100 itself is minimized. Moreover, such a diffuser 130 creates a certain axial counter-pressure in the water turbine, thus reducing the risk of damage to the water turbine 100 by cavitation is reduced.
Figure 11 illustrates the water flow 10 in the assembly 1 according to the above embodiment. The water flow 10 enters the assembly 1 through the inlet 210 where it is guided to the basin 40. In the basin, the vortex 20 is

then induced by guiding the water flow 10 into the spiral-shaped basin. At the bottom of the basin, the water flow then enters the water turbine 100 where the axial, radial and tangential component of velocity of the water flow 10 relative to the rotor induces the rotor to rotate. When the water flow 10 has passed the rotor, it arrives at the bottom of the assembly after which it is guided laterally through the diffuser to the outlet 220. The water flow 10 finally exits the outlet 220.
Figures 5 to 7 schematically show respectively a top view, side view and perspective view of the turbine rotor 120 for use in the assembly 1 accord¬ing to a first embodiment of the present invention. Figures 8 and 9 sche¬matically show respectively a side view and top view of the turbine rotor 120 for use in the assembly 1 according to a second embodiment of the present invention. Both of these embodiments are described together be¬low.
Rotor 120 comprises a central hub 122 which is rotatably mounted around the central axis 22 in the turbine housing 110. Five rotor blades 124 are mounted onto the hub 122. The number of rotor blades is not limited to five, but is preferably in the range of two to ten, inclusive. By limiting the number of rotor blades the distance 129 between the rotor blades 124 may be kept sufficiently large. In this manner, for example, fish can pass through the rotor if they are smaller than the distance 129 and a fish-friendly water turbine is thus obtained. Furthermore, the water turbine is therefore also less sensitive to disturbance by pollution and silting. This effect can be further enhanced by the turbine rotor 120 to rotate at a rela-tively low rotational speed such as, for example, 300 revolutions per mi-nute or less, for example, 100 revolutions per minute or less.
The rotor blades 124 are positioned on the rotor hub 122 such that they absorb the tangential, axial and radial component of the water stream 10 of the vortex 20, i.e., that the rotor 120 starts to rotate and thus experienc-

es a torque by the action of each of these components. The direction of these components is indicated in each of Figures 5 to 7, wherein T stands for the tangential component, for the radial component R and A for the ax¬ial component. Known gravitational vortex water turbine assemblies, wherein the turbine rotor is positioned in the basin, make use of vertical rotor blades. In this manner, only the radial component of the water flow of the vortex is captured by the rotor blades. The axial and radial component of the water flow of the vortex is not disturbed in such known systems to minimize the risk that the vortex is disturbed in the basin. This embodi¬ment, wherein the water turbine is positioned under the outflow opening in the bottom of the basin, allows to capture all of the components of the wa¬ter flow of the vortex near the water turbine, without the risk that the vortex in the basin is disturbed. This allows energy to be extracted from the water flow through the turbine rotor with greater efficiency.
Rotor blade 124 comprises an upstream end or side 126, i.e., the upper side of the rotor blade since in operation the upper or upstream side 126 first comes into contact with the water flow 10 from the vortex 20. This is schematically shown in Fig. 6 where the relative movement of the water flow 10 relative to the rotor blade is shown. The water flow 10 then leaves the rotor blade 124 along the side 128, i.e., the downstream side or lower side or end 128 at the bottom of the rotor blade 124. The placement of these two sides then determine the extent to which the energy of the axial velocity component of the water flow will be converted in a movement of the rotor 120. The positioning of the sides 126 and 128 is characterized by the smallest respective angle 126A and 128A between the central axis 22 and the plane tangent to the respective side 126 and 128. For an optimum conversion of the axial velocity component, the angle 126A at the up¬stream end or side 126 is preferably smaller than the angle 128A on the downstream end 128. Preferably, the angles are further selected such that, at the nominal rotational speed of the rotor, the radial velocity com¬ponent of the water flow 10 is optimally engaging the rotor blade 124. This

