Vertical wind turbine comprising rotor blade-supporting pitch motor, as well as kit for same, and method for operating same

Abstract

A vertical wind turbine that includes a plurality of vertical vanes which can be rotated independently of one another about a respective vane rotational axis by a motor and which are mounted on a common circular path in a rotatable manner about a vertical rotor rotational axis. A method for operating a vertical wind turbine. Angular positions are specified for vertical wind turbine vanes which are mounted in a rotatable manner about a respective vertical rotor rotational axis and which can be rotated about a respective vane rotational axis by a motor. The vertical wind turbine is operated in a particularly efficient and material-preserving manner in that the angular positions of the vanes are specified by at least one respective pitch motor which at least partly supports the respective vane.

Claims

1. A vertical wind turbine with a plurality of vertical blades, wherein each blade of the plurality of vertical blades is supported and motor-driven pivotable around a respective blade rotation axis independently of the other blades of the plurality of vertical blades, wherein the plurality of vertical blades are rotatable on a common circular path around a vertical rotor rotation axis, wherein each blade of the plurality of vertical blades is supported exclusively by at least one pitch motor for motor-driven pivoting of each blade of the plurality of vertical blades around its respective blade rotation axis by the at least one pitch motor, wherein each pitch motor comprises a motor shaft arranged concentrically around a respective blade rotation axis and a stator ring that is rigidly connected to a motor housing at which a rotor arm is fastened to connect the blades to a rotor hub, and wherein each of the blades is driven directly by the at least one pitch motor.

2. The vertical wind turbine according to claim 1, wherein the pitch motor is embodied as a torque motor with at least one rotor ring that is torsionally rigidly coupled to the respective blade.

3. The vertical wind turbine according to claim 1, wherein a rotor ring rests against the outer circumference of a motor shaft of the pitch motor.

4. The vertical wind turbine according to claim 1, wherein the blades are borne supported on motor bearings in the pitch motor.

5. The vertical wind turbine according to claim 1, wherein the blades include an upper blade section and a lower blade section and the pitch motor is positioned between the upper blade section and lower blade section.

6. The vertical wind turbine according to claim 1, wherein the blades are flange-mounted to the pitch motor.

7. The vertical wind turbine according to claim 6, wherein the pitch motor includes at least one rotary position transducer for determining a rotation position of the blade.

8. The vertical wind turbine according to claim 1, wherein the pitch motors each has a motor housing to which a rotor arm is fastened, which connects the blades to a rotor hub of the vertical wind turbine.

9. The vertical wind turbine according to claim 8, wherein the rotor arm is flange mounted to the motor housing.

10. The vertical wind turbine according to claim 8, wherein a stator ring of the pitch motor is positioned between two flange halves of a mounting collar of the motor housing and/or between an upper shell and a lower shell of a casing that at least partially cases-in the pitch motor.

11. The vertical wind turbine according to claim 10, wherein the casing forms at least one intake socket and at least one discharge opening in order to convey cooling air between the intake socket and the discharge opening along at least part of a cooling body that is mounted on the stator ring.

12. The vertical wind turbine according to claim 1, further comprises a transmission that couples a rotor of the vertical wind turbine, which is able to rotate around the rotor rotation axis, to a generator of the vertical wind turbine, wherein at least one transmission stage of the transmission is embodied as a planetary gear stage.

13. The vertical wind turbine according to claim 12, wherein at least one planet gear of the planetary gear stage is connected by means of a flexible pin to a strut of the planetary gear stage.

14. A kit, comprising: components, parts, and tools for installation of a vertical wind turbine according to claim 1.

15. A method for operating a vertical wind turbine that comprises vertical blades and pitch motors, each pitch motor having a motor shaft arranged concentrically around a respective blade rotation axis of a respective vertical blade and a stator ring that is rigidly connected to a motor housing at which a rotor arm is fastened to connect the blades to a rotor hub, each vertical blade being supported exclusively by a respective pitch motor to rotate around the vertical rotation axis thereof, wherein each of the vertical blades is driven directly by the pitch motor to which the vertical blade is fastened, and wherein angular positions of vertical blades of the vertical wind turbine, which are supported such that they are rotatable around a vertical rotor rotation axis, and are motor-driven pivotable around a respective blade rotation axis independently of one another, are being predetermined, and wherein the angular position of a blade of the vertical blades is predetermined by means of the pitch motor to which the blade is mounted.

