The invention relates to a machine to convert energy, e.g. a driven ship propeller (wherein also the so called bow propeller for directional control is meant) or a wind or water turbine with generator for generation of energy, e.g. electricity. Preferably this machine has a power in the range of one or a few or tens of Watts and many thousands or even more (e.g. in the range of kilowatt or megawatt) . An example is disclosed in DE-A-3 638 129. The invention can be disclosed in an electrical machine (e.g. with a stator and rotor ring) and can also be applied to different fields wherein e.g. two substantially co axial rings rotate relative to each other around a preferably axial axis. The object is a relatively high circumferential velocity of the rotor relative to the stator of the machine by providing the rotor at a maximised distance to the spinning axis. For that the machine becomes a system as two co axial rings that rotate relative to each other around the axial axis, wherein the rings contain the rotor and stator of the machine.

Preferably a so called shaftless machine is obtained, i.e. the bearing of the rotor ring, such as at the hub of a wheel, near its axial spinning axis is absent. And the in co operation with the driving or driven fluid operating blades (e.g. propeller- or turbine blades) preferably extend from the rotor ring in radial direction inwards (substantially comparable to a bicycle wheel wherein the spokes are replaced by the blades and the rim provides the rotor) . These blades are preferably at least partly supported by the rotor ring and move preferably along with the rotor ring and turn around the axial axis.

An example of such a machine can be found in the European patent, nr . 1 051 569 (Patentee: HydroRing B.V.). This disclosure offers further technical background for the invention, and its complete disclosure is incorporated in here by reference. Particularly this document discloses keeping the rotor ring in a desired position relative to the stator ring without the use of mechanical bearings, i.e. free of bearings or in other words floating journalling by making use of electromagnets of which the provided magnetic force is controlled by a control unit receiving signals from sensors which detect the position of the rotor ring relative to the stator ring. Thus a floating active journalling/positioning is provided such that the rotor ring turns around its axial axis with the least friction.

The invention particularly relates to a machine with preferably a high power capacity and preferably equipped with one or more of: a ring shaped stator ring, a ring shaped rotor ring turning inside or outside said stator ring; at least one blade mounted to said rotor ring and driving the fluid, such as liquid or gas (e.g. environmental air or water) or driven by it; magnetic means generating magnetic forces between the rotor ring and the stator ring, e.g. to aid in mutually located them in a predetermined position; means to detect a event which influences the position of at least a part of the rotor ring relative to the stator ring; means to control at least a part of the magnetic forces of the magnetic means, e.g. in dependence from the detection by the detection means to keep the rotor ring in a stable position relative to the stator ring; means, like a motor, to drive the rotor ring in rotation relative to the stator ring (the blade drives the fluid like the bow propeller application) and/or means, such as a generator, to take energy from the rotation of the rotor ring relative to the stator ring (the blade is driven by the fluid, like the generator application) . Preferably the magnetic means generate attracting and/or repelling magnetic forces between the rotor ring and the stator ring, e.g. to keep the rotor ring in a stable position relative to the stator ring. The magnetic forces preferably provide in that case that the shape stability of the stator ring and/or rotor ring is improved, preferably at least 10%, 20% or 25%.

The magnetic forces can be controlled by supplying more or less energy to the magnets. Alternatively the distance is changed between two magnets or between a magnet and an element attracted by it.

Thus preferably a magnetic field is used to at least partly journal (preferably axially and/or radially), or differently spoken during operation maintain the desired position or stability, respectively, of the rotor ring relative to the stator ring while the rotor ring turns around its axial axis with the least friction. Also from a magnetic field stemming magnetic forces are preferably used to improve during operation the static and/or dynamic stability of a rotor and/or stator ring, wherein e.g. the rotor and/or stator ring are mechanically stiffened, which offers many advantages, like the rotor and/or stator ring can have a light weight structure (e.g. of plastic, e.g. polymer material, possibly fibre reinforced, containing) . Adding stability can in the radial and/or axial direction of the rotor or stator ring. A lower limit is that the contribution of the magnetic field to the stability is clear or advantageous. Preferably due to said magnetic field the stability, e.g. flexural stiffness or shape stability of the rotor ring and/or stator ring increases with at least 10%, more preferably at least 20%, most preferably at least 25%. It is convenient if the rotor ring and/or stator ring are as flexible as possible, such that its stability is almost completely determined by the magnetic field. Since blades (if applied) or different to the rotor ring mechanically fixed parts (if used) can contribute to the stability in one or both directions, it is expected that the magnetic field offers the most advantages when stabilising in the direction which is not stabilised by said blades. In practise the diameter of the rotor ring and the stator ring can be large compared to the dimensions of the cross section of the rotor ring, e.g. wherein the diameter measures at least 3 times the axial dimension, preferably approximately at least 10 times the axial dimension of the rotor ring, such that a rotor ring is provided with a fairly unstable shape such that further stabilisation is required for long term economical use. On the other hand the rotor ring can be unstable at small ratios of the diameter/axial dimension if e.g. made of plastic material . Of the components (e.g. two magnets or a magnet and an element attracted by it) which cooperate to generate magnetic forces acting there between, the one is present at the rotor ring and the other at the stator ring.