may be, for example, when the angle 126A at the upstream end 126 is in the range of 0° to 45° and when the angle 128A at the downstream end 128 is in the range of 45° to 80°.
The placement and shape of the rotor blade 124 is further determined by the angles 125A and 127A. Angle 125A is the angle between a vertical plane tangent to the radially inward end 125 of the rotor blade 124 and a plane through the central axis 22 and through this radially inward end 125. The radially inward end is thereby the position where the rotor blade is attached to the central hub 22. Angle 127A is the angle between a vertical plane tangent to the radially outward end 127 of the rotor blade 124 and a plane through the central axis 22 and through this radially inward end 127. Preferably, the angle 125A is greater than the angle 127A in order to achieve an optimal impact of the water flow 10 on the turbine blades. With other words, the radially inward end 125 has such a greater angle 125A with respect to a plane according to the central axis 22 than at the radially outward end 127.
Finally, the placement and shape of the rotor blade 124 is also determined by the angles 125B and 125C. Angle 125B is the angle between the radi¬ally inward end 125 of the rotor blade 124 and a plane perpendicular to the central axis 22 and through this radially inward end 125. Hence, angle 125C is the angle between the radially outward end 127 of the rotor blade 124 and a plane perpendicular to the central axis 22 and through this radi¬ally inward end 127. Preferably, the angle 125C is larger than the angle 125B in order to achieve an optimal impact of the water flow 10 on the tur¬bine blades. With other words, the radially inward end 125 has a smaller angle 125B with respect to a plane perpendicular to the central axis 22 than at a radially outward end 127.
According to an embodiment of the invention, the following method may be provided in the turbine rotor 120. In a first step, a simulation of the cre-ated vortex 20 is carried out in the assembly 1. In this simulation, the rotor

120 is still not present such that the vortex 20 can flow freely through the water turbine. An example of a graphical result of such a simulation is shown in Figure 11. The rotor is shown in an illustrative way, but it does not interact with the water flow 10. In a next step, the axial, tangential and radial components of the vortex 20 near the rotor blades 124 in the water turbine 100 are determined. Subsequently, on the basis of these compo-nents, the rotor blades are generated in such a manner that a minimal boundary layer separation of the water flowl 0 is created near the rotor blades. Since all necessary parameters are known, the generation of the shape of the rotor blades may occur completely automatically. Finally, the rotor blades are manufactured. This may be done efficiently using additive manufacturing techniques, such as, for example, three-dimensional print¬ing. Using the above steps, a turbine rotor 120 may be dimensioned and produced in an efficient manner.
Figures 12 and 13 show respectively a side view and a cross section in side view of an alternative embodiment of the water turbine assembly ac-cording to the embodiment of Figures 1 to 4. Inlet 210, basin 40 and water turbine 100 are herein constructed in the same manner. The diffuser 330 and outlet 320 have an alternative configuration. The diffuser 330 is con-figured such that the water flow 10 is first guided away radially from the rotor 120 and is then axially from the lowest position forced back upwards towards the outlet 320. As a result, the bottom 340 of the outlet 320 is po-sitioned higher than the position of the water flow 10 when it has passed the rotor 120. Because the water flowl 0 is to be forced back upwards, in this manner a constant and higher axial counter-pressure is created which reduces the risk of cavitation, as well as a turbulent disturbance of the flow in the water turbine. Furthermore, such an embodiment also ensures that, even when the outflow opening of the water turbine would be located above the water surface, that the risk is reduced that an airflow through this outlet opening of the water turbine would mix with the water flow, which would reduce the efficient operation of the water turbine 100.