Description

DESCRIPTION OF FIGURES

(1) Exemplary embodiments of the invention will be described below based on the following figures. In the drawings:

(2) FIG. 1 shows a schematic perspective view of a vertical wind turbine according to the invention;

(3) FIG. 2 shows a schematic side view of a vertical wind turbine according to the invention;

(4) FIG. 3 shows a schematic top view of a vertical wind turbine according to the invention;

(5) FIG. 4 shows a detail IV indicated in FIG. 2 of a blade of a vertical wind turbine according to the invention;

(6) FIG. 5 shows a detail V indicated in FIG. 4 of a blade of a vertical wind turbine according to the invention with a pitch motor according to the invention in a schematic cross-sectional view along a rotation axis of the blade;

(7) FIG. 6 shows a schematic perspective view of aerodynamically cased-in pitch motors of a vertical wind turbine according to the invention;

(8) FIG. 7 shows a schematic perspective view of a pitch motor together with blades mounted on it, particularly showing a motor flange of the pitch motor for fastening the pitch motor together with the blades to an arm of a rotor of a vertical wind turbine according to the invention;

(9) FIG. 8 shows a schematic partial cross-sectional view of a pitch motor according to the invention;

(10) FIG. 9 shows a schematic cross-sectional view of a drive train of a vertical wind turbine according to the invention along a drive shaft of the drive train;

(11) FIG. 10 shows a schematic perspective view of a first embodiment according to the invention of a hub connection of a vertical wind turbine according to the invention;

(12) FIG. 11 shows a schematic front view of a section of an arm of a rotor of a vertical wind turbine according to the invention;

(13) FIG. 12 shows a schematic side view of the section shown in FIG. 11 of an arm of a rotor of a vertical wind turbine according to the invention;

(14) FIG. 13 shows a schematic cross-sectional view of the section shown in FIGS. 11 and 12 of an arm of a rotor of a vertical wind turbine according to the invention along the cross-sectional line A-A shown in FIG. 12;

(15) FIG. 14 shows a schematic top view of the section shown in FIGS. 11 to 13 of an arm of a rotor of a vertical wind turbine according to the invention;

(16) FIG. 15 shows a schematic top view of a vertical wind turbine according to the invention during operation to illustrate angular positions and force conditions at blades of the vertical wind turbine;

(17) FIG. 16 shows a schematic diagram to illustrate the function of a control device according to the invention belonging to a vertical wind turbine according to the invention;

(18) FIG. 17 shows a schematic diagram with a sample torque characteristic curve of a pitch motor according to the invention for a vertical wind turbine according to the invention;

(19) FIG. 18 shows a schematic diagram with sample cam disks for controlling a pitch motor for a vertical wind turbine according to the invention;

(20) FIG. 19 shows a schematic perspective view of a test bench for determining a positioning error of a pitch motor of a vertical wind turbine according to the invention;

(21) FIG. 20 shows a schematic diagram of a positioning error of a pitch motor according to the invention, which has been determined by means of the test bench shown in FIG. 19, over a plurality of control cycles;

(22) FIG. 21 shows a schematic diagram of a positioning error of a pitch motor according to the invention over one control cycle at a; and

(23) FIG. 22 shows a schematic diagram of a positioning error of a pitch motor according to the invention over one control cycle at a cut-out wind speed.

IMPLEMENTATION OF THE INVENTION

(24) For better comprehension of the present invention, reference is made to the drawings in the following. The drawings merely show exemplary embodiments of the subject-matter of the invention; as described above, features can be arbitrarily combined with one another or also omitted, depending on the respective requirements.