Floating journalling/positioning of the rotor ring by means of controlled electromagnets requires relatively much energy, such that the efficiency of the machine suffers. Not only substantial energy loss is created since the electromagnets have to provide magnetic forces (e.g. 10% of the net power of the machine) , also a fast acting control of the electromagnets is required (e.g. position sensors are required which must react within milliseconds) .

According to WO2009/145620 this problem could partly or completely be solved by compensating at least a part of the by the environment at the rotor ring acting forces at least partly by preloads from one or more permanent magnets which can be mounted fixedly or displaceably and co operate with another magnet or an element attracted by it, which other magnet or element can be fixedly or displaceably mounted. Because of the displaceable mounting the mutual distance between the mutually co operating components can be changed, and with that the magnetic force generated by it. For the displacement the provision is made of displacement means which are connected to control means.

The forces acting by the environment onto the rotor ring are particularly the in axial direction active forces from the fluid driving the rotor or driven by it and the gravity force which is e.g. active in a direction normal to the axial direction if the machine is installed such that the axial direction extends horizontally.

A further energy saving can be obtained by in a further development of the invention mechanically journalling the rotor ring relative to the stator ring. By the magnetic preload one can provide that the mechanical bearing is low loaded, such that friction losses stay small. A further advantage of the mechanical bearing is the robustness; if the magnetic force vanishes the mechanical bearing maintains the position of the rotor ring, while in case of an axial floating bearing in such case the rotor ring immediately looses position and can thus be damaged or causes damage.

Within this proposal three basic designs for the axial positioning are feasible: (1) wherein the rotor ring is journalled to axially float by means of permanent magnets and electromagnets of which the power is controlled; (2) wherein the rotor ring is axially journalled by permanent magnets and mechanical journals; (3) wherein the rotor ring is journalled axially by permanent magnets, electromagnets of which the power is controlled and mechanical bearing. Electromagnets could be even absent. If electromagnets are applied it could in relation with the invention be sufficient if they are controlled by a relatively slow operating control (e.g. with a reaction time of a second or more), particularly in combination with a mechanical bearing. It has come out that the additional friction losses in the mechanical bearing by the slowness of the control of the electromagnets in general are sufficient small in duration such that the because of this caused losses are acceptable compared to the losses that would be caused when a fast control of the electromagnets is applied (such as required by a machine based on EP 1 051 569) .

It is preferred to generate with the by the rotor ring driven electrical generator or the the rotor ring driving electromotor, respectively, axially directed magnetic forces, more preferably substantially exclusively axially directed magnetic forces. The generator or motor, respectively, is preferably asymmetrically designed, such that a resulting axial magnetic force is generated by it, which can be used as magnetic preload. E.g. the permanent magnets at the rotor at the one axial side are located closer to the coil cores of the stator compared to the other axial side, or merely at one axial side of the rotor coil cores of the stator are located. This is further exemplified by the on the drawing based description.

E.g. can the rotor in the direction normal to the axial direction or the radial direction, respectively, be journalled by forces coming from mechanical bearings and/or permanent magnets (compensation of e.g. gravity force) . The forces from the environment which in this direction act on the rotor ring will generally not fluctuate such that a variation of the bearing forces, e.g. magnetic forces, in this direction is not required. The permanent magnets provided to generate magnetic forces in the axial direction and/or the direction normal to it/radial direction can be e.g. located in the Halbach-configuration, such that the magnetic forces are as much as possible concentrated at the one side of the magnets, which side is preferably facing to the ring onto which the magnetic forces must act .

Thus the magnetic bearing is preferably operative to at least partly decrease the load on the mechanical bearing, such that the mechanical bearing causes the least energy loss due to friction.

The mechanical bearing can be of any feasible type, e.g. comprise roller bearings or needle bearings. Most preferable is a slide bearing, preferably designed with slide faces with low coefficient of friction, such as Teflon (PTFE) or ceramic material. Application of water lubrication for the bearings is preferred.

