DE102018114768A1 - Electric machine assembly for a wind turbine - Google Patents

Abstract

An electric machine assembly for a wind turbine is disclosed. The electric machine assembly comprises a rotor shaft and at least one electric machine having a rotary body, wherein coupling means are provided which mechanically couple the rotor shaft and the rotary body of the respective electric machine in a first position for transmitting a rotational movement, wherein at least one stationary arranged frame is provided, wherein each rack accommodates a plurality of electric machines, preferably more than 5, more preferably more than 15, and wherein each electric machine received by the rack is positioned around the rotor shaft. Furthermore, the invention relates to a wind turbine with an electric machine assembly.

Description

The present invention relates to an electric machine assembly, in particular for a wind power plant, as well as a wind turbine with an electric machine assembly.

1. 1) Zum einen ist es bekannt, dass eine Rotornabe auf ein Getriebe mit einer Eingangs- und einer Ausgangswelle einwirkt, wobei die Ausgangswelle des Getriebes mit der Eingangswelle eines Generators bzw. einer Elektromaschine verbunden ist. Aufgrund der sehr hohen Eingangsmomente sind die Belastungen auf die einzelnen Zähne, die die Kräfte zwischen der Rotornabe und dem Getriebe übertragen, sehr hoch, so dass diese sehr massiv ausgeführt werden müssen. Weiterhin führen die Verformungen der Zähne während des Eingriffs zu Schwingungsanregungen. Diese Getriebe sind deswegen mehrstufig ausgeführt, da die Übersetzungsverhältnisse zur Ausgangswelle in der Größenordnung von 1 zu 50 liegen. Jedoch verschlechtert sich der Wirkungsgrad des Triebstranges aufgrund der Mehrstufigkeit des Getriebes und der damit verbundenen Reibung. Beide Faktoren (Übersetzungsverhältnis und Mehrstufigkeit) resultieren in schweren und aufwendigen Getrieben, so dass für große Windräder bzw. Windkraftanlagen diese Ausführung rückläufig ist.
2. 2) Zum anderen ist es bekannt, dass bei verschiedenen Ausführungen, bei denen die Rotornabe direkt mit dem Generator bzw. mit einer Elektromaschine verbunden ist, Nabe und Generator mit gleicher Drehzahl drehen. Für die hohen Eingangsdrehmomente müssen diese Generatoren mit einem großen Durchmesser ausgeführt werden (zum Beispiel Größenordnung 12 m). Aufgrund des großen Durchmessers der Direktgeneratoren muss der Luftspalt groß (in der Größenordnung mehrerer cm) ausgeführt werden, wodurch sich ein hoher magnetischer Widerstand und eine geringe Nutzung der magnetischen Erregung ergibt. Im Ergebnis wird beim Einsatz bzw. im Falle von Permanentmagneten für die Erregung viel magnetisches Material mit entsprechend hohen Kosten benötigt. Hinzu kommt, dass aufgrund der Abmessungen diese Generatoren masseintensiv sind.

Wind power plants with drive trains are known from the prior art according to the following principles, for example:

1. 1) First, it is known that a rotor hub acts on a transmission having an input and an output shaft, wherein the output shaft of the transmission is connected to the input shaft of a generator or an electric machine. Due to the very high input torques are the loads on the individual teeth that transmit the forces between the rotor hub and the gearbox, very high, so they must be made very solid. Furthermore, the deformations of the teeth during the procedure lead to vibration excitations. These transmissions are therefore designed in several stages, since the gear ratios to the output shaft in the order of 1 to 50. However, the efficiency of the drive train deteriorates due to the multi-stage transmission and the associated friction. Both factors (gear ratio and multistage) result in heavy and expensive gearboxes, so that this design is declining for large wind turbines or wind turbines.
2. 2) On the other hand, it is known that in various embodiments, in which the rotor hub is connected directly to the generator or to an electric machine, hub and generator rotate at the same speed. For the high input torques, these generators must be designed with a large diameter (for example, 12 m). Due to the large diameter of the direct generators, the air gap must be made large (on the order of several cm), resulting in a high magnetic resistance and little use of the magnetic excitation. As a result, in the use or in the case of permanent magnets for the excitation much magnetic material is required at a correspondingly high cost. In addition, due to the dimensions of these generators are mass-intensive.

It is accordingly the object of the present invention to provide an electric machine assembly and a wind turbine, which reduces the total mass and total costs, composed of generator or electric machine and transmission, and / or reduces or avoids torque fluctuations that can stimulate disturbing vibrations.

This object is achieved by the features of the independent claims.

Further advantageous embodiments of the present invention are the subject of the dependent claims.

According to the invention comprises in a first aspect of the present invention, an electric machine assembly, in particular for a wind turbine, a rotor shaft and at least one rotary body having electric machine, wherein preferably coupling means are provided, the rotor shaft and the rotary body of the respective electric machine in a first position for transmitting a Mechanically couple rotary motion with each other.

Preferably, at least one stationary arranged frame is provided. This is used to receive and forward of acting forces and moments.

Further, it is preferred that each rack house a plurality of electric machines, preferably more than 5, more preferably more than 15, each of the electric machines picked up by the rack being positioned around the rotor shaft.

By means of such a configuration, it is possible to use, for example, electric machines from the field of motor vehicles in, for example, a wind turbine. The use of a variety of electric machines in the field of motor vehicles and power generation from wind power creates the opportunity to use a cost-effective alternative to the existing electric machines in wind turbines and on the other by the modular design maintenance and repair easier to implement.

Automobile electric machines preferably have a weight of 100 kg, preferably a weight of 80 kg, preferably a weight of 60 kg, favorably a weight of 40 kg or preferably a weight of 20 kg.

It is also advantageous if the respective coupling means between the rotor shaft and the rotary body comprises either a rotating body side provided, rolling on the rotor shaft friction wheel or a rotor side provided gear and a rotating body side provided, standing in mesh with the gear pinion. Due to the fact that the pinion meshes with a gear wheel or rolls off the friction wheel on the rotor shaft, mechanical forces and moments can be removed from the rotor shaft and fed to an electric machine, e.g. B. designed as a generator supplied.

Further, it is preferable that each electric machine includes a torque input to receive a torque from the rotor shaft.

The torque input advantageously has the pinion or a generator pinion and / or an input shaft and / or a spacer element.

The spacer element, in particular designed as a spacer wheel, expediently serves to set the optimum distance between pinion or friction wheel and rotor shaft. For an exceeding or falling below the distance to be ensured by the spacer can lead to damage to the electric machine and / or the rotor shaft. This spacer can act as a reference variable to hold together with a contact force the distance of the teeth in the vicinity of a desired setpoint.

Furthermore, it is advantageous if the spacer element is designed as a sliding bearing or as a ball bearing, in particular with an outer and an inner ring and arranged therebetween rolling elements. Such a design reduces the friction between the spacer element and the rotor shaft or its gear.

Furthermore, it is provided that the rotor shaft is or can be under an axial load.

Preferably, the respective meshing connection between the pinion and gear is formed as a helical gear pairing.

It is also advantageous if each helical gear pairing between the pinion and the gear generates an axial force along the axis of rotation of the rotor shaft, wherein preferably all the axial forces generated by the helical gear pairings acting on the rotor shaft either cancel each other out or counteract the axial load. Thus, the acting, mechanical load can be easily compensated or compensated / compensated between rotor shaft and electric machine.

It is also advantageous if electrically, pneumatically, hydraulically and / or mechanically acting means are provided, which act at least on the coupling means and reciprocate them individually or in groups between the first position and a second, the coupling to the rotor shaft eliminating position , Thus, a controlled relative movement of an electric machine to the rotor shaft can be realized.

Preferably, the electrically, pneumatically, hydraulically and / or mechanically acting means comprises at least one actuator to actively vary the distance between an electric machine and the axis of rotation of the rotor shaft. In this way it is possible, for example, to maintain individual electric machines for maintenance purposes during the operation of an entire wind turbine without the wind turbine having to stand still. It is also possible by means of the means, for example, according to the wind power, which acts on a wind turbine, to switch on or off individual electric machines. Thus, therefore, a wind turbine can be optimally adjusted according to the wind power, so that in the result always a maximum of electrical energy from the acting wind force or from the acting wind power can be obtained.