(25) FIG. 1 shows a schematic perspective view of a vertical wind turbine according to the invention 1. The vertical wind turbine 1 extends along a longitudinal direction X, a transverse direction Y, and a vertical direction Z, which together define a Cartesian coordinate system. The vertical wind turbine 1 includes a rotor 2, a nacelle 3, a tower system 4, footings 5, and a container-like switchgear box 6.

(26) The rotor 2 includes a plurality of vertical blades 7, which are fastened by means of a blade mount 8 to a rotor hub 9, which is supported in the nacelle 3 so that it is able to rotate around a rotor rotation axis C.sub.2 that is vertically oriented, i.e. extends parallel to the vertical direction Z. The blade mount 8 includes rotor arms 10, which extend between the blades 7 and the rotor hub 9. A signaling and/or measuring unit 11 is positioned on the rotor hub 9 concentric to the rotor rotation axis C.sub.2.

(27) As a rule, the nacelle 3 is positioned at the top of the tower system 4, is cased-in in a sound-absorbing way, and contains a drive train of the vertical wind turbine 1 (generator, rotor bearing system, transmission, mechanical brake, and cooling/lubricating system, see FIG. 9). The tower system 4 is preferably embodied as a lattice mast tower. The footings 5 are preferably concrete footings, which absorb the load of the tower system 4, the nacelle 3, and the rotor 2. Other components such as electrical transformers, switch components, and a control device (see FIG. 16) of the vertical wind turbine 1 are preferably accommodated in the switchgear box 6.

(28) The blades 7 are supported so that they are able to rotate around a blade rotation axis C.sub.7, which likewise extends essentially parallel to the vertical direction Z. For the rotation of each of the blades 7 around its respective blade rotation axis C.sub.7, they are each provided with at least one pitch drive 12. At least one of the rotor arms 10 is connected to the pitch drive 12, which can thus help absorb a load of the blade 7.

(29) FIG. 2 shows a schematic front view of the vertical wind turbine 1. Here, it becomes clear that the blades 7 have a plurality of blade sections 13, namely an upper end section 13a, an upper middle section 13b, a lower middle section 13c, and a lower end section 13d. The upper end section 13a and upper middle section 13b together constitute an upper blade section 13e. The lower middle section 13c and lower end section 13d together constitute a lower blade section 13f. The pitch drive 12 is positioned between the upper middle section 13b and lower middle section 13c, i.e. between the upper blade section 13e and lower blade section 13f. Between the upper end section 13a and the middle end section 13b as well as between the lower middle section 13c and the lower end section 13d, respective cross-sectional change of a profile of the blades 7 is provided, respectively.

(30) At bearing points 14 between the upper blade section 13e and lower blade section 13f, the blades 7 are each connected by means of one of the arms 10 to the rotor hub 9, which is designed to transmit forces acting radially and axially relative to the rotor rotation axis C.sub.2, said forces therefore acting essentially in a horizontal plane, which is defined parallel to the longitudinal direction X and transverse direction Y, and along the vertical direction Z. At the pitch drive 12, between the upper middle section 13b and lower middle section 13c of the blades 7, forces are absorbed, which act both radially and parallel to the rotor rotation axis C.sub.2. Consequently, the entire weight load of the rotor 2 is absorbed at the pitch drive 12.

(31) Further, it is illustrated in FIG. 2 that the rotor hub 9 and the tower system 4 are each embodied as a tubular lattice structure. At the top of the tower system 4 embodied as a lattice mast tower, it tapers in the direction toward the nacelle 3 and at this location, absorbs all of the static and dynamic loads generated by the rotor 2. At the bottom of the tower system 4, the loads are transferred to the ground by means of the footings 5. The nacelle 3 can be accessed by means of a ladder (see FIG. 10).

(32) A maximum width B.sub.4 of the tower system 4 measured parallel to the longitudinal direction X at the footings 5 is 22 m, for example. A length L.sub.7 of the blades 7 measured parallel to the vertical direction Z is 54 m, for example. An overall height of the vertical wind turbine 1 measured to include a height of the footings extending above the ground is 105 m without the signaling and/or measuring mast 11, for example.