With a mechanical bearing the play in the journals will generally be less than 1,5 or less than 0,5 millimetre. When a mechanical bearing is absent the play between a component of the rotor ring and stator ring will be at least 1,5 or at least 2,0 millimetre.

The inventor came to the conclusion that, without making any change to the elements of the machine providing the magnetic preload, the magnetic preload can be adjusted with the aid of the mechanical journalling of the rotor ring, such that merely variation is required within the mechanical journalling to optimise a for the rest identical machine for different nominal flow speeds of the fluid through the machine. Thus the machine becomes universally applicable for all appropriate locations in the world and merely adaptation to the mechanical journaling is required to adapt the machine to the locally prevailing nominal flow speed of the fluid to be able to guarantee maximised efficiency .

Preferably use is made of a machine in combination with a group of a plurality of mechanical bearing assemblies or bearing sets, wherein each bearing assembly of the group is adapted for integration in the machine, wherein the group is made of at least two or three or four sub groups each containing preferably the same number of bearing assemblies or sets, and preferably the number of bearing assemblies of all subgroups of the group together equals said plurality and of the group each time the bearing assemblies of a single sub group are required for simultaneous integration in the machine for reliable operation of the machine according to its design purpose and wherein each sub group provides a different positioning of the elements to provide the magnetic preload, or a different magnetic preload of said elements, if integrated in the machine (e.g. in that a dimension of the mechanical bearing assembly is each time different, yielding a different magnetic gap) . Preferably each bearing assembly of each sub group is identical to a bearing assembly of each other sub group in such a way, that they are completely exchangeable for integration into the machine. Preferably each bearing assembly of the group is designed such that merely mounting of it into the machine is required to provide the relevant positioning of the elements to provide the magnetic preload, in other words no adaption of the bearing assembly is required. E.g. the number of sub groups of the group equals the number of possible configurations of the machine, each configuration yielding a different magnetic preload. In that case each configuration is designed for a different nominal flow speed of the fluid flowing through the machine, and all sub groups contain an equal number of mechanical bearing assemblies.

It will be appreciated that the axial mechanical journalling of the rotor ring is particularly meant here. Thus a universal machine can, by selection of a mechanical bearing assembly or set of mechanical bearing assemblies from the group, be tailor made for the prevailing circumstances at a particular application location.

Preferably a single mechanical bearing assembly comprises all mechanical bearing components present at the same axial location . For simple mounting and exchangeability it is preferred that the mechanical bearing assemblies in the machine are present at an extreme radial outward position of the rotor ring and/or that a machine contains merely one mechanical bearing assembly . Now the invention is illustrated by way of embodiments. Fig. 1 shows a sectional side view of a principle example. Fig. 2 and 3 each show a sectional side view of a part of each time a different water turbine;

Fig. 4 shows the water turbine of fig. 3, after modification.

Fig. 1 shows schematically a machine served as a basis for the invention. A rotor ring 9 rotates within a stator ring 12. The propeller 8 drives the through the motor flowing fluid or is driven by said fluid. The blades of the propeller 8 are mechanically coupled with the stator ring 9 and extend from the rotor ring 9 (radially) inwards, towards the parallel to the axial direction extending spinning axis 11 of the ring 9. The ends of the blades facing away from the propeller 8 mutually merge or end at a mutual distance and have no additional bearing. Thus the blades are exclusively at their to the rotor ring 9 facing ends journalled. The fluid flows according to the arrow A through the machine which is e.g. completely submerged in the fluid.

The rotor ring 9 has a rotor 7 of an electrical machine and anchors 10 of magnetic means. The stator ring has electromagnets 2, 3, 4, 5 of magnetic means, connected to control means (not shown) and co operating with the anchors 10 to provide axial and/or radial forces to control the axial and radial, respectively, position of the rotor ring 9 relative to the stator ring 12. The stator ring 12 comprises the stator 6 of the electrical machine. Between stator 6 and rotor 7 there is a gap with a magnetic field of the electrical machine. Radial forces and weak axial forces are provided by parts of the magnetic circuits 2 and 3. Axial forces and weak radial forces are provided by parts of the magnetic circuits 4 and

5. The magnetic field in the gap 1 can generate radial forces if the rotor ring is not exactly centred relative to the stator ring, or accidentally, if the flows within the stator and rotor of the electrical machine azimuthally are not equally spread.