Figure 10 schematically illustrates an installation of the water turbine as-semblies 1 in or near a watercourse 2. In an initial installation option, the assembly 1 is placed in the river 2. The inlet 210 is thereby directed up-stream such that the water flowl 0 can flow into the basin where the vortex 20 is induced. The outlet 220 or 320 is located below the water surface and is directed downstream such that the water flow 10 can flow with the flow of the river 2 out of the outlet 220, 320. According to a further embod¬iment, there is provided a water turbine assembly, characterized in that the water turbine is located at its downstream end under the water surface. In this manner, the pressure in the water flow 10 near the water turbine 100 is maintained and there is no risk that an airflow mixes with the outflowing water, which could lead to a decrease in the efficiency of the system. This embodiment has the advantage that the installation thereof can be done relatively easy without a lot of earthmoving. It is surely sufficient to provide an adequate foundation in the watercourse 2 and anchor the assembly thereon.
In a second installation option, the assembly is embedded in the bank alongside the watercourse 2. To guide the water flow 10 up to the inlet 210, a portion of the watercourse 2 is artificially branched off and guided to the inlet 210. The basin 40 itself is then partially elaborated above ground while the water turbine 100 is embedded underground. The assembly is further elaborated such that the outlet 220 or 320 discharge further down¬stream into the watercourse 2. Again, the outlet 220 or 320 is preferably positioned under the water level of the watercourse 2. This embodiment requires more earthmoving and space than the first embodiment, but has the advantage that it is not subjected to the external forces of the water¬course 2. Hence, the assembly 1 needs to be dimensioned less firmly.
An advantage with the installation of assembly 1 according to the embod-iment, illustrated in Figures 1 to 4, is that the bottom 140 of the outlet 220

and hence, of the assembly 1 is flat. Hence, it is sufficient to provide a flat foundation on which the assembly can then be mounted. This is particular¬ly advantageous when the assembly 1 is installed in the watercourse be¬cause providing under water a recess for diffuser 330 is more complex than with a flat base plate 140.
According to a further embodiment, the maximum radius 42 is in the range of 1.5 m to 10 m, inclusive. Such a water turbine assembly is compact and can be installed without major work in, near, or in the vicinity of an existing watercourse.
The following dimensions can be used, for example, for the second em-bodiment of the assembly 1 according to Figures 12 and 13:
- a height of 1500 mm for the basin 40 and thus also for the inlet 210.
- a width of 2000 mm at the entrance of the inlet 210.
- a width of 700 mm at the inflow opening 60, i.e., the difference be-tween the radius 42 and 48 is 700 mm.
- a largest diameter of the basin 40 of 3600 mm, the distance of the 1st side 62 along the radius 42 to the opposite side of the basin is 3600 mm.
- the inner radius 112 of the turbine housing is 600 mm.
- the diameter of the rotor hub 122 near the rotor blades 124 is 480 mm.
- the total height of the assembly 1 is 2862 mm, i.e., from the top of the basin 40 to the bottom of the diffuser 330.
- the height of the outlet 320 is 450 mm and the width of the outlet 320 is 3000 mm.
In this manner, the water undergoes a total height difference of 500 mm. With such dimensions, one is able to realize a water turbine assembly wherein the total generated nominal electrical power of this assembly 1 may be 10 kW or more. In order to realize such a generated electrical power using known gravitational vortex water turbine assemblies, dimen-

sions should be used, in particular for the basin, which are, in general, a multiple of the dimensions mentioned above.
Figure 14 illustrates the simulated efficiency of different turbine assemblies as function of the flow rate. The flow rate is expressed in cubic meters per second. The efficiency is a percentage, determined in a test arrangement wherein the power that was used by a pump to generate a water flow with a particular flow rate, which was controlled by the inflow opening in a test¬ed embodiment of the gravitational vortex water turbine, was compared with the power generated by an electrical generator coupled to the turbine rotor. Curve 401 corresponds to an assembly 1 according to the embodi¬ment as illustrated in Figures 1 to 4, wherein use is made of a spiral-shaped basin. Curve 404 shows, for comparison, the efficiency of a known turbine assembly with a known turbine rotor having vertical turbine blades. Curves 402 and 403 show, respectively, the relative increase of the effi¬ciency due to the use of the optimized turbine rotor according to the em¬bodiment of, on the one hand, Figures 1 to 7, and on the other hand, Fig¬ures 8 and 9.
Figure 15 illustrates the nominal power of a water turbine assembly as function of the rotational speed of the rotor 120. The rotational speed is expressed in terms of the number of revolutions per minute (RPM) and the power is expressed in kilowatt (kW). Curve 501 corresponds to an assem¬bly 1 according to the embodiment as illustrated in Figures 1 to 7, wherein use is made of a spiral-shaped basin. Curve 504 shows, by way of com¬parison, the generated power of a known turbine assembly with a known rotor turbine having vertical turbine blades. Curves 502 and 503 show, respectively, the relative increase in the efficiency due to the use of the optimized turbine rotor according to the embodiment of, on the one hand, Figures 1 to 7, and on the other hand, Figures 8 and 9,.