Advantageously, the translation stage or the transmission ratio between the rotor shaft and the respective rotary bodies is greater than 20, greater than 50, greater than 100 or greater than 200. Thus advantageously z. B. the rotor shaft by a factor greater than 20, greater than 50, greater 100 or greater 200 more teeth than the pinion of an electric machine.

Furthermore, it is advantageous if a Nachführanordnung is provided, which preferably acts in the first position of the rotor shaft and coupling means on the respective coupling means and holds them at a constant radial distance to the lateral surface of the rotor shaft, with which the coupling means are coupled.

Furthermore, it is advantageous if the tracking arrangement is designed as a rotary suspension for the rotatable arrangement of an electric machine.

Furthermore, it is advantageous if the rotary suspension has a pivot about which an electric machine is rotatable or pivotable relative to the frame.

Preferably, the rotary joint of the rotary suspension or the Nachführanordnung is rotatable about an axis which is the same orientation to the axis of rotation of the rotor shaft of a wind turbine. In other words, it is thus possible for the rotary suspension, radially inward and / or to pivot radially outward to the axis of rotation of the rotor shaft. Concretely, this means that an electric machine of the electric machine module is made possible to vary the distance between the axis of rotation of the rotor shaft and a torque input of the electric machine. As a result, tolerances in the assembly of a wind turbine can be compensated in a simple manner and clearance between individual parts, in particular between an electric machine and the rotor shaft, are eliminated.

It is also advantageous if the rotary suspension or the tracking arrangement comprises a biasing spring by means of which an electric machine can be prestressed in one direction, in particular in the direction of a rotor shaft. In other words, the rotary suspension is enabled by means of a biasing spring to dynamically reduce or vary the distance between the axis of rotation of the rotor shaft and a torque input of the electric machine or the pinion / friction so always a constant distance from the lateral surface of the rotor shaft to keep. In this way, an optimal transmission of forces from the rotor shaft to an electric machine can be ensured.

It is also advantageous if the Nachführanordnung is designed as a linear suspension for linearly movable arrangement of an electric machine. So it is possible to move an electric machine along a straight line or a curved path.

Preferably, the linear suspension comprises a spring and / or damper element, along which an electric machine is linearly movable relative to the frame or relative to the axis of rotation of the rotor shaft. Conveniently, with the help of the linear suspension, an electric machine in one direction, in particular in the direction of the rotor shaft, can be prestressed. In other words, the linear suspension enables an electric machine to dynamically vary the distance between the rotational axis of the rotor shaft and a torque input of the electric machine or the pinion / friction wheel.

Conveniently, the linear suspension is displaceable along an axis or curved track, which is preferably oriented perpendicular to the axis of rotation of the rotor shaft. Thus, it is easily possible to vary the distance between an electric machine and the axis of rotation of the rotor shaft.

It can also be provided that at least one frame has a first row and a second row of electric machines.

Advantageously, the rotary bodies of the electric machines, which are combined in the first row, are arranged offset in the circumferential direction of the rotor shaft by an angular amount to the rotary bodies of the electric machines, which are summarized in the second row.

Also, the rotary body of the electric machines of the two rows can be arranged without displacement to each other, if the connection between the rotary body and torque input by means of an off-axis gearbox or a propeller shaft.

Furthermore, it is advantageous if a frame comprises at least two struts for holding the electric machines, wherein preferably the at least two struts receive and relay the mechanical forces and moments of the electric machines.

It is also advantageous if at least two struts accommodate at least two electric machines.

Furthermore, it can be provided that a frame comprises four struts for holding the electric machines. These struts form a sufficiently stable mechanical framework for receiving and transmitting mechanical forces.

Advantageously, two struts each receive at least two electric machines. Thus, it is advantageous if per rack two struts each accommodate at least two electric machines.

Conveniently, the frame has a first and a second strut and a third and fourth struts each for receiving electric machines.

Preferably, the electric machines are generators that are driven by the rotor shaft.

It is also preferable that the electric machines are electric motors that drive the rotor shaft.

Furthermore, it is favorable that the electric machines act individually or in groups with respect to each other with respect to their torque ripple phase-shifted on the rotor shaft. As a result, the excitation of the tower of a wind turbine can be reduced, which in turn is advantageous in terms of noise reduction.

A second aspect of the present invention includes a wind turbine.

It is expressly understood that the features of the electric machine assembly as mentioned in the first aspect can be used individually or in combination with each other in the wind turbine application.

In other words, the features mentioned above under the first aspect of the invention relating to the electric machine assembly can also be combined here with further features in the second aspect of the invention.

Of course, it is also possible to combine features of the wind turbine with features of the electric machine assembly.

Advantageously, a wind turbine comprises an electric machine assembly according to the first aspect.

Furthermore, it is preferred that the rotor shaft comprises a flange for connecting a rotor hub.

Conveniently, the rotor shaft is connectable to the rotor hub of the wind turbine.

Furthermore, it is favorable if the rotor shaft has stiffening rings, in particular at their axial ends. Thus, mechanical forces can be absorbed and relayed in a simple and weight-saving manner without the rotor shaft deforming.

Preferably, the rotor shaft is designed as a hollow shaft.

It is also preferred that the rotor shaft comprises at least one central gear or a gear or gear provided on the rotor side. By means of the central gear or the gear wheel, the torque acting on the rotor shaft can be transmitted to the electric machines.

Furthermore, it is possible for a central gearwheel to be arranged on the outside of the rotor shaft per frame.

Conveniently, the at least one central gear or the rotor side provided gear / gear in cross-section T-shaped.

It can also be provided that the at least one central gear comprises a toothing for combing with a torque input of an electric machine or with a pinion of an electric machine. In this way, torque can be transmitted from the rotor shaft to the electric machines of the electric machine assembly to convert mechanical energy into electrical energy.

Furthermore, it is preferred that the at least one central gear comprises a horizontal sub-element which has at its ends in each case a toothing for the power transmission to electric machines. By means of the toothing, it is possible to transmit a torque from the rotor shaft to the electric machines.

Preferably, the horizontal sub-element of the central gear on a left-hand toothing for a first electric machine and a right-hand toothing for a second electric machine. In this way, electric machines, which are arranged on the left and right sides of the central gear, pick up the torque of the rotor shaft. When using a helical toothing and an opposite skew of the left and right teeth, the axial forces of the electric machines on the left and right sides can compensate each other. Or with a suitable choice of the bevels results in a resulting axial force on the rotor shaft, which acts against the axial force on the rotor shaft on a flange of the rotor shaft. Further, it is preferable that the torque inputs of the electric machines arranged on the first and second braces are arranged on the one side of the central gear, and preferably the torque inputs of the electric machines arranged on the third and fourth braces on the other side of the central gear are arranged. In other words, it is favorable when the torque inputs or the pinion / friction wheel of the electric machines of the first / second strut and the third / fourth strut are arranged on respectively different sides of the central gear. As a result, thus preferably result in electric machines whose torque input interacts with the central gear, for example, at least two electric machines are arranged on the right side of the central gear and two electric machines on the left side of the central gear. Here, the term "left side" and "right side" is favorably referred to the central gear, which extends substantially in the radial direction and rotates about a rotation axis which is oriented in the axial direction.

Furthermore, it is advantageous if the at least one central gear wheel comprises a running surface for a spacer element of an electric machine. The spacer element helps to compensate for temperature expansions, elasticities, manufacturing and assembly tolerances between the rotor shaft of the electric machine assembly and a single electric machine or their torque input such that a toothing on a central gear and / or are operatively connected to a torque input of an electric machine with good efficiency and is not damaged. By means of the spacer element and the contact pressure, a desired engagement depth of the teeth is preferably largely maintained.

Preferably, a running surface for a spacer element is arranged between the two toothings (left and right toothing). Thus, therefore, the central gear with the tread a support surface for a spacer available, with the spacer can be supported on the support surface.

It is further preferred that the at least one central gear or the at least one gear provided on the rotor side comprises a vertical subelement for connection to the rotor shaft. By means of the vertical sub-element, a torque of the rotor shaft can be transmitted to the electric machines in a simple manner.

