DE102009051117B4 - Horizontal runner turbine with passive yaw angle adjuster - Google Patents

Abstract

Horizontal runner turbine comprising; 1.1 a support structure (2); 1.2 a machine nacelle (1) which is fastened to the support structure (2) by means of an azimuth swivel joint (3) so that the machine nacelle (1) can execute a rotary movement about a substantially vertically oriented yaw axis (27); 1.3 a rotor (7) designed as a windward rotor, which rotates at a distance from the yaw axis (27) on the machine nacelle (1) and defines an axis of rotation (14), the rotor (7) comprising turbine blades (8.1, 8.2, 8.3) and the rotor (7), a rotor plane (12) which is spanned by the base points of the turbine blades (8.1, 8.2, 8.3), and a blade tip plane (28) which is defined by the radially outer ends of the turbine blades (8.1, 8.2, 8.3) , assigned; characterized in that 1.4 the turbine blades (8.1, 8.2, 8.3) are swept backwards at least in sections, the blade tip plane (28) lying between the rotor plane (12) and a plane which receives the yaw axis (27) and to the axis of rotation (14) stands vertically; and 1.5 the machine nacelle (1) is attached to the support structure (2) so that it can rotate freely about the yaw axis (27).

Description

The invention relates to a horizontal rotor turbine with passive yaw angle adjustment device, in particular for an underwater power plant for the production of tidal energy with the preamble features of claim 1.

Horizontal damper turbines standing free of dam structures are known and correspond to the concept known from wind power. In order to use a generic horizontal rotor turbine for the use of tides, an adaptation to the resulting ebb and flow alternation between two main flow directions is necessary. In the simplest case, the rotor is provided with bidirectionally flowable turbine blades for this purpose. These may have elliptical profiles, as for example by the WO 2006/125959 A1 be revealed.

Alternatively, for a bilateral approachability point-symmetric profiles with an S-blow through the US 2007/0231148 A1 proposed. Such a bidirectionally inflatable rotor with a torsionally rigid attachment of the turbine blades to the hub allows a simplified and therefore robust system concept. However, the efficiency is reduced compared to an airfoil adapted to only one inflow direction. In addition, large torsional forces are generated on the turbine blades, in particular for the point-symmetrical profiles with S-impact, so that they have to be designed with high structural strength.

An alternative plant design for adaptation to a change in the direction of flow provides for a rotational movement of the individual turbine blades by 180 ° at the hub of the rotating unit. For such a pitch angle adjustment mechanism is exemplified on the EP 1366287 B1 directed. The pitch angle adjustment allows not only an adaptation to a changing direction of flow simplified power control and the safe shutdown of the system in case of overload by screwing the turbine blades in the flag position. However, a disadvantage is the high design complexity for the realization of the rotary mechanism in the region of the base of the turbine blades. Furthermore, the failure of a pitch angle adjustment device leads to an uncontrolled operating situation, which can lead to the loss of individual turbine blades. This circumstance is disadvantageous, in particular due to the difficulty of maintenance, poor accessibility of underwater power plants for a plant location in the sea.

Yet another way to adapt a generic horizontal rotor turbine to a direction variable flow is to carry out a total movement of the machine nacelle with the rotating unit, so that a rotor with torsionally rigid turbine blades and an optimized airfoil can be used. If only a change of direction between two main orientations is provided, it is possible to pivot the machine nacelle on the support structure about a horizontally extending axis of rotation. This is exemplified in the GB 2431207 A directed. However, preferred is a flow tracking, which allows a rotational movement about a vertical axis in an angular range of at least 180 °. As a result, the ellipsoidal flow characteristic of a typical tidal current can be fully utilized.

To set a certain yaw angle, the nacelle is attached to the support structure by means of an azimuth pivot, which is associated with a vertical axis of rotation. If active tracking is selected, there is a need to integrate a drive into the azimuth pivot. However, then a control and control device must be provided which optimizes the yaw angle adjustment depending on the flow. For this purpose, for example, an MPP control can be used.

A disadvantage of the above-mentioned actively tracking yaw angle adjustment is the expenditure on equipment for the actuators and sensors necessary for this purpose as well as the control and regulating devices. Therefore, a passive device for yaw angle adjustment is desirable. In the simplest case, this is effected by the use of a leeward runner, which, however, is disadvantageous due to the adverse flow control by the upstream support structure against a windward runner. When the idea of passive yaw angle adjustment is applied to a windward runner, a known way is to use a cross stabilizing component, such as a rigid fin, in the downstream part of the nacelle, which is downstream of the axis of rotation of the azimuth pivot. However, this concept is structurally complicated if the machine nacelle is elongated in order to space the rotor upstream of the support structure with the aim of bringing it out as far as possible from the tower ramp. This extension, which is desired in the upstream direction, must be balanced by the transversely stabilizing, downstream device, so that appropriately sized fins and the support structures necessary for this purpose are necessary.