Furthermore, it is also clear that the above described embodiments of the water turbine assembly can be coupled to an electrical generator and that this electrical generator can be controlled by means of an associated con-trol unit. The electrical generator may be coupled, for example, to the tur-bine rotor of the water turbine by means of a shaft or any other suitable mechanical coupling. Alternatively, the generator may also be integrated into the water turbine. In such an embodiment, for example, the rotor of the generator rotor is mounted in the turbine rotor and the stator of the generator in the turbine housing. The control unit of such a coupled gen-erator preferably makes use of an MPPT or Maximum Power Point Track-ing algorithm that may impose, by means of the control electronics, a vari-able load onto the generator, and thus also onto the turbine rotor. By means of this variable load and rotational speed of the turbine rotor, the impact velocity of the water flow on the turbine rotor can be controlled, and for the turbine rotor virtual, variable blade angles for the fixed turbine blades may be set, as it were. This allows to further optimize the efficiency to generate electrical energy by the water turbine assembly.
It is further apparent that both at the design of the water turbine assembly and at the controlling thereof, it is desired to limit the maximum relative velocity difference between the turbine blades and the water flow in the vortex during operation of the water turbine assembly. This may be real-ized, for example, by controlling the water turbine assembly such that the maximum relative velocity difference between the turbine blades and the water flow in the vortex does not exceed a predetermined maximum value during operation of the water turbine assembly. This predetermined maxi-mum value may be determined, for example, in function of bioparameters, such that, for example, fish survival can be ensured. This predetermined maximum value, for example, amounts to a value in the range of 0.5m/s to 5m/s, for example, 1 m/s.

Figures 15 and 16 shows an alternative embodiment similar to that de-tailed in Figures 1 and 2. Similar elements comprises similar references and generally function in a similar way as described above. However ac-cording to this embodiment the side wall 50 comprises a movable section 67 at the second side 64 of the inlet 210, configured to allow for a modifi-cation of the distance 48 between the second side 64 of the inlet 210 and the central axis of the turbine rotor 120, such that the alignment of the cen¬tral axis of the turbine rotor 120 and central axis 22 of the vortex 20 is modified, preferably such that the alignment of the central axis of the tur-bine rotor 120 and the central axis 22 of the vortex 20 is increased. It is clear that alternative embodiments are possible, but according to the em-bodiment shown this is implemented by making the movable section 67 rotatable about a suitable shaft 66 providing for a rotation axis 65 such that the second side 64 of the inlet 210 can be moved along the direction indicated with arrow 69. It is clear that the part 68 of the side wall to which the movable section 67 is rotationally coupled remains stationary. As shown, preferably the rotational axis 65 is parallel with the central rotation axis 22.
Figure 19 details an embodiment in which the rotor blades 124 cover an annular section around the central axis 22 of the vortex (20) which does not exceed the core zone of the vortex by more than 25%, and preferably does not exceed the core zone of the vortex by more than 20%. The re-spective radius 113 of the hub 122, radius 112 of the turbine rotor 120, radius 82 of the turbine housing 110 are shown in relation to the different zones of the speed profile of the vortex 20. As shown , the diameter of the hub 122 covers the low speed core zone of the vortex, the annulus cov-ered by the turbine blades 124 covers the high speed core zone of the vor¬tex which also excludes the low speed exterior zone of the vortex at the annulus between the diameter of the outlet opening and the diameter of the turbine rotor 120.