(33) FIG. 3 shows a schematic top view of the vertical wind turbine 1. Here, it becomes clear that the blades 7 have a blade profile and move on a circular path K around the rotor rotation axis C.sub.2. A diameter D.sub.K of the circular path K is 32 m, for example, and approximately corresponds to a maximum diameter of the tower system 4.

(34) FIG. 4 a detail IV indicated in FIG. 2 of one of the blades 7 of the vertical wind turbine 1. The blade 7 has vanes 19. Between the upper middle section 13b and lower middle section 13c, i.e. between the upper blade section 13e and lower blade section 13f, the blade 7 is supported in the pitch drive 12 on a motor shaft 25 of the pitch drive 12. Together with the motor shaft 25, the vanes 19 form a blade axis 26, which passes through the entire length of the blade 7 and the vanes 19 are supported so that they are able to move in rotating fashion around this axis. For example, the vanes 19 can be manufactured having a shell construction. To this end, the vanes 19 have a vane axis section and an outer skin for absorbing normal forces, flexural forces, and torsional forces as well as torques (see FIG. 5).

(35) FIG. 5 shows a detail V indicated in FIG. 4 of the blade 7 with the pitch drive 12 in a schematic cross-sectional view along the blade rotation axis C.sub.7. The pitch drive 12 has a pitch motor 27, which is positioned in a clearance 28 between the upper middle section 13b and lower middle section 13c of the blade 7. The pitch motor 27 is embodied as an electronically controlled, transmissionless, air-cooled torque motor and has a stator ring 29 and a rotor ring 30 that is circumferentially surrounded by the stator ring 29 and is spaced apart from it by a gap. A cooling body 31 with cooling fins 32 is fastened to an outer circumference surface of the stator ring 29 so as to be able to dissipate waste heat of the pitch motor 27.

(36) The rotor ring 30 of the pitch motor 27 is mounted on a rim 33, which is embodied as a kind of collar that is of one piece with the motor shaft 25, at which rim the rotor ring 30 is connected in a rotationally coupled fashion to the essentially cylindrical motor shaft 25 with the aid of fastening elements 34 in the form of bolts. The rotor ring 30 extends essentially on the outer circumference side along the motor shaft 25 and is positioned so that it is spaced radially apart from the motor shaft 25 by at most a small gap. By means of the rim 34, a drive torque of the pitch motor 27—which is electromagnetically generated between the stator ring 29 and the rotor ring 30 and acts in a direction oriented around the blade rotation axis C.sub.7—is transferred from the rotor ring 30 to the motor shaft 25.

(37) A motor housing 35 of the pitch motor 27 forms a motor interior 36 in which the rotor ring 30 is accommodated. The motor housing 35 has a top 37 and a bottom 38, which extend in a disk shape along and essentially parallel to the rim 33. On their inner circumference sides, the top 37 and bottom 38 are each respectively connected to a bearing seat 39. The top 37 and bottom 38 are connected to the stator ring 29 and cooling body 31 by means of walls of the motor housing 35 and, on a side of the pitch motor 27 facing the rotor arm 10 that supports the blade 7, are connected to a motor flange 40 of the pitch drive 12.

(38) The motor flange 40 provides end surfaces 41 at which the rotor arm 10 is connected to the motor flange 40 by means of a mounting collar 42 connected to the rotor arm 10. The mounting collar 42 provides a counterpart end surface 43 that faces radially away from the rotor rotation axis C.sub.2 in the direction toward the circular path K of the blades 7. The motor flange 40 and mounting collar 42 are connected to each other by means of connecting elements 44, which are embodied for example in the form of detachable connecting elements 44 such as bolted connections. Between the end surfaces 41 of the motor flange 40, there is an open space 40a in order to provide sufficient space in the region of the cooling fins 32 for heat dissipation or more precisely stated, to prevent a heat buildup.