The invention has for its object to overcome the above-mentioned disadvantages of the prior art and to provide a windward rotor with a horizontal axis of rotation with a structurally simplified device for passive yaw angle adjustment. Such a horizontal rotor turbine with a self-tracking for the yaw angle should be applicable not only underwater power plants, especially tidal power plants, also for wind turbines.

For a further design, the horizontal-turbofan turbine should automatically turn into the optimum yaw angular position regardless of the starting position and preferably perform a forward and backward movement in the angular range of about 180 ° instead of a full circle motion to a twisting of the power cable between the electric by the exclusion of a repeated full circle rotation To prevent generator in the nacelle and the support structure. Starting from a generic flow power plant with a designed as windward rotor with a horizontal axis of rotation, the inventor has realized that a passive yaw angle adjustment is effected when the rotor turbine blades with at least one swept back section. Preferably, a rotor is used with a plurality of backward swept turbine blades with rectilinear longitudinal axis. In this case, a reverse sweep is understood to mean a deviation of the course of the longitudinal axis of a turbine blade from the radial beam, which causes a spacing from the rotor plane in the direction parallel to a plane which comprises the axis of rotation of the azimuth rotary joint.

The backward sweep of the turbine blades of the rotor results in an angular position between the axis of rotation of the rotor and the direction of flow, hereinafter referred to as angular deviation, an asymmetry of the thrust forces on the two lateral halves of the rotor and a spatial offset of the associated shear centers. This results in a yaw moment about the axis of the azimuth rotary joint of the system, the machine nacelle with the rotor again to the parallel orientation of the axis of rotation and the flow direction, d. H. in the centered position, leads back.

The self-tracking leading angular deviation torque will always be present when the deflection angle to the centered position does not exceed a certain critical angle that defines a capture range. The extent of the capture range depends on the one hand on the prevailing flow and on the other by the dimensioning of the systems. Relevant is the determination of the overhang length, d. H. the distance between the rotor plane and the axis of the azimuth rotary joint, the sweep angle of the turbine blades, the outer diameter of the rotor and the turbine blade profile.

Due to the self-centering of the windward runner according to the invention, it is possible to form the azimuth rotary joint for realizing the connection between the machine nacelle and the support structure in a free-rotating manner as a large bearing with a rotational degree of freedom about the vertical bearing axis. As far as the swept rotor is in the capture area and automatically aligns with a rotation axis parallel to the flow, no drive for the azimuth rotary joint is necessary. However, there is a need to initially orient the machine nacelle so that the axis of rotation of the rotor in the. Catch area occurs. For a first embodiment, an activatable drive is assigned to the azimuth rotary joint, which leads to the start of operation, the system in the desired basic orientation. Subsequently, the drive can release the azimuth swivel and the machine nacelle with the rotating rotor is carried along by the effect of self-centering with the flow. In the case of tidal flow, this may be followed by both a fundamental inflow direction change and a gradual inflow angle change in a tidal flow.

To dispense with a structurally complex, temporarily switchable drive for the azimuth rotary joint, the basic orientation of the machine nacelle for guiding the axis of rotation of the rotor in the capture area can be effected by an additional drive outside of the azimuth rotary joint, for example in the form of a transverse thruster. In this case, the auxiliary drive with respect to the axis of rotation of the azimuth rotary joint to space and must produce a transverse thrust on the nacelle, which leads to a sufficiently large yaw moment.

For a further embodiment of the invention, a device is provided which also causes the yaw angle tracking to the capture area passively. For this purpose, a fin articulated on the machine nacelle on a region opposite the rotor relative to the axis of rotation of the azimuth rotary joint is provided. The fin may pivot about a vertical axis in a swivel range defined by stops on the nacelle. In the case of a rotor, which has flown against the operating direction and is in the position of a flag, the fin is folded over on one side and pressed against the stop provided thereon on the machine nacelle. With appropriate dimensioning results due to the back pressure on the fin a rotational movement of the nacelle to the azimuth hinge to the Rotor reaches its windward-rotor position and the self-centering effect according to the invention leads to parallel alignment with respect to the flow.