Figure 20 shows an alternative embodiment of a turbine rotor similar to that described with reference to Figures 5 to 7 and similar elements com-prise similar references, however this embodiment of the turbine rotor 120 also comprises a radially outward cylindrical shroud 127 coupled to the rotor blades 124, such that the cylindrical shroud 127 is rotated coaxially with the rotor blades 124 during rotation of the turbine rotor 120. Figures 21 and 22 show different views of a rotor blade 124, each comprising a respective shroud segment 127B coupled to its radial outer end, such that when all rotor blades 124 are mounted to the central hub 122, the respec¬tive shrouds segments 127B are coupled to each other thereby forming the cylindrical shroud 127. Such an embodiment is advantageous as it in¬creases structural rigidity of the turbine rotor, thereby reducing vibrations during operation, especially in the tangential direction. Additionally the cy¬lindrical shroud 127 interacts with the wall of the turbine housing 110 as a sort of labyrinth buffer, in which the enclosed water volume acts similar as a fluid bearing and/or damping element, thereby providing for additional vibration reducing effects. As further shown, according to this embodiment preferably the generator 122A is integrated into the hub 122.
It goes without saying that numerous variations and combinations of the above-described embodiments are possible that are within the scope of protection, as defined by the claims.

CLAIMS
1. A gravitational vortex water turbine assembly (1), comprising:
- a spiral-shaped vortex basin (40) configured to induce a vortex (20) in a water flow (10) under the influence of gravity, having a sub¬stantially vertical central axis (22), the vortex basin (40) comprising a side wall (50) with a tangential inflow opening (60) for supplying the water flow (10) to the vortex (20) and a bottom (70) with a central outflow opening (80) for discharging the water flow (10) of the vortex (20),
- a water turbine (100), disposed under the basin (40), coaxially with the central axis (22) of the vortex (20), comprising a turbine housing (110), coupled to the central outflow opening (80) and a tur¬bine rotor (120),
wherein the turbine rotor (120) comprises a central rotor hub (122) and rotor blades (124) attached thereon, and wherein the rotor blades (124):
- at an upstream end (126) have a smaller angle (126A) relative to the central axis (22) than the angle (128A) at the downstream end (128);
-at a radially inward end (125) have a larger angle (125A) rela-tive to a plane according to the central axis (22) than at a radially outward end (127); and
-at a radially inward end (125) have a smaller angle (125b) rel¬ative to a plane perpendicular to the central axis (22) than at a radial¬ly outward end (127),
such that the rotor blades (124) are configured to absorb the tangential, axial and radial component of the water flow (10) of the vortex (20).
2.A water turbine assembly (1) according to claim 1, characterized in that the side wall (50) extends downstream around the central axis (22) from a first side (62) up to an opposite second side (64) of the inflow opening ( 60), wherein the distance between the side wall (50) and the central axis (22) thereby decreases from a maximum radius (42) near the first side (62) to a minimum radius (48) near the second side (64) according to a downstream direction.
3.A water turbine assembly according to claim 1 or 2, characterized in that the minimum radius (48) is in the range of 50% to 85% of the maximum radius (42).
4.A water turbine assembly according to one or more of the claims 1 to
3,characterized in that the course of the distance of the side wall
(50) to the central axis (22) between the maximum radius (42) and
the minimum radius (48) occurs according to:
-a logarithmic spiral;
-a Bernoulli spiral;
-a Fibonacci spiral; or
-an Archimedes spiral.
5.A water turbine assembly according to one or more of the claims 1 to
4,characterized in that the side wall (50) comprises a plurality of
segments.
6.A water turbine assembly according to one or more of the claims 2 to
5,characterized in that the central outflow opening (80) of the bottom
(70) has a radius which is smaller than or equal to the minimum radi¬
us (48) of the side wall (50); and the inner radius (112) of the turbine
housing (110), near the turbine rotor (120), is in the range of 20% to
45% of the maximum radius (42) of the side wall (50).
7.A water turbine assembly according to one or more of the claims 1 to 6, characterized in that the downstream end of the turbine housing (110) comprises a diffuser (130, 330) configured to guide the water flow (10) in a direction having a component radially away from the central axis (22).