(39) Reinforcing ribs 45 extend between the bearing seat 39 and motor flange 40 in order to be able to transmit the static and dynamic loads, which originate from the blade 7, from the bearing seat 39 via the motor housing 35 to the motor flange 40 with as little distortion of the motor housing 35 as possible. The reinforcing ribs 45 are each advantageously embodied of one piece with the motor housing 35, for example during the casting, and/or are connected by means of welding to the top 37, bottom 38, bearing seat 39, and motor flange 40 or to the top 37, bottom 38, and bearing seat 39; they extend away from the top 37 and bottom 38 in strut-like fashion. In addition to their reinforcing action, the reinforcing ribs 45 also contribute to the cooling of the pitch motor 37 through heat dissipation via the motor housing 35.

(40) At least one sensor element 46, for example in the form of an induction sensor, is provided in the wall of the motor housing in order to detect a rotation position of the motor shaft 25 and thus of the blade 7 for the control or regulation of the vertical wind turbine 1. Respective motor bearings 47 are positioned between the two bearing seats 39 and the motor shaft 25. For example, the motor bearings 47 are embodied in the form of spherical roller bearings. They transmit high radial forces from the blades 7 to the rotor arms 10 and also stiffen the rotor 2 as a whole. In order to protect the motor bearings 47 from harmful environmental influences, the motor bearings 47 are each accommodated in a bearing receiving chamber 48, which, to the greatest extent possible, is hermetically sealed by means of sealing elements 49.

(41) The sealing elements 49 seal the bearing receiving chamber 48, both in relation to the motor interior 36 and in relation to the surroundings of the vertical wind turbine 1. Toward the motor interior 36, the bearing receiving chamber 48 is sealed by means of inner rings 50, which—resting against the motor bearing 47 and, on the outer circumference side, against the sealing element 49 in the axial direction of the blade 7, both in and away from the upward direction Z, respectively—isolate the bearing receiving chamber 48 from the motor interior 36. The bearing receiving chamber 48 is sealed in relation to the surroundings of the vertical wind turbine 1 by means of outer rings 51, which respectively rest against the outside of the bearing seat 39 and enclose the sealing element 49 on the inner circumference.

(42) At its ends oriented toward the vanes 19, the motor shaft 25 is connected to a transition section 52 or transitions into it in integral fashion. The transition section 52 widens as it extends away from the pitch drive 12 and is mounted in a vane axis section 53, which rotationally couples the transition section 52 to the blade 7 in adapter fashion. To that end, connecting ends 55 of the transition section 52 extending in the direction along the blade rotation axis C.sub.7 are embodied in flange-like fashion and are additionally provided with a compensation weight holder 56 for holding a compensation weight 56a for the vane 19 so that they have flange sections 57 oriented axially away from the connecting ends 55, on which positive-fit elements 58 and other connecting elements 59 are provided, for example likewise detachable ones in the form of bolt connections, which create a positive-fit and/or force-fit engagement between the transition section or more precisely, its flange section 57, and the respective vane axis section 53. The motor shaft 25, the transition section 52, and the vane axis section 53 extend coaxial to one another. The vane axis section 53 supports an outer skin 60 of the blade 7.

(43) FIG. 6 shows a schematic perspective view of the pitch drives 12 in which the pitch motor 27 is provided with an aerodynamic cover in the form of a casing 61. The casing 61 has a upper shell 62 and a lower shell 63, which enclose the motor housing 35 of the pitch motor 27 like a cowling and thus cover the top 37 and bottom 38 together with the reinforcing ribs 45 and support ribs 46 as well as the motor flange 40, thus minimizing the size of a drive gap 64 that is formed between the pitch drive 12 and the blade 7 and minimizing the accompanying losses in pressure and output that occur at such a gap. Between the upper shell 62 and lower shell 63, an annular gap-shaped cooling opening 65 is formed, which axially surrounds the cooling body 31 and through which the cooling fins 32 freely extend so that with ambient air circulating unhindered around them, they can give off the waste heat of the pitch motor 27 to the surroundings of the vertical wind turbine 1.