The above-described device for guiding the system into the catching area in which the self-centering takes place, which works exclusively with the aid of the flow forces acting on the system, can be further improved with the aim of carrying out a controlled rotation limited to a semicircle. By this is meant that the rotational movement of the nacelle about the azimuth pivot on the support structure is limited to a back and forth movement between the oppositely directed main inflow directions at low tide and high tide flow and an adjoining, site-adapted angular variation range. This is advantageous because a power cable that leads from a generator in the nacelle to the support structure is not twisted uncontrollably. In this case, the desired back and forth movement is enforced by additional stops on the support structure, which lead to an angle specification for the fin relative to the axis of rotation and limit the yaw motion of the nacelle.

The invention will be explained in more detail below with reference to exemplary embodiments in connection with figures representations, in which the following is shown in detail:

1 shows a horizontal rotor turbine according to the invention in side view.

2a shows the horizontal runner turbine 1 in plan view in a centered to the direction of flow position.

2 B shows the effective flow and the resulting flow forces on a leaf element.

3a shows a view corresponding to 2a in the case of an angular offset between the axis of rotation and the direction of flow.

3b shows the determination of a leaf element according to the operating situation 3a ,

4a shows a hydroelectric power plant according to the invention with a fin pivotally mounted on the machine nacelle for guiding the system in the capture area of self-centering in side view.

4b shows the embodiment according to 4a in plan view with the range of motion of the plant.

5 - 10 show for a 4a and 4b corresponding Appendix in plan view the operation of a completely passive yaw angle adjustment with a yaw movement restriction to a semicircle with an additional location-related angular variation range.

1 schematically shows a simplified generic, formed without dam structures freestanding horizontal rotor turbine, in particular for exploiting a tidal current. In the present case the plant stands by means of the foundation 4 , which is designed as a gravity foundation, on the riverbed 5 , From this goes a tower-like support structure 2 out on a machine nacelle 1 is set. The connection between the support structure 2 and the machine nacelle 1 is via an azimuth swivel 3 causes the rotation of the machine nacelle 1 about a vertical axis, hereinafter referred to as yaw axis 27 designated, allows.

In a machine nacelle 1 are the bearings for the shaft 9 the circulating unit 6 as well as components of the electric generator coming from the shaft 9 is housed (not shown in detail). The essential part of the rotating unit 6 is the rotor 7 , which in this case is formed vierblättrig. Further embodiments with an odd number of turbine blades, in particular the use of a three-blade rotor, is conceivable, whereby the automatic yaw angle adjustment explained below can also be realized for such a rotor design. According to the invention, the rotor comprises 7 at least partially backward swept turbine blades 8.1 . 8.2 . 8.3 , For the in 1 shown embodiment are the turbine blades 8.1 . 8.2 . 8.3 with a rectilinear oriented threading line, which has the required backward sweep over its entire longitudinal extent. The threading line connects the profile intersection points on the chords at a quarter of the tread depth. The result is the rotor plane 12 passing through the centers of the bases of the rotor blades 8.1 . 8.2 . 8.3 is clamped, for the illustrated windward-rotor arrangement upstream of the blade tip plane 28 at the radially outermost end of the turbine blades 8.1 . 8.2 . 8.3 , The resulting effect on the passive yaw angle adjustment will be described below with reference to FIG 2a - 3b shown.

2a shows a plan view of the plant according to the invention 1 , Sketches a first lateral thrust D1 and a second lateral thrust D2 on the rotating rotor 7 at the first lateral thrust center 30 and at the second lateral thrust center 31 attack. For the determination of the rotating rotor 7 swept surface through a vertical section plane 29 divided by the axis of rotation 14 and the yaw axis 27 is spanned, and all thrust to both Sides of the vertical section plane 29 isolated vectorially added. For the approximate determination of the shear forces on the turbine blades designed as lift rotors 8.1 . 8.2 . 8.3 the leaf element theory can be used. These are exemplified in 2a in the direction of flow 13 oriented leaf elements 15.1 . 15.2 . 15.3 with a matching radial distance to the rotation axis 14 shown.

2 B shows the flow against the middle profile section 16 of the leaf element 15.2 of the turbine blade 8.2 whose profile polar to determine the force on the leaf element 15.2 is used. For clarification is in 2 B The following is shown: The chord 17 takes to the direction of rotation 50 the blade pitch Wb. The flow angle Wa of the effective flow velocity Vr results from the vectorial addition of the rotational velocity U and the flow velocity Va. This results at the hydrodynamic center 51 of profile section 18 the total flow force Fg vectorially in the direction of rotation 50 Parallel tangential force Ft and the perpendicular thrust force Fs can disassemble.