8.A water turbine assembly according to claim 7, characterized in that the diffuser (330) is further configured to guide the water flow (110) from a lowest position back upwards.
9.A water turbine assembly according to one or more of the claims 1 to
8,characterized in that the water turbine (100) is positioned at its
downstream end under the water surface.
10 A water turbine assembly according to one or more of the claims 1 to
9,wherein the number of rotor blades (124) is in the range of two to
ten, inclusive.
11.Water turbine assembly according to one or more of the claims 1 to
10,characterized in that the angle (126A) relative to the central axis
(22) at the upstream end is in the range of 0 ° to 45 °, and in that the
angle (128A) at the downstream end is in the range of 45 ° to 80 °.
12.Water turbine assembly according to one or more of the claims 1 to
11,characterized in that the water turbine assembly further compris¬
es:
-an electrical generator, coupled to the water turbine, or mounted in the water turbine;
-a control unit, coupled to the generatr, wherein the control unit is configured to control the rotational speed and the load of the generator and the therewith coupled turbine rotor of the water turbine during operation such that:
WO 2017/097943 PCT/EP2016/080349
36
-a Maximum Power Point Tracking Control is achieved; and/or
-a relative maximum velocity difference between the turbine blades and the water flow in the vortex does not exceed a predeter-mined maximum value.5
13. Water turbine assembly according to one or more of the claims 1 to 12, wherein:
-the radius (113) of the turbine central rotor hub (122) is larger than a pre-
determined minimum radius, the minimum radius being determined:
10- as a percentage in the range of at least 10%, for example in the
range of 15% to 50%, for example in the range of 20% - 30%, of the radius (112) of the turbine rotor (120) and/or of the tur¬bine rotor housing (110);
-as a percentage in the range of 10% to 65%, for example in the
15range of 15% to 50%, for example of the radius of the forced
vortex zone of the vortex; and/or
-such that the rotor blades (124) cover an annular section around
the central axis (22) of the vortex (20) which does not exceed
the core zone of the vortex by more than 25%, and preferably
20does not exceed the core zone of the vortex by more than 20%.
a water turbine (100); and/or
-The water turbine assembly further comprises an outlet (220, 320),
which is located below the water surface and is directed downstream;
-The radius of the turbine housing (110) is smaller than the maximum
25radius of the central outflow opening (80), and preferably the transition
between the turbine housing (110) and the central outflow opening (80) comprises a curved shape, such as for example a conical shape or hy¬perbolical shape with a rounded transition to straight ends; and/or
-The turbine rotor (120) comprises a radially outward cylindrical shroud
30(127) coupled to the rotor blades (124), such that the cylindrical shroud
(127) is rotated coaxially with the rotor blades (124) during rotation of the turbine rotor (120).
14.Water turbine assembly according to one or more of the claims 2 to
13, wherein:
-the side wall (50) comprises a movable section (67) at the second side
(64) of the inlet 210, configured to allow for a modification of the dis-tance (48) between the second side (64) of the inlet (210) and the central axis of the turbine rotor (120), such that the alignment of the central axis of the turbine rotor (120) and central axis (22) of the vor-tex (20) is modified, preferably such that the alignment of the central axis of the turbine rotor (120) and the central axis (22) of the vortex (20) is increased; and/or
-no intermediate guide vanes are positioned in or upstream of the inlet
opening (210).
15.Method for the manufacture of a turbine rotor (120) for use in a water
turbine assembly (1) according to one or more of the claims 1 to 14,
characterized in that the method comprises the following steps:
-simulation of the vortex (20) on the basis of the turbine as-sembly (1);
-determination of the axial, tangential and radial components of the vortex (20) near the water turbine (100);
-automatic generation of a shape for the rotor blades (124) on the basis of the axial, tangential and radial components of the vortex such that a minimum boundary layer separation near the rotor blades (124) occurs;
-manufacturing the generated shape of the rotor blades (124) by means of additive manufacturing techniques, for example, three-dimensional printing.
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