It is also possible that the Nachführanordnung acts on the central gear such that the torque of the rotor shaft is transmitted via the central gear to the electric machines to convert mechanical energy and electrical energy. In other words, it is advantageous if the Nachführanordnung or the biasing spring of the Nachführanordnung moves the electric machine in the direction of the central gear or presses or pressed. Thus, a connection between the rotor shaft and the individual electric machines can always be created, so that at any time a maximum of electrical energy can be obtained.

Advantageously, each electric machine includes a torque input that meshes with the teeth of the central gear to convert mechanical energy into electrical energy.

Hereinafter, the inventive idea presented above is expressed in other words in addition.

This idea preferably relates - in simplified form - to an electric machine assembly for a wind power plant, in which a plurality of electric machines are provided on a circumference of central gears, which are advantageously provided on a rotor shaft and preferably coupled to a rotor hub.

Advantageously, the electric machines are coupled to respective central gears using small pinions or torque inputs.

1. a) Vorteilhafterweise ist eine Rotornabe mit einer Rotorwelle verbunden und treibt diese an, so dass vorzugsweise Rotornabe und Rotorwelle mit gleicher Drehzahl drehen.
2. b) Auf der Rotorwelle ist vorzugsweise mindestens ein Zentralzahnrad / Zahnrad mit großem Außendurchmesser (z.B. ca. 3 m) und hoher Zähnezahl (z.B. 3163) angeordnet, welches günstigerweise von der Rotorwelle angetrieben werden.
3. c) Auf dem Umfang des mindestens einen Zentralzahnrads bzw. des mindestens einen Zahnrades ist vorzugsweise eine Vielzahl kleiner elektrischer Maschinen bzw. Elektromaschinen (z.B. aus E-Mobility Anwendungen) angeordnet, welche mittels eines Momenteneingangs bzw. mittels kleiner Ritzel (z. B. 31 Zähne) an das zugehörige Zentralzahnrad bzw. an das rotorseitig vorgesehene Zahnrad angebunden und als elektrischer Generator betreibbar sind.
4. d) Die einzelnen E-Maschinen bzw. jede Elektromaschine ist elastisch montiert, so dass diese einen radialen Positionsfehler der Verzahnung auf dem Zentralzahnrad ausgleichen können. Axiale Positionsfehler werden vorzugsweise mittels breiter Verzahnungen ausgeglichen.
5. e) Eine Anpassung an diverse Leistungen kann mittels Variation der Länge der Rotorwelle und Variation der Anzahl der Zentralzahnräder sowie Anzahl der E-Maschinen bzw. Elektromaschinen je Zentralzahnrad erfolgen.
6. f) Vorzugsweise hat die Zentralverzahnung eine Referenzkontur bzw. eine Referenzfläche bzw. eine Lauffläche für ein Distanzelement, welche in radialer Richtung zur Verzahnung auf dem Zentralzahnrad bemaßt ist.
7. g) Mittels eines Distanzelementes wird vorzugsweise auf Basis der Referenzkontur der Abstand zwischen den Verzahnungen bzw. die Eingriffstiefe der Verzahnungen nahe einem Sollwert gehalten, wobei vorzugsweise ein kleines Verzahnungsmodul verwendet werden kann, so dass das Verzahnungsmodul günstigerweise klein im Verhältnis zum Durchmesser des Zentralzahnrades gewählt werden kann, insbesondere in einer Größenordnung kleiner 1/50, kleiner 1/100, kleiner 1/200, kleiner 1/500, kleiner 1/1000, kleiner 1/2000.
8. h) In der Folge kann dann zusammen mit dem Generatorritzel mit nur einer Übersetzungsstufe eine Übersetzung größer 20, größer 50, größer 100 oder größer 200 erreicht werden kann.

In other words, a wind turbine with a drive train is preferably created according to the following principle:

1. a) Advantageously, a rotor hub is connected to a rotor shaft and drives it, so that preferably rotor hub and rotor shaft rotate at the same speed.
2. b) On the rotor shaft is preferably at least one central gear / gear with a large outer diameter (eg, about 3 m) and a high number of teeth (eg 3163) are arranged, which are favorably driven by the rotor shaft.
3. c) on the circumference of the at least one central gear or the at least one gear is preferably a plurality of small electric machines or electric machines (eg from e-mobility applications) arranged, which by means of a torque input or by means of small pinion (eg 31 Teeth) connected to the associated central gear or to the rotor-side provided gear and are operable as an electric generator.
4. d) The individual electric machines or each electric machine is elastically mounted so that they can compensate for a radial position error of the toothing on the central gear. Axial position errors are preferably compensated by means of wide teeth.
5. e) An adaptation to various services can be done by varying the length of the rotor shaft and variation of the number of central gears and number of E-machines or electric machines per central gear.
6. f) Preferably, the central toothing has a reference contour or a reference surface or a running surface for a spacer element, which is dimensioned in the radial direction to the toothing on the central gear.
7. g) By means of a spacer element is preferably kept based on the reference contour of the distance between the teeth or the depth of engagement of the teeth near a desired value, preferably a small toothing module can be used, so that the toothed module are favorably chosen small in relation to the diameter of the central gear can, in particular in the order of less than 1/50, less than 1/100, less than 1/200, less than 1/500, less than 1/1000, less than 1/2000.
8. h) As a result, together with the generator pinion with only one gear ratio, a ratio greater than 20, greater than 50, greater than 100 or greater than 200 can be achieved.

Due to the large diameter of a central gear and the small pinion of a torque input of the individual electric machines or electric machines is conveniently achieved in only one stage, a very high speed translation, so that preferably the small electric machines rotate much faster (about factor 100 ) as the main shaft or the rotor shaft.

Due to the large number of small electrical machines, each with its own tooth connection to the respective central gear, preferably each tooth connection only a fraction of the torque transmitted from the rotor hub, so that the individual teeth are exposed to only low loads.

By preferably the phases of the torque ripples of the individual electric machines are arranged offset from each other selectively, preferably results in a total excitation with extremely low excitation amplitude and very high order. These are easier to control.

• 1 eine 3-D-Ansicht einer Elektromaschinenbaugruppe;
• 2 einen Schnitt der Elektromaschinenbaugruppe;
• 3 ein Teil der Elektromaschinenbaugruppe ohne Rotorwelle;
• 4 einen Teilbereich der Elektromaschinenbaugruppe;
• 4a einen Schnitt durch eine Elektromaschine;
• 5 die Elektromaschinen einer Elektromaschinenbaugruppe ohne Rotorwelle und ohne Abstützungen;
• 6 einen umrandeten Ausschnitt aus 6 vergrößert;
• 7 einen Schnitt entlang eines Ritzels einer der Elektromaschinen;
• 8 einen Schnitt entlang eines Ritzels einer der Elektromaschinen ohne Halterung;
• 9 ein Detail Ritzel und Distanzrad; und
• 10 Prinzip einer Kompensation der abweisenden Verzahnungskräfte.

The present invention will be described below with reference to the description of an embodiment with reference to the accompanying drawings. Here are shown schematically:

• 1 a 3-D view of an electrical machine assembly;
• 2 a section of the electric machine assembly;
• 3 a part of the electric machine assembly without rotor shaft;
• 4 a portion of the electric machine assembly;
• 4a a section through an electric machine;
• 5 the electric machines of an electric machine assembly without rotor shaft and without supports;
• 6 an outlined section 6 increased;
• 7 a section along a pinion of one of the electrical machines;
• 8th a section along a pinion of one of the electric machines without a holder;
• 9 a detail pinion and spacer wheel; and
• 10 Principle of compensation of the repulsive toothing forces.

Below is the description of an embodiment.

It will open 1 to 10 directed.

In the following description, like reference characters will be used for like items.

1 a 3-D view shows an electrical machine assembly 1 ,

Shown in more detail, shows 1 that the electric machine assembly 1 a rotor shaft 2 and various electrical machines 3 Has.

Here are the electric machines 3 each a rotating body 4 on. An electric machine 3 with a rotating body 4 is in 4a shown schematically. The rotary body 4 , is -as with electric machines 3 - Usually a rotor 4.1 that of a wave 4.2 rotatable in the housing 3.1 the electric machine 3 stored. The looking up 4a left, out of the case 3.1 protruding part of the shaft 4.2 , which in the following also as input shaft 17 or momentary input 16 is called, carries a pinion 6 and a spacer 18 , which will be discussed in more detail in the further description.