Thus the illustrated machine has no journalled, with the main axis (axial axis 11) covering, central physical axis and the blades 8 are merely journalled by the rotor ring 9 which is only magnetically journalled within the stator ring 11. Further embodiments are feasible, e.g. wherein the elements 7 and 10 do not project into the stator ring 12, such that elements 4 and 5 e.g. do not project out ring 12. Also elements 2, 3, 4 and 5 can be completely or partly be changed with respective elements 10. Or the magnetic means are provided by merely the stator 6 and the rotor 7 of the electrical machine. Fig. 2-4 are each taken at an arbitrary position along the circumference of the rotor ring and show in detail how the stator and rotor ring mutually fit, wherein a small piece of a with the rotor ring integrated blade 8 is shown. Shown for fig. 2-4 are the mechanical bearing blocks 13 of which the slide faces both in radial and axial direction have a for these bearings typical play of e.g. 0,5 millimetre. In the embodiment of fig. 4 the mechanical bearing is located furthest radially outward. Alternatively between the rotor and stator ring a play of approximately 2 millimetre in both axial and radial direction is present.

In fig. 2 the windings are shown of the coils belonging to the stator 6 to obtain electrical energy from turning of the rotor 7. These are wound around also to the stator belonging iron cores 10 (anchors) at both sides of a gap in which are present the permanent and in a fixed position mounted magnets of the part of the generator belonging to the rotor 7. These magnets keep to the iron cores to the left of it a distance tl of e.g. 1 millimetre and to the right of it a (relative to tl different, e.g. larger or smaller) distance t2 of e.g. 5 millimetre. Thus these magnets provide a to the left directed resulting, constant preload, opposite the to the right through the machine flowing water (arrow A) . By removing the iron cores to the right of these magnets, this preload can be enlarged. To the right of the generator 6, 7 in fig. 2 there are some sets of to the stator ring 12 in a fixed position mounted electromagnets 4, 5 at both sides of a gap inside which a to the rotor ring 9 mounted iron core 10 is present. Through a control unit with a the water force onto the machine detecting sensor the energy supply to these electromagnets 4, 5 is controlled to minimize the axial load of the mechanical bearings 13.

E.g. the by the generator provided axial preload is such that it counteracts 80% or 100% of the nominal axial force of the water flow onto the blades of the rotor. E.g. the machine can be designed such that from e.g. 30% of the nominal speed of the water flow through the machine, the water flow overrules the friction (static or dynamic) in the mechanical bearings such that the rotor ring starts turning and the generator generates electrical power. This generated power can be used to supply the electromagnets to lower the friction in the mechanical bearings such that more net power is generated. E.g. at a fluid velocity below the required velocity to equal the by the generator provided preload (generally below the nominal speed) the electromagnets have to exert an axial force in the direction of fluid flow of the water while at a velocity above said required velocity (generally above the nominal speed) , the electromagnets have to provide a force opposite the fluid flow direction to unload the mechanical bearings. In stead the generator exerts axial preload, one can provide that by a separate set of permanent magnets and magnetically co operating components.

Fig. 3 shows an embodiment based on fig. 2 with as most important modification compared to fig. 2 that electromagnets are removed and the set of iron cores and coils of the to the stator 6 mounted part of the generator are present at merely the upstream side of the permanent magnets of the to the rotor 7 mounted part of the generator. Thus the generator provides the axial magnetic preload which is directed opposite to the water flow through the machine. Since electromagnets are absent this preload can during operation not be varied and is thus constant.

The embodiments of fig. 2 and 3 each have two mechanical bearing assemblies; one in an axial upstream and one in an axial downstream position . The axial upstream bearing assembly holds the rotor ring in upstream direction; the axial downstream bearing assembly holds the rotor ring in downstream direction. The embodiment of fig. 4 has merely one single mechanical bearing assembly which is at a location radially furthest outward at the rotor ring and thus can easily be exchanged. This bearing assembly is provided at a single axial location and holds the rotor ring both in upstream and in downstream direction. The bearing component shown in fig. 4 is comprised from two parts: the one for holding in upstream, the other for holding in downstream direction.

For a generator a group of mechanical bearing assemblies is provided. All mechanical bearing assemblies belonging to the group have identical external dimensions and shape to be completely exchangeable. Contrary, for each bearing assembly of the group the location of the axial bearing faces of the two parts is different, such that the rotor ring can be located in an identical number of different axial positions relative to the stator ring by mounting of the relevant bearing assembly.

Thus, by exchanging the mechanical bearings the distance between rotor and stator of the generator can be adapted to adapt the mechanical preload to the local nominal flow speed of the water.

It will be appreciated that the machine is provided with a number circumferentially with equal spacing positioned mechanical bearing components, e.g. between four and twelve bearing components for each mechanical bearing assembly, such that the rotor ring is equally and stably journalled.

The invention also covers all other combinations from at least two of the in the description, drawing and/or claims disclosed measurements.