(44) The drive gap 64 is further reduced in that the casing 61 provides an extension 66, which is formed in accordance with aerodynamic aspects, which adjoins the upper shell 62 and lower shell 63, and outer contour of which in a projection along the blade rotation axis C.sub.7 essentially corresponds to a blade profile of the blades 7. In the direction toward the rotor arm 10, the casing 61 is provided with end caps 67, which rest flush against the motor flange 40 and an outer diameter of which, at least in some places, is adapted to an outer diameter of the mounting collar 42. An outer contour of the mounting collar 42 is in turn adapted to an outer contour of the rotor arm 10. As a result, the end caps 67, the motor flange 40, the connecting flange 42, and the rotor arm 10 transition into one another with outer contours that are as flush with one another as possible and there is an aerodynamically advantageous transition between the pitch drive 12 and the blade mount 8.

(45) Further, it is illustrated in FIG. 6 that at least one intake socket 68a or intake opening and a discharge opening 68b are formed into the casing 61 of the pitch drive 12. Between the intake socket 68a and the discharge opening 68b, a cooling air duct 69 is shaped into the casing 61 or is formed between the casing 61 and the pitch drive 12. The intake opening embodied in the intake socket 68a is oriented in the circumference direction along the circular path K so that during the rotation of the rotor 2, the intake socket 68a takes in ambient air and this is conveyed through the cooling air duct 69 along the cooling body 31 or more specifically its cooling fins 32 to the discharge opening 68b. This prevents cooling air in the region of the cooling body 31 or more precisely its cooling fins 32 from flowing away from them, which helps to ensure a cooling of the pitch drive 12 that satisfies the respective requirements. In addition, two intake sockets 68a and a discharge opening 68b are advantageously provided, with a combined cross-section of the intake sockets 68a being greater than a cross-section of the discharge opening 68b, as a result of which along the two cooling air ducts 69 per pitch drive 12 that are respectively formed between the intake sockets 68a and the discharge opening 68b, the cooling air tends to experience a slight compression and thus acceleration, which helps to further increase a cooling capacity of the cooling air.

(46) FIG. 7 shows a schematic perspective view of a pitch motor 27 together with the blades 7 mounted thereon, particularly showing the motor flange 40 of the pitch motor 27 for fastening the pitch motor 27 together with the blade 7 to one of the rotor arms 10 of the rotor 2 of the vertical wind turbine 1. Here, it becomes clear that the open space 40a at the motor flange 40 is formed between upper housing half 35a and a lower housing half 35b of the motor housing 35. As a result, the motor flange 40 has an upper flange half 41a and a lower flange half 41b, between which the pitch motor 27 is accessible from the respective rotor arm 10 and between which cooling air can flow along the cooling body 31. The reinforcing ribs 45 on the motor housing 35 each provide a stabilization of the upper housing half 35a and the lower housing half 35b considered individually, in order to ensure that they are sufficiently rigid.

(47) FIG. 8 shows a schematic partial cross-sectional view of the pitch motor 27. In order to be able to lock the pitch motor 27 in position and thus prevent the blade 7 from being able to execute rotations around its blade rotation axis C.sub.7, the pitch drive 12 is provided with a motor-braking and/or motor-locking unit 27a, which is arranged on the motor housing 35, is accessible via the motor flange 40, and is manually actuatable. For example, the motor-braking and/or motor-locking unit 27a is embodied to cooperate in a form-locking manner with the compensation weight holder 56, for example in that a locking bolt 27b of the motor-braking and/or motor-locking unit 27a engages in a positive-fit with a corresponding locking opening 27c of the compensation weight holder, so that a locking of the motor shaft 25 relative to the motor housing 35 in at least one rotation direction around the blade rotation axis C.sub.7 for maintenance and/or safety purposes prevents the pitch motor 27 and thus the blade 7 from executing any rotation around the blade rotation axis C.sub.7.