3a shows the rotor 7 with a rotation axis 14 , in an angular offset to the direction of flow 13 stands. This will be the first push center 30 and the second first thrust center opposite the yaw axis 27 shifted so that a change in leverage is taken into account. To this end, a first transverse distance Q1 and a second transverse distance Q2 of the thrust centers are sketched for a magnitude consideration 30 . 31 to the plane through the yaw axis 27 and the direction of flow 13 is spanned. For the in 3a shown situation of an angular deviation within the capture range creates the resulting yaw moment 18 , which counteracts the angular deviation and thus the rotor 7 on the in 2a shown centered position returns.

If, in turn, the leaf element theory is used to determine the hydrodynamic rotor forces, the vertical section plane results on both sides 29 different leaf elements. This is exemplified by the leaf element 15.4 on the turbine blade 8.1 explains that due to the angular offset of the system now has a reduced effective sweep angle, ie it is compared to the centered position steeper against the direction of flow, so increases on this side of the projection radius of the rotor flight perpendicular to the flow.

3b shows an enlargement of the circular, dashed area A from 3a with the leaf element 15.4 on the turbine blade 8.1 , The illustrated leaf element 15.4 has a profile section direction 52 on, parallel to the flow direction 13 is oriented. Their course deviates from the original profile section direction 53 from (dashed lines), the corresponding leaf element 15.1 in the case of a parallel alignment of the axis of rotation 14 according to the flow direction 2a equivalent. It follows that the profile cutting directions used to carry out the sheet element theory depend on the angular adjustment between the axis of rotation 14 and the direction of flow 13 are due to the twisting and tapering of the turbine blades 8.1 . 8.2 . 8.3 angle-dependent profile cross sections 16 to be considered with different profile polar.

Furthermore, for the integration of the hydrodynamic forces on the turbine blades 8.1 . 8.2 . 8.3 one of the angular deviation of the axis of rotation by means of the leaf element theory 14 dependent radial blade element extension, if an originally selected number of blade elements 15 . 15.1 . 15.2 . 15.3 . 15.4 is maintained. This results from the change in the projection surface of the turbine blades 8.1 . 8.2 . 8.3 perpendicular to the direction of flow 13 ,

For a design alternative of the invention, turbine blades are conceivable which do not have a backward sweep over their entire longitudinal extent. In this case, at least the hydrodynamically particularly effective radially outer region is preferably provided with the desired sweep. Further, a further embodiment is conceivable, for which there is a first turbine blade section with radial jet geometry and a second turbine blade section with rearward sweeping, wherein the transition between these two sections has a certain flexibility. This ensures that in the case of overload, the sweep angle of the second turbine blade section increases and thus the effective diameter of the rotor 7 to reduce the power consumed by the installation. Further, not shown in detail embodiments of the invention are conceivable, such as sunken turbine blades 8.1 . 8.2 . 8.3 which lead to a backward sweep, and the most advantageous in terms of the simplified sliding of foreign bodies on the rotor 7 are.

4a shows a further embodiment of the invention with an additional, passive-acting device for guiding the swept rotor 7 into the catch area where self-centering occurs. For this purpose is at the rear end 33 the machine nacelle 1 that the rotor 7 with respect to the yaw axis 27 opposite, a fin 21 hinged. The fin 21 can be about a vertical pivot axis 22 perform a limited rotational movement, wherein, as in the plan view 4b shown, the movement by a pairwise symmetrical arrangement of a first co-rotating fin stop 23 and a second co-rotating fin stop 24 is limited.

Such a fin 21 becomes in case of a false flow towards the rear end 33 the machine nacelle 1 against the first mitdrehenden fin stop 23 or the second co-rotating fin stop 24 pressed. The resulting impact pressure on the fin 21 turn the machine nacelle 1 with the rotor 7 around the yaw axis 27 ,

On this basis, for a further development according to the 4a and 4b provided a first additional stop pair, namely the first stationary fin stop 25 and the second stationary fin stop 26 that with the support structure 2 are connected. A third stop pair, the first gondola stop 34 and the second gondola stop 35 , concerns the movement restriction of the nacelle 1 , The interaction of all attacks is used to the direction of the fin 21 to adjust so that the machine nacelle 1 Movements around the yaw axis 27 performs in a limited angular range, so that when changing the direction of flow substantially a back and forth movement is completed. This will ensure that via the azimuth swivel 3 running power cable is not twisted.