Also has the electric machine assembly 1 coupling agent 5 . 6 (in 1 not shown), the rotor shaft 2 and the rotary body 4 the respective electric machine 3 mechanically couple together in a first position to transmit a rotational movement. This situation will be explained in more detail and vividly in the further description.

In 1 It can also be seen that the electric machine assembly 1 also several stationary arranged racks 7 includes, each frame 7 a plurality of electric machines 3 picking up, and taking each from the rack 7 recorded electric machine 3 around the rotor shaft 2 is positioned around.

Below is 1 further described.

The electrical machine assembly 1 exists, like 1 shows, from a main shaft 2 or a rotor shaft 2 extending over the entire length of the electrical machine assembly 1 extends.

Along this main shaft 2 or rotor shaft 2 are several racks 7 arranged. Every rack 7 includes several individual electrical machines 3 , which around the rotor shaft 2 are arranged around and through the rotor shaft 2 be driven and attached to a rack 7 support.

The individual racks 7 are attached to the housing (not shown) or a structure of the nacelle (not shown) and are supported on this.

In the after 1 shown illustration has the electrical machine assembly 1 six racks 7 , with each rack 2x20 electrical machines 3 includes.

It should be noted that this is just an exemplary embodiment and the number of racks 7 and the electric machines 3 each frame can be varied.

On a flange 10 at the front end of the main or rotor shaft 2 the connection to a rotor hub (not shown) takes place.

2 shows a section of the electrical machine assembly 1 ,

More specifically, is in 2 the electrical machine assembly 1 together with the rotor shaft 2 and various racks 7 shown cut.

It can be seen that the rotor shaft 2 various stiffening rings 11 , in particular at the axial ends of the rotor shaft 2 , wherein the rotor shaft 2 is designed as a hollow shaft.

Further shows 2 that the rotor shaft 2 at the one end, at which the flange 10 for a rotor hub (not shown) is mounted, a radial bearing assembly 13A and at the opposite or other end of an angular contact ball bearing assembly 13B having.

Between the two ends of the rotor shaft 2 are the racks 7 arranged at regular intervals.

According to 2 has each rack 7 various electrical machines or electrical machines 3 for generating electrical energy.

The electric machines 3 are doing so on a frame 7 arranged that a torque of the rotor shaft 2 using the electric machines 3 is convertible into electrical energy.

Furthermore goes out 2 produced that every frame 7 four struts 12A . 12B . 12C . 12D to hold the electric machines 3 includes.

Described in more detail, rejects each rack 7 a first 12A and a second brace 12B and a third 12C and fourth brace 12D each for receiving electric machines 3 on.

Thereby - as already mentioned - each two braces 12A . 12B or. 12C . 12D various electrical machines 3 on.

The struts 12A . 12B . 12C . 12D have the task, mechanical forces and moments of electric machines 3 and the rotor shaft 2 to record and forward.

Below is 2 further described.

Visible is in 2 again the rotor shaft 2 with the flange 10 for the connection of a rotor hub (not shown).

Furthermore, the bearing of the rotor shaft is an example 2 shown.

Near to the flange 10 The rotor hub high radial forces must be absorbed and storage by roller bearings 13A or a radial bearing arrangement 13A ,

In the vicinity of the opposite end significantly lower radial forces occur, still have the axial forces are absorbed. This is done z. B. by means of two angular contact ball bearings 13B or by means of an angular contact ball bearing arrangement 13B , which can accommodate radial and axial forces / can.

In the field of bearings 13A . 13B or the bearing arrangements 13A . 13B are stiffening rings 11 for the rotor shaft 2 shown. Because of this storage, the individual bearings 13A . 13B record little or no tilting moments, preferably the individual bearings 13A . 13B allow a small degree of tilting freedom (eg in execution as self-aligning ball bearings, spherical roller bearings, etc.). This makes it possible alignment errors but especially elastic deformation of the rotor shaft 2 to balance during operation.

At the six racks 7 is the arrangement of the individual electric machines 3 in the individual racks 7 visible in two groups each.

Part of the electrical machines 3 is in the left half (formed by the struts 12A . 12B ) and the other part in the right half (formed by the struts 12C . 12D ) of the racks 7 ,

The area "A" is in 7 presented with more details.

3 shows a single frame 7 without main shaft or rotor shaft 2 ,

The frame 7 has according to 3 various electrical machines 3 for generating electrical energy.

The electric machines 3 are doing so around the rotor shaft 2 arranged that a torque of the rotor shaft 2 using the electric machines 3 is convertible into electrical energy.

At the rotor shaft 2 , in the 3 not shown is a gear 5 or a central gear 5 arranged to the torque acting on the rotor shaft 2 interacts with the electrical machines 3 transferred to.

Furthermore, in 3 the axis of rotation D represented by which the rotor shaft 2 as well as the gear 5 / Central gear 5 rotate.

Furthermore, in 3 to recognize that between the struts 12A . 12B . 12C . 12D , each a stiffening wreath 14 is arranged for further mechanical stabilization.

Below is 3 further described.

Every frame 7 is a central gear 5 or a gear 5 assigned, which of the main shaft 2 or the rotor shaft 2 is driven and on the rotor shaft 2 stored or attached.

Right and left of the central gear 5 are on the circumference (around the axis of rotation D the rotor shaft 2 around - marked with circumferential direction U ) in each case several individual electric machines 3 . 3A . 3B arranged.

The individual electric machines 3 a frame 7 be on a generator bracket or on the struts 12A . 12B . 12C . 12D of the frame 7 mounted / supported. In the embodiment shown here, there is the generator bracket or the frame 7 - As already mentioned - from several struts 12A . 12B . 12C . 12D , which among themselves by means of connecting or stiffening rings 14 are connected.

4 shows a portion of the frame 7 ,

In the mentioned figure is as well as in 4a shown that the electric machine assembly 1 Coupling means has the rotor shaft 2 and the rotary body 4 the respective electric machine 3 mechanically couple together in a first position to transmit a rotational movement. In the execution according to 4a this is so realized that the shaft 4.2 directly with a pinion 6 is provided, which provided with a rotor side gear 5 (in 4a not visible) is in combative connection.

This goes out 4 It also shows that the electric machine assembly 1 a tracking arrangement 9 for the movable arrangement of an electric machine 3 . 3A . 3B relative to the frame 7 includes.

In the specific case after 4 is the tracking arrangement 9 as a rotary suspension for the rotatable arrangement of an electric machine 3 . 3A . 3B educated.

Described in more detail, has the tracking arrangement 9 or the rotary suspension a swivel joint 9.1 to which an electric machine 3A . 3B relative to the frame 7 or relative to the struts 12A . 12B . 12C . 12D The frame is pivotable 7 form.

The rotational movement of an electric machine is an example of one of the electric machines 3B on the right side of the gear 5 or central gear 5 with the help of a double arrow S shown.

The swivel joint 9.1 the tracking arrangement 9 is rotatable about an axis which is to the axis of rotation D the rotor shaft 2 equals.

As 4 shows, has the Nachführanordnung 9 Further, a biasing spring 15 on, with whose help an electric machine 3A . 3B in one direction, especially in the direction of the rotor shaft 2 , can be prestressed.

Although not shown in the figures, it is mentioned for the sake of completeness that electrically, pneumatically, hydraulically and / or mechanically acting means can be provided, which at least on the coupling means 5 . 6 (Central gear 5 and pinion 6 ) act and these individually or in groups between the first position and a second, the coupling to the rotor shaft 2 back and forth.

Thus, therefore, the distance between an electric machine or an electric machine 3 . 3A . 3B and the axis of rotation D the rotor shaft 2 be actively varied. This also allows temperature expansion, elasticity, manufacturing and assembly tolerances between the rotor shaft 2 and a single electric machine 3 easy to compensate. This also makes it possible, individual electric machine 3 depending on wind power of a wind turbine to switch on or switch off or even individual electric machines 3A . 3B to maintain or replace this without the entire electrical machine assembly 1 must be disabled.

Alternatively to a rotary joint of the Nachführanordnung 9 it is also possible, the Nachführanordnung 9 as a linear suspension for the linearly movable arrangement of an electric machine 3 . 3A . 3B train.

In such a case, conveniently, the linear suspension has a spring and / or damper element along which an electric machine 3 . 3A . 3B relative to the frame 7 is linearly movable.

It is also preferred if the linear suspension is displaceable along an axis, which is preferably perpendicular to the axis of rotation D the rotor shaft 2 is oriented.

Below is 4 further described.

Visible is in 4 again the gear or the central gear 5 with the electric machines 3A . 3B which left ( 3A ) and right ( 3B ) of the central gear 5 along the circumference U are arranged.

The individual electric machines 3A . 3B are not rigid with the frame 7 attached, but flexible, so that the input shafts or torque inputs of the electric machines 3A . 3B can perform a radial movement to position error of a toothing on the central gear 5 compensate.

The causes of these position errors can z. As: concentricity error, thermal expansions of the teeth on the central gear 5 , Bends of the rotor shaft 2 , Etc.

In the embodiment shown here, this is exemplified by each electric machine 3A . 3B a rotary body 4 has and by means of a rotary joint 9.1 is attached, which in the direction of contact U laterally offset to the input shaft or to the torque input of the electric machine 3A . 3B is arranged.

A turn in the hinge 9.1 , allows a pivoting movement (indicated by the double arrow S ) of the input shaft or moment input (in 4 not visible) of the electric machine 3A . 3B around the hinge 9.1 , This causes in this embodiment mainly a movement radially to the circumferential direction U ,

By means of a support (not visible in this figure), preferably coaxial to the input shaft or to the moment input (not in 4 visible) of the electric machine 3A . 3B the electric machine is supported 3A . 3B at the central gear 5 from, wherein by means of the biasing spring 15 the supporting force can be adjusted.

The swivel together with the support on the central gear 5 and the biasing spring 15 together make a clear positioning of the input shaft and the torque input of the electric machine 3A . 3B relative to the circumferential plane of the central gear 5 for sure.

By means of the spring force of the preload springs 15 the individual electric machines 3A . 3B will ensure that all electrical machines 3A . 3B a similar contact force for support on the central gear 5 respectively.

Due to gravity is for a similar contact pressure of the individual electric machine 3A . 3B against the central gear 5 , depending on the location of the individual electric machine 3A . 3B on the circumference, a different spring force of the biasing spring 15 necessary.

Alternative to the preload springs 15 can also be an active contact pressure or distance positioning, such as by means of an actuator or an electrically, pneumatically, hydraulically and / or mechanically acting means executed.

This still gives the possibility of individual electric machines 3A . 3B if necessary in a position without contact with the central gear 5 to proceed. This fulfills the function of a controllable coupling between the individual electric machine 3A . 3B and the rotor shaft 2 so that the individual electric machines 3A . 3B individually or as groups if necessary from the drive train or from the rotor shaft 2 can be connected or disconnected.

This is z. B. in order to adapt the number of active electric machines depending on the currently required generator power or depending on the current wind conditions necessary. Furthermore, a targeted decoupling of individual electrical machines 3A . 3B performing maintenance on these without interrupting the operation of the entire system.

In the case of an active distance positioning or a movement device with an actuator or with an electrically, pneumatically, hydraulically and / or mechanically acting means per electric machine, it is possible to detect the current toothing position by means of sensors and the electric machines 3A . 3B accordingly active positioning.

An active contact pressure / bias can z. B. by means of a pneumatic or hydraulic cylinder or by means of an electrically, pneumatically, hydraulically and / or mechanically acting means supporting parallel or alternatively to the biasing spring 15 or to Nachführanordnung 9 will be realized.

Alternatively or additionally, the biasing spring 15 by means of an electric, pneumatic, hydraulically and / or mechanically acting means are actively changed in their bias and thus a lifting of a pinion or the torque input of an electric machine 3A . 3B from the central gear 5 be enforced.

A re-meshing during operation can be achieved by the electric machine is first accelerated to a synchronous speed (so that the teeth of the pinion or the torque input and the teeth of the central gear 5 Move approximately equally fast / synchronously to each other and only then by swinging the electric machine 3A . 3B the pinion or the torque input again in tooth contact with the central gear 5 is brought.

In summary, therefore 2 to 4 that the electric machine assembly 1 with a rotor shaft 2 and with various rotating bodies 4 having electrical machines 3 . 3A . 3B Is provided.

Also are coupling agents 5 . 6 provided, concerning 5 to 9 to be explained in more detail, the rotor shaft 2 and the rotary body 4 the respective electric machine 3 . 3A . 3B mechanically couple together in a first position to transmit a rotational movement.

Also includes the electrical machine assembly 1 several fixed racks 7 where each frame 7 a plurality of electric machines 3 . 3A . 3B picking up, and taking each from the rack 7 recorded electric machine 3 . 3A . 3B around the rotor shaft 2 is positioned around.

5 shows the electric machines 3A . 3B a frame 7 without central shaft 2 or rotor shaft 2 and without supports 12A to 12D or struts 14 ,

For illustration, therefore, are the central shaft 2 or rotor shaft 2 and the struts 12A to 12D for the electric machines 3A . 3B hidden.

Otherwise, the same elements are visible, which have already been described in the preceding figures.

More details on the execution will be in 6 represented or described.

6 shows the outlined section of the 5 increased.

As you can see, every electric machine has 3A . 3B a moment entrance 16 to a torque from the rotor shaft 2 to tap and convert into electrical energy.

Furthermore, as already mentioned, the electric machine assembly has 1 coupling agent 5 . 6 that the rotor shaft 2 and the rotary body 4 the respective electric machine 3 . 3A . 3B mechanically couple together in a first position to transmit a rotational movement.

According to 6 includes the respective coupling agent 5 . 6 between rotor shaft 2 (not shown) and rotary body 4 a gear provided on the rotor side 5 or the central gear 5 and a rotating body side provided, with the gear 5 in meshed pinion 6 ,

In other words, the moment input includes 16 a pinion 6 or a generator pinion 6 , an input shaft 17 and a spacer 18 ,

Here is the spacer element 18 designed as a ball bearing, with an outer 18A and an inner ring 18B and arranged therebetween rolling elements (see also 9 ).

The spacer element 18 or the spacer wheel serves to the distance of a tread 19 of the central gear 5 to a rotation axis of the moment input 16 not to fall below. Because falling below a minimum distance from the spacer 18 is to be ensured, can damage the teeth of the moment input 16 or the pinion 6 an electric machine 3 . 3A . 3B and at the teeth of the central gear 5 to lead.

Alternatively, it is possible that the spacer element 18 is designed as a sliding bearing.

Also is in 6 the tracking arrangement 9 shown, designed with a swivel joint 9.1 and a biasing spring 15 ,

The tracking arrangement 9 causes the torque of the rotor shaft 2 over the central gear 5 on the electric machines 3A . 3B is transferred to convert mechanical energy into electrical energy.

This meshes with the moment input 16 an electric machine 3A . 3B or the pinion 6 with the teeth 5A . 5B of the central gear 5 in order to convert a mechanical torque into electrical energy, as already described.

Again described in other words, shows 6 in that the tracking arrangement 9 in the first position of rotor shaft 2 and coupling agents 5 . 6 to the respective coupling agent 5 . 6 acts and this in a constant radial distance to the lateral surface of the rotor shaft 2 holds, with which the coupling agent 5 . 6 are coupled.

Furthermore, in the synopsis of 5 and 6 to recognize that a frame 7 a first row and a second row of electric machines 3 . 3A . 3B has and that the rotary body 4 the electric machines 3A , which are summarized in the first row, to the rotating bodies 4 the electric machines 3B , which are summarized in the second row, in the circumferential direction U the rotor shaft 2 offset by an angular amount are arranged.

Below is 6 further described.

The electric machines 3A . 3B are by means of a swivel joint on the frame 7 or by means of the tracking arrangement 9 on the frame 7 attached so that the input shaft 17 or the moment input 16 the electric machines 3A . 3B can perform a pivoting movement. This pivotal movement allows one to the axis of rotation or to the axis of rotation D the rotor shaft 2 radial degree of freedom of the input shaft 17 or the momentary input 16 the electric machines 3A . 3B ,

The central gear 5 has a right 5B and a left gearing 5A on. The individual electric machines 3A . 3B have - as already mentioned - input shafts 17 on, on which externally toothed pinion 6 or generator gear 6 are arranged.

The individual sprockets 6 Teeth or comb with the right 5B or the left teeth 5A of the central gear 5 , By means of these tooth engagement drives the central gear 5 the electric machines 3A . 3B on.