The completely passive yaw angle centering will be explained below with reference to the sequence 5-10. A tidal power plant according to the invention with the in 4b illustrated movement possibilities. The main flow direction is at low tide at 0 ° and at high tide for the maximum speed at 180 °. Opposite these two Hauptanströmungsrichtungen is the range of motion for the yaw angle of the system, by the rotor circuit segment shown by dashed lines 19 in 4b is shown, extended by 30 ° in the region of the two main flow directions. This angular variation range is location-dependent and takes account of angular variations and the passage through a tidal ellipse and can be adapted to local conditions. The yaw range is through the rotor circle segment 19 fixed, wherein a movement substantially in the third and fourth quadrant, specifically in the angular range of 150 ° to 30 ° is possible. These two angular positions mark two end positions, for those on the nacelle 1 attached pin 37 at the first gondola stop 34 or at the second gondola stop 35 is applied. These are in 4b indicated by dashed lines.

The possibility of movement of the fin 21 is on the fin circle segment 20 limited, with the associated stops, the first stationary fin stop 25 and the second stationary fin stop 26 , assume for the illustrated embodiment, the angular positions 190 ° and 350 °. This site-specific designs are possible for the fixed fin stops 25 . 26 closer to 180 ° and 360 °. This is the fin circle segment 20 essentially in the first and second quadrants. Furthermore, for the fin 21 the rocking angle range 36 indicated, the movement restrictions between the first mitdrehenden fin stop 23 and the second co-rotating fin stop 24 describes.

5 shows the flow of the rotor 7 for a direction of flow 13.1 which, in accordance with the definition 4b is at 0 ° and represents a first main direction of inflow at low tide. 6 represents the final phase of the ebb, the direction of flow 13.2 is about 30 °, so that in this case a clockwise rotating Tidenellipse is assumed. For clarification, the figures are based on a tidal ellipse with a pronounced direction of flow variation, wherein the tidal ellipse is generally much flatter for a real tidal flow. Furthermore, due to the positional symmetry of the stationary stops with respect to an axis, the for the determination according to 4b through the angles 90 ° and 270 °, a system according to the invention also follow a tidal ellipse with a flow angle that moves in the counterclockwise direction.

For the significantly reduced flow velocity for the flow according to 6 The braking torques of the systems can not be overcome and the rotor stops. With regard to the yaw angle adjustment, the system remains in the azimuth swivel due to bearing friction 3 in the end position, for each of which a stop of all stop pairs is on contact. Accordingly, the fin is 21 on the first co-rotating fin stop 23 and additionally on the first stationary fin stop 25 at. In addition, the machine nacelle 1 against the second gondola stop 35 led what was in 6 not shown in detail. However, the end position is apparent through the illustrated rotor circuit segment 19 ,

7 shows a direction of flow 13.3 from about 175 ° for the flood on the back of the plant. Accordingly, at the beginning of the operating situation in 7 the rotor 7 wrong flowed. Due to the slightly angled position of the fin compared to the horizontal 21 arises at the in 8th shown inflow direction 13.4 from 180 °, which is the second main direction of flow in the case of the flood, a back pressure on the fin 21 that suffices the plant around the yaw axis 27 to turn. It is the through the fin 21 caused rotational movement up to the capture range for the present direction of flow 13.4 guided, so that the self-centering effect on the backward swept rotor 7 the system finally to the flow direction 13.4 aligns. This operating situation with rotating rotor is in 9 shown.

For the further time course of the tidal flow, in turn, a displacement of the direction of flow in the clockwise direction takes place. In this case, the usable angle range ends at high tide and thus the rotational movement of the rotor 7 at a flow of about 210 ° according to the in 10 shown inflow direction 13.5 , For this case, neither is the fin 21 the machine nacelle still 1 at one of the abovementioned stops. For the further course of the tide, which is not described in detail below, a transverse flow onto the fin takes place in the event of rising tide 21 , this against the second mitdrehenden fin stop 24 leads and with a further increasing flow strength of the system in the area of the rotor circuit segment 19 Turn back to the operating position, until again in 5 shown starting situation in the case of the direction of flow 13.1 is reached at 0 °.