The spacer wheels or spacer elements 18 for the electric machines 3A on the left side or on the left-hand side 5A as well as the spacer wheels or spacer elements 18 for the electric machines 3B on the right side or sides of the right teeth 5B run on a common tread 19 of the central gear 5 ,

The tread 19 on the central gear 5 has a defined height to the teeth "left" 5A and "right" 5B on the central gear 5 , The spacer wheels 18 or the spacer elements 18 have on their outer contour in each case a largely constant radius to the axis of rotation of the pinion 6 on the input shaft 17 of the moment entrance 16 the electric machine 3A . 3B ,

By the spacer wheels 18 or spacer elements 18 with her outer contour on the tread 19 support the gears 5A . 5B of the pinion 6 and the central gear 5 a largely constant distance.

The force with which the spacer wheels 18 on the tread 19 of the central gear 5 is supported by the biasing spring 15 set. The flexible mounting by the Nachführanordnung 9 with swivel ensures the necessary degree of freedom.

7 shows a section along the input shaft 17 or the momentary input 16 one of the electrical machines 3A ,

The statements concerning the 5 and 6 of course, also meet 7 to, where 7 describes some aspects in more detail.

So is 7 to see that per frame 7 on the outside of the rotor shaft 2 a central gear 5 is arranged, which is T-shaped in cross section.

Here has the central gear 5 a horizontal sub-element for connection to the electrical machines 3A . 3B and a vertical sub-element for connection to the rotor shaft 2 ,

The horizontal sub-element of the central gear 5 has at its ends in each case a toothing 5A . 5B for force transmission to electric machines 3 . 3A . 3B on, wherein the horizontal sub-element a left-hand toothing 5A for a first electric machine 3A has and a right gearing 5B for a second electric machine 3B ,

Named gearing 5A . 5B of the central gear 5 serves combing with a moment input 16 or with the pinion 6 an electric machine 3A . 3B ,

Furthermore, the toothing extends 5A . 5B of the central gear 5 in the radial direction R outward.

Also has the central gear 5 - As already described to the preceding figures - a tread 19 for a spacer element 18 an electric machine 3 . 3A . 3B where between the two gears 5A . 5B the tread 19 for a spacer element 18 is arranged.

Furthermore, it should be mentioned, but not what 7 it can be seen that the rotor shaft 2 is under an axial load, and that the respective meshing connection between pinion 6 and gear 5 or central gear 5 is designed as a helical gear pairing.

Each helical gear pair between pinions 6 and central gear or gear 5 generates an axial force along the axis of rotation D the rotor shaft 2 , all of which are generated by the helical gear pairings, on the rotor shaft 2 acting axial forces either cancel each other or counteract the axial load.

According to the present embodiment 4 is the translation stage between rotor shaft 2 and the respective rotating bodies 4 greater 100 ,

Below is 7 further described.

The in 7 section shown extends along a plane which, through the axis of rotation of the input shaft 17 of the moment entrance 16 the electric machines 3A and through the axis of rotation D the rotor shaft 2 runs.

The electric machine 3A is outlined only as an outline, since this structure is independent of the type of electric machine. It is possible to use PMSM, FPD, ASM and double fed ASM and other types of electric machines. Preferably, an electric machine is used from the electromobility, as they are cheap available due to increasing quantities and have high availability due to the high quality requirements of the automotive industry.

In particular, the here as an electric machine 3A . 3B also designate other units (such as an integrated transmission). An integrated transmission allows, for example, a further speed adjustment between the rotary body 4 an electric machine 3A . 3B and the input shaft 17 or the momentary input 16 the electric machine 3A . 3B ,

In a version with an integrated gearbox, the input shaft to the electric machine 3A . 3B and the axis of rotation of the rotor is no longer concentric and not parallel to the axis, but the axis of rotation of the rotor and the axis of rotation of the generator pinion 6 or the pinion 6 to the central gear 5 can also be executed parallel to the axis or askew.

The central gear 5 which is on the rotor shaft 2 is fixed, has a - as already mentioned - left 5A and right teeth 5B on. Between the two gears 5A . 5B there is a tread 19 or a reference surface for the spacer wheels or spacer elements 18 which gives a constant spacing of the gears 5A . 5B of the central gear 5 and the pinion 6 on the input shaft 17 the electric machine 3A . 3B ensures.

This reference area 19 or tread 19 can also be arranged differently, important is preferably a constant relative distance to the teeth of the central gear 5 ,

The toothing of the pinion 6 is on the input shaft 17 the electric machine 3A . 3B significantly wider than the teeth 5A . 5B on the central gear 5 ,

The wide pinion 6 allows a compensation of position deviations in the axial direction A between the rotor shaft 2 and the position of the electric machines 3A . 3B or between that with the gear 5 meshing pinion 6 , These occur forcibly due to thermal expansion, elasticity, manufacturing and assembly tolerances.

As 7 shows, is the spacer or spacer 18 at the electric machine 3A fastened and rests on the tread 19 of the central gear 5 and thus provides a largely constant distance between the input shaft 17 the electric machine 3A to the toothing 5A on the central gear 5 for sure.

The tread 19 on the central gear 5 is made wide to compensate for positional deviations in the axial direction A between impeller or torque input 16 and central gear 5 to make sure.

With a corresponding design of the teeth, so that they can also support radial forces, can on a spacer or spacer element 18 be dispensed with and the distance between the teeth directly on the teeth themselves or by means of other contours in the vicinity of the gear can be ensured.

8th shows a section along an input shaft 17 or a momentary input 16 one of the electrical machines 3A . 3B without holder or without frame 7 ,

Further shows 8th a section along a plane which through the axis of rotation of the rotor shaft 2 and also through the input shaft or through the moment input 16 one of the electric machines 3B on the right goes.

The area "c" is in 9 shown larger.

Visible are in a further perspective various elements, which have already been explained in some of the previous figures. It is therefore for the sake of simplicity and brevity on the References to the previous figures.

9 shows as detail a moment input 16 or a pinion 6 and a spacer 18 or spacer wheel 18 and an input shaft 17 ,

In this figure, the section "c" is from the 8th shown enlarged.

In the embodiment shown here is the spacer or the spacer element 18 designed as a ball bearing.

The outer ring 18A rests on the tread 19 of the central gear 5 from. The inner ring 18B the ball bearing or the spacer element 18 is on the input shaft 17 or at the moment input 16 the electric machine 3B mounted and rotates at the same speed as the pinion 6 the electric machine 3B ,

The ball bearing thus only has low speed differences between the inner ring 18B and the outer ring 18A compensate and only perform a little rolling work.

Depending on the design of the diameter of the impeller in relation to the unwind diameter of the pinion 6 and the height of the tread 19 on the central gear 5 relative to the gearing 5A . 5B on the central gear 5 , the relative speed of the inner ring 18B to the outer ring 18A to be changed.

With a suitable choice of dimensions, the relative speed can be greater, smaller or equal to zero. In a vote with only very small relative speeds, the ball bearing can also be replaced by a plain bearing. In extreme cases, when tuning to a relative speed close to "zero", the bearing can be completely eliminated, so that the spacer wheel 18 or the spacer element 18 only consists of a massive part, which is on the input shaft 17 the electric machine 3A . 3B is attached and on the tread 19 of the central gear 5 rolls.

10 shows a compensation of the repulsive Verzahnungskräfte.

The biasing spring 15 generates a contact force of the spacer wheel or the spacer element 18 against the tread 19 so that the spacing of the gears between pinion 6 and central gear 5 is defined.

Under torque load of the toothing of the pinion 6 arise further torque-proportional forces on the teeth of the pinion 6 , which into a tangential force TF and a repellent force AF can be divided.

Without countermeasures the repellent forces would AF against the biasing spring 15 Act. If the force of the preload spring is insufficient 15 lifts the spacer wheel 18 or the spacer element 18 from the tread 19 from. At the same time, the distance of the teeth of the pinion changes 6 to the toothing of the central gear 5 , so that a secure tooth mesh is no longer guaranteed.

For a secure meshing even without a very strong biasing spring 15 To ensure a torque-dependent additional contact force or compensation of the repellent teeth forces is proposed.

In 10 the principle of this compensation of the repulsive toothing forces is shown greatly simplified.

10 shows the teeth of the central gear 5 , the pinion 6 on the input shaft 17 or the moment input 16 the electric machine 3 . 3A . 3B and the rotation axis 9.1 of the rotary joint or the Nachführanordnung 9 for fixing the electric machine 3A . 3B on the frame 7 ,

The repellent gearing force AF causes due to the distance D2 to the swivel joint 9.1 parallel to the tangential direction U a repellent torque M1 , By the swivel 9.1 is spaced perpendicular to the tangential (distance measure D1 ), generates the tangential force TF a torque M2 , which counteracts the repellent torque M1 acts.

Because the repellent M1 and the pressing torques M2 proportional to the transmitted torque can be done by means of interpretation of the distances compensation. This is preferably designed so that the pressing torque M2 slightly stronger than the repellent torque M1 , so that a secure tooth engagement is ensured.

It should be noted that with the reference numeral 20 the mechanical connection of an electric machine 3 at a swivel joint 9.1 referred to as.

• - vorzugsweise Verwenden einer Vielzahl kleiner Generatoren bzw. Elektromaschinen aus Serienfertigung (z. B. Automobilbereich - E-Mobility), welche zusammen die geforderte Gesamtleistung ergeben.
• - vorzugsweise Anbindung der einzelnen Generatoren bzw. Elektromaschinen 3 an die Rotorwelle 2 mittels eines großen Zentralzahnrades 5 auf der Rotorwelle 2 und kleine Ritzel 6 auf der Generatorwelle 17 bzw. auf der Eingangswelle 17, wobei das Modul der Verzahnung an die geringen Momente eines einzelnen Generators 3 angepasst ist. Dies ergibt vorzugsweise ein kleines Verzahnungsmodul (z. B. in der Größenordnung 2) im Verhältnis zum Durchmesser des Zentralzahnrades 5. Daraus folgt eine hohe Zähneanzahl (Größenordnung 1000 Zähne und mehr) des Zentralzahnrades 5, welche in Kombination mit dem kleinen Ritzel 6 an der Generatorwelle 17 eine einstufige Übersetzung in der Größenordnung von z. B. 50 bis mehreren 100 ermöglicht. Falls die Übersetzung vom Zentralzahnrad 5 auf das Ritzel 6 des Generators bzw. der Elektromaschine 3 nicht ausreichend ist, kann für eine weitere Drehzahlanpassung, vor den einzelnen Generatoren 3 eine dedizierte Getriebestufe je Generator / Elektromaschine 3 ergänzt werden.

• - vorzugsweise Aufhängung des Generators 3 bzw. der Elektromaschine 3 mittels eines Gelenkes bzw. eines Drehgelenks, so dass der Generator bzw. die Elektromaschine radiale Fehler (radiale Bewegungen) mittels einer Bewegung im Gelenk bzw. im Drehgelenk ausgleichen kann.
• - vorzugsweise stellt ein Distanzrad bzw. ein Distanzelement 18 sicher, dass der Achsabstand (Abstand der Verzahnungen) konstant bleibt. Dieses kann z. B. als Kugellager ausgeführt sein. Je nach Auslegung erfolgt nur eine geringe Dreharbeit über dieses Lager, so dass auch auf Gleitlager ausgewichen werden kann.
• - vorzugsweise erfolgt die Aufhängung des Generators 3 mittels Gelenk so, dass die abweisenden Verzahnungskräfte drehmomentabhängig kompensiert werden können.
• - vorzugsweise wird mittels einer Feder bzw. einer Vorspannfeder 15 eine ausreichende Vorspannung erzeugt und eventuell die Gewichtskraft kompensiert, so dass eine Abstützung über das Distanzrad bzw. das Distanzelement 18 gewährleistet ist.
• - vorzugsweise werden, zum Ausgleich axialer Positionsfehler zwischen Ritzel 6 und Zahnrad 5, die beispielsweise durch Fertigungsungenauigkeiten oder unterschiedliche Wärmeausdehnungen hervorgerufen werden, besonders breite Ritzel 6 eingesetzt.
• - vorzugsweise sind die Verzahnungen für die rechte und linke Hälfte der Generatorkränze eines Zentralzahnrades 1x rechts und 1x links schrägverzahnt, so dass die axialen Kräfte aufgrund der Schrägverzahnung entgegengesetzt wirken. Auf das Zentralzahnrad 5 wirken somit nur minimale axiale Kräfte. Die Motorkränze rechts und links eines Zentralzahnrades 5 stützen sich gegenseitig in axialer Richtung A ab.
• - vorzugsweise Phasenversatz zwischen den einzelnen Generatoren bzw. Elektromaschinen 3, so dass die Restwelligkeiten des Drehmomentes der einzelnen Generatoren 3 zueinander phasenverschoben auf das Zentralzahnrad 5 wirken. Ggf. sind rotationssymmetrisch einzelne Generatoren bzw. Elektromaschinen 3 auch in Phase zueinander, so dass radiale Kräfte auf die Zentralwelle 2 bzw. Rotorwelle 2 minimiert werden.
• - vorzugsweise kann ein Zugang zum Innenbereich der Rotornabe für Zuleitungen und Wartungsarbeiten durch den Innendurchmesser der Hauptwelle 2 bzw. Rotorwelle 2 erfolgen, welche vorzugsweise aus Gewichtsgründen hohl ausgeführt ist.

The embodiment described above preferably has the following properties:

• preferably using a large number of small generators or electric machines from mass production (eg automobile sector - e-mobility), which together result in the required overall performance.
• - preferably connection of the individual generators or electric machines 3 to the rotor shaft 2 by means of a large central gear 5 on the rotor shaft 2 and small sprockets 6 on the generator shaft 17 or on the input shaft 17 , where the modulus of gearing to the low moments of a single generator 3 is adjusted. This preferably results in a small gearing module (eg of the order of magnitude 2 ) in relation to the diameter of the central gear 5 , This results in a high number of teeth (order of magnitude 1000 Teeth and more) of the central gear 5 , which in combination with the small pinion 6 at the generator shaft 17 a one-step translation of the order of z. B. 50 to several 100 allows. If the translation from the central gear 5 on the pinion 6 of the generator or the electric machine 3 is not sufficient, for another speed adjustment, before the individual generators 3 a dedicated gear stage per generator / electric machine 3 be supplemented.

• - Preferably suspension of the generator 3 or the electric machine 3 by means of a joint or a swivel joint, so that the generator or the electric machine can compensate for radial errors (radial movements) by means of a movement in the joint or in the swivel joint.
• - Preferably, a spacer or a spacer element 18 sure that the center distance (spacing of the gears) remains constant. This can be z. B. be designed as a ball bearing. Depending on the design, only a small amount of turning work takes place via this bearing, so that it is also possible to avoid sliding bearings.
• - Preferably, the suspension of the generator 3 by means of a joint so that the repellent toothing forces can be compensated depending on the torque.
• - Is preferably by means of a spring or a biasing spring 15 generates a sufficient bias voltage and possibly compensates the weight, so that a support via the spacer or the spacer element 18 is guaranteed.
• - Preferably, to compensate for axial position error between pinion 6 and gear 5 , which are caused for example by manufacturing inaccuracies or different thermal expansions, especially wide pinion 6 used.
• - Preferably, the teeth for the right and left half of the generator rings of a central gear 1x right and 1x left helical teeth, so that the axial forces act in opposite directions due to the helical gearing. On the central gear 5 Thus, only minimal axial forces act. The engine wreaths right and left of a central gear 5 support each other in the axial direction A from.
• - Preferably phase offset between the individual generators or electric machines 3 , so that the residual ripples of the torque of each generator 3 out of phase with each other on the central gear 5 Act. Possibly. Are rotationally symmetrical individual generators or electric machines 3 also in phase with each other, allowing radial forces on the central shaft 2 or rotor shaft 2 be minimized.
• - Preferably, access to the interior of the rotor hub for leads and maintenance through the inner diameter of the main shaft 2 or rotor shaft 2 take place, which is preferably made hollow for weight reasons.