The embodiments discussed to illustrate the invention treat tidal power plants. Nevertheless, the inventive use of a swept rotor for automatic yaw angle adjustment for a windward runner in horizontal design should not be limited exclusively to this application. Advantageous applications also arise for river water power plants or for the development of maintenance-free wind turbines. Further embodiments of the invention will become apparent from the subsequent claims.

LIST OF REFERENCE NUMBERS

1

nacelle

2

support structure

3

Azimuth rotary joint

4

foundation

5

body of water

6

circulating unit

7

rotor

8.1, 8.2, 8.3

turbine blade

9

wave

10

hub

11

Hood

12

rotor plane

13, 13.1,

13.2, 13.3,

13.4

inflow direction

14

axis of rotation

15.1, 15.2,

15.3

leaf member

16

profile section

17

chord

18

resulting yaw moment

19

Rotor disc segment

20

Fins circle segment

21

fin

22

swivel axis

23

first co-rotating fin stop

24

second co-rotating fin stop

25

first stationary fin stop

26

second stationary fin stop

27

yaw axis

28

Sheet top level

29

Vertical cutting plane

30

first lateral push center

31

second lateral push center

32

Flow cross-section plane

33

rear end

34

first pod stop

35

second pod stop

36

Wippwinkelbereich

37

pen

50

direction of rotation

51

hydrodynamic center

52

Profile cutting direction

53

original profile cut direction

d

radial leaf element extension

D1

first lateral thrust

D2

second lateral thrust

fg

Total flow force

fs

thrust

Ft

tangential

Q1

first transverse distance

Q2

second transverse distance

U

velocity of circulation

Va

inflow velocity

Vr

effective flow velocity

Wa

angle of attack

wb

blade pitch

Claims (6)

Horizontal runner turbine comprising; 1.1 a support structure ( 2 ); 1.2 a nacelle ( 1 ) by means of an azimuth rotary joint ( 3 ) on the support structure ( 2 ), so that the nacelle ( 1 ) a rotational movement about a substantially vertically oriented yaw axis ( 27 ); 1.3 a trained as a windward rotor ( 7 ) which is spaced from the yaw axis ( 27 ) on the nacelle ( 1 ) and a rotation axis ( 14 ), whereby the rotor ( 7 ) Turbine blades ( 8.1 . 8.2 . 8.3 ) and the rotor ( 7 ) a rotor plane ( 12 ) through the bases of the turbine blades ( 8.1 . 8.2 . 8.3 ) and a blade tip plane ( 28 ) through radially outer ends of the turbine blades ( 8.1 . 8.2 . 8.3 ) are assigned; characterized in that 1.4 the turbine blades ( 8.1 . 8.2 . 8.3 ) are at least partially swept backwards, wherein the blade tip plane ( 28 ) between the rotor plane ( 12 ) and a plane containing the yaw axis ( 27 ) and to the axis of rotation ( 14 ) is vertical; and 1.5 the machine nacelle ( 1 ) freely around the yaw axis ( 27 ) rotating on the support structure ( 2 ) is attached. Horizontal runner turbine according to claim 1, characterized in that all turbine blades ( 8.1 . 8.2 . 8.3 ) of the rotor ( 7 ) are swept backwards. Horizontal rotor turbine according to one of claims 1 or 2, characterized in that all turbine blades ( 8.1 . 8.2 . 8.3 ) of the rotor are swept back over their entire longitudinal extent. Horizontal runner turbine according to one of claims 1 or 2, characterized in that at least a part of the turbine blades ( 8.1 . 8.2 . 8.3 ) of the rotor ( 7 ) have in at least one portion a radially extending longitudinal axis. Horizontal rotor turbine according to one of the preceding claims, characterized in that the yaw angle of the turbine blades ( 8.1 . 8.2 . 8.3 ), the diameter of the rotor ( 7 ) and the distance between the rotor plane ( 12 ) and the yaw axis ( 27 ) are coordinated so that for angular deviations between the axis of rotation ( 14 ) and the direction of flow ( 13 ) within a capture range ( 15 ), a residual yaw moment resulting in the yaw moment ( 18 ) arises. Horizontal runner turbine according to one of the preceding claims, characterized in that at the rear end ( 33 ) of the nacelle ( 1 ), which is the rotor ( 7 ) with respect to the yaw axis ( 27 ), a fin ( 21 ) with a vertical pivot axis ( 22 ) is movably mounted, wherein the pivoting range by a paired arrangement of a first co-rotating stop ( 23 ) and a second co-rotating stop ( 24 ) on the nacelle ( 1 ) is limited.

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