• - vorzugsweise geringeres Gesamtgewicht (ca. 100 To statt ca. 220 To).
• - vorzugsweise modularer Aufbau, so dass eine einfache Skalierung der Leistung möglich ist.
• - vorzugsweise hohe Wiederverwendbarkeit der komplexen Bauteile (Generatoren, Leistungselektronik), Anpassungen an Leistung, etc. erfolgt mittels relativ einfachem Maschinenbau.
• - vorzugsweise geringer bzw. dünner magnetischer Luftspalt, geringe Magnetische Widerstände im Generator/Elektromaschine => Hohe Leistungsdichte, bei reduziertem Aufwand zur magnetischen Erregung.
• - vorzugsweise geringerer Materialeinsatz für Elektromaschine, da nur auf dem Umfang verteilt (innerer Bereich „Hohl“)
• - vorzugsweise verwenden von E-Motoren bzw. Elektromaschinen aus der Serie. Hohe Stückzahlen des einzelnen E-Motors (Skaleneffekte bei der Herstellung). => Geringere Gesamtkosten als für einen großen Generator in Sonderfertigung.
• - vorzugsweise ist der Motor für das E-Wheel-Drive ist bereits für flexible Aufhängung ausgelegt.
• - vorzugsweise Modularität / Fehlertoleranz bei Ausfall einzelner E-Motoren bzw. einzelner Elektromaschinen.
• - vorzugsweise Verteilung der Zahnbelastung auf viele kleine Kontakte (Zahnräder müssen nicht so massiv ausgeführt werden wie bei einem zentralen Getriebe).
• - vorzugsweise Schwingungen mit nur geringer Amplitude und hoher Frequenz aufgrund der Vielzahl der Quellen (leichter zu isolieren / teilweise gegenseitige Auslöschung).
• - vorzugsweise Dank der vielen Generatoren viele Freiheitsgrade um Schwingungen aktiv zu dämpfen.
• - vorzugsweise mögliche weitere Gewichtsreduzierung in der Gondel, indem die Hauptwelle bzw. die Rotorwelle 2 aus Verbund-Werkstoff hergestellt wird.
• - vorzugsweise mehr Freiheitsgrade zur Lagerung der Hauptnabe der Windkraftanlage. Die lange Hauptwelle 2 ermöglicht z. B. die Lagerung auf zwei relativ weit auseinanderliegender Lager aufzuteilen. Z.B. vorne in der Nähe der Nabe ein Lager spezialisiert auf hohe radiale Kräfte. Am anderen Ende günstigerweise ein Lager für axiale Kräfte und nur geringere radiale Kräfte.

With the embodiment described above, the following advantages are favorably obtained:

• - Preferably lower total weight (about 100 To instead of about 220 To).
• - Preferably modular design, so that a simple scaling of performance is possible.
• - Preferably high reusability of the complex components (generators, power electronics), adjustments to performance, etc. takes place by means of relatively simple engineering.
• - Preferably low or thin magnetic air gap, low magnetic resistance in the generator / electric machine => High power density, with reduced effort for magnetic excitation.
• - Preferably less material used for electric machine, as distributed only on the circumference (inner area "hollow")
• - preferably using electric motors or electric machines from the series. High quantities of the individual electric motor (economies of scale in production). => Lower overall costs than for a large generator in special production.
• - Preferably, the engine for the E-Wheel-Drive is already designed for flexible suspension.
• - Preferably modularity / fault tolerance in case of failure of individual electric motors or individual electric machines.
• - Preferably distribution of tooth load on many small contacts (gears do not need to be as massive as a central gear).
• preferably low amplitude, high frequency vibrations due to the multiplicity of sources (easier to isolate / partially cancel each other out).
• - Thanks to the many generators many degrees of freedom to actively damp vibrations.
• - Preferably possible further weight reduction in the nacelle, by the main shaft or the rotor shaft 2 made of composite material.
• - Preferably more degrees of freedom for storage of the main hub of the wind turbine. The long main shaft 2 allows z. B. divide the storage on two relatively widely spaced bearings. For example, in the front near the hub a bearing specializing in high radial forces. At the other end favorably a bearing for axial forces and only lower radial forces.

Although the present invention has been described above with reference to an embodiment, it should be understood that various embodiments and changes can be made without departing from the scope of the present invention as defined in the appended claims.

With regard to further features and advantages of the present invention, reference is expressly made to the disclosure of the drawing.

LIST OF REFERENCE NUMBERS

1

Output of a wind turbine

2

rotor shaft

3

electric machine

3.1

casing

3A

Electric machine on the left

3B

Electric machine on the right

4

rotating body

4.1

rotor

4.2

wave

5

gear

5A

Toothing left

5B

Toothing right

6

pinion

7

frame

8th

electrically, pneumatically, hydraulically and / or mechanically acting means

9

tracking array

9.1

swivel

10

flange

11

stiffening ring

12A

brace

12B

brace

12C

brace

12D

brace

13A

Radial bearing arrangement

13B

Angular contact ball bearing assembly

14

stiffening ring

15

biasing spring

16

moment input

17

input shaft

18

spacer

18A

outer ring

18B

inner ring

19

Tread for spacer

20

Connection electric machine to swivel

AF

repellent toothing force

TF

tangential force due to the transmitted torque

M1

repellent torque

M2

pressing torque

D1

Distance of the rotary axis of the rotary joint to the tangential force

D2

Distance of rotation axis of the swivel joint to the point of application of the toothing parallel to the tangential force

D

axis of rotation

U

circumferentially

A

axial direction

R

radial direction

S

double arrow

Claims (10)

Electric machine assembly (1) comprising a rotor shaft (2) and at least one electric machine (3, 3A, 3B) having a rotary body (4; 4.1, 4.2; 16; 17), wherein coupling means (5, 6) are provided the rotor shaft (2) and the rotary body (4) of the respective electric machine (3, 3A, 3B) mechanically coupled to each other in a first position for transmitting a rotational movement, and at least one stationary arranged frame (7) is provided, and that each frame (7) comprises a plurality of electric machines (3 3A, 3B), preferably more than 5, more preferably more than 15, each of the frame (7) accommodated electric machine (3, 3A, 3B) is positioned around the rotor shaft (2) arranged around. Electrical machine assembly according to Claim 1 , characterized in that the respective coupling means (5, 6) between the rotor shaft (2) and the rotary body (4) either a rotating body side provided, on the rotor shaft (2) rolling off friction wheel or a rotor side provided gear (5) and a rotating body side provided with the gear (5) in meshed connection pinion (6). Electrical machine assembly according to Claim 2 , characterized in that the rotor shaft (2) is under an axial load, that the respective meshing connection between the pinion (6) and gear (5) is designed as a helical gear pairing and that each helical gear pairing between pinion (6) and gear (5) a generated axial force along the axis of rotation (D) of the rotor shaft (2), wherein all of the helical gear pairings produced on the rotor shaft (2) acting axial forces either cancel each other or counteract the axial load. Electrical machine assembly according to one of Claims 1 to 3 , characterized in that electrically, pneumatically, hydraulically and / or mechanically acting means (8) are provided, which act at least on the coupling means (5, 6) and these individually or in groups between the first position and a second, the coupling to Back and forth the rotor shaft (2). Electrical machine assembly according to one of Claims 1 to 4 , characterized in that the translation stage between the rotor shaft (2) and the respective rotary bodies (4) is greater than 20, greater than 50, greater than 100 or greater than 200. Electrical machine assembly according to one of Claims 1 to 5 , characterized in that a Nachführanordnung (9) is provided, which in the first position of the rotor shaft (2) and coupling means (5, 6) acts on the respective coupling means (5, 6) and this at a constant radial distance from the lateral surface of the rotor shaft (2) with which the coupling means (5, 6) are coupled. Electrical machine assembly according to one of Claims 1 to 6 , characterized in that at least one frame (7) comprises a first row and a second row of electric machines (3, 3A, 3B) and that the rotary bodies (4) of the electric machines (3A), which are combined in the first row, belong to the Rotary bodies (4) of the electric machines (3B), which are combined in the second row, in the circumferential direction (U) of the rotor shaft (2) are arranged offset by an angular amount. Electrical machine assembly after each of Claims 1 to 7 , characterized in that the electric machines (3, 3A, 3B) are generators driven by the rotor shaft (2). Electrical machine assembly after each of Claims 1 to 7 , characterized in that the electric machines (3, 3A, 3B) are electric motors that drive the rotor shaft (2). Wind power plant, characterized in that it comprises an electric machine assembly (1) according to one of Claims 1 to 8th having.

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