(48) In addition, a first rotary position transducer 46a and a second rotary position transducer 46b extend parallel to each other along the outer circumference of the motor shaft 25 and are embodied to be detected by the at least one sensor element 46. The first rotary position transducer 46a is embodied for example as an absolute position transducer. The second rotary position transducer 46b is embodied for example as a relative position transducer. The first rotary position transducer 46a embodied as an absolute position transducer can for example have increments at least some of which are positioned at irregular distances from one another along the outer circumference of the motor shaft 25. The second rotary position transducer 46b embodied as a relative position transducer can for example have increments positioned at regular distances from one another along the outer circumference of the motor shaft 25. As a result, the first rotary position transducer 46a permits the determination of an absolute position of the motor shaft 25 and thus of the blade 7 around the blade rotation axis C.sub.7. The second rotary position transducer 46 permits the determination of a relative position of the motor shaft 25 and thus of the blade 7 around the blade rotation axis C.sub.7. Using the first rotary position transducer 46a and second rotary position transducer 46b in this way makes it possible to determine the rotation position of the motor shaft 25 and of the blade 7 with a high position resolution.

(49) FIG. 9 shows a schematic cross-sectional view of a drive train 70 of the vertical wind turbine 1 along a drive shaft 71 of the drive train 70, whose drive rotation axis C.sub.71 extends coaxial to the rotor rotation axis C.sub.2. The rotor hub 9 has a pedestal 72 that forms a stud 73, which likewise extends coaxial to the drive rotation axis C.sub.71 and rotor rotation axis C.sub.2. At the place where the pedestal 72 tapers toward the stud 73, a hub shoulder 74, which points away from the upward direction Z, is formed on the pedestal 72 and rests on a transition ring 75, which in turn rests axially in a direction oriented away from the upward direction Z on a first rotor bearing 76a, which constitutes a part of a rotor bearing system 76.

(50) In addition to the first rotor bearing 76a, the rotor bearing system 76 also includes a second rotor bearing 76b and a third rotor bearing 76c. The first and second rotor bearings 76a, 76b are embodied for example as prestressed conical roller bearings and transmit radial loads resulting from wind loads to the tower system 4. For this purpose, the first and second rotor bearings 76a, 76b are mounted on a rotor shaft 78 by means of a separate bearing bush 77. The part of the rotor bearing system 76 comprising the first and second rotor bearings 76a, 76b is assembled in an axially free-floating fashion in a hub connection 79 that constitutes a machine support and therefore remains free of vertical loads. The third rotor bearing 76c absorbs the vertical loads of the rotor 2 and thus essentially its weight force and for this purpose, is advantageously embodied in the form of an axial spherical roller bearing, which introduces the vertical loads directly into the nacelle 3.

(51) Below the nacelle 3, a transmission 80 of the vertical wind turbine 1 is arranged in which a rotor speed of the rotor shaft 78 is converted into a generator rotation speed at an output shaft 82 of the transmission 80. A clutch unit 83, for example in the form of a double-Catalan, torsionally rigid steel disk clutch, connects the output shaft 82 in a torque-transmitting fashion to a generator shaft 84 of a generator 85, for example a synchronous machine with permanent magnets, in order to produce electrical current, in this case for example with a maximum power of 750 kW. The clutch unit 83 prevents a redundant dimensioning of bearing forces. To limit the torque, the rotor shaft 78 is provided with an intended break point 86 (for example with a nominal torque of 500 kNm; an intended break moment of 1000 kNm; and a permissible transmission peak torque of 1500 kNm).

(52) The transmission 80 converts the low rotor speed according to the invention into a high generator rotation speed. For example, a transmission step-up factor i amounts to roughly 65 to 75, preferably approx. 70. A transmission housing 87 of the transmission 80 is rigidly screw-mounted to the hub connection by means of a flange bell 88. This results in a direct feedback of the high operating torque. Between the rotor shaft 78 and drive train 70, there is a double-cardan, spherically ground double-tooth clutch 89, which transmits the torque of the rotor 2 to the transmission 80 without redundant dimensioning of bearing forces.

(53) In addition, a pitch pipe 90 passes through the transmission 80 coaxial to the rotor shaft 78 and serves as a feed-through for control wires and power cables for the pitch drive 12. The pitch pipe 12 is driven to a point above the intended break point 86 in the coupling 89 by being rotationally coupled to the rotor 2. Thus, after a breakage occurs at the intended break point 86 and after the system subsequently coasts to a stop, the cables and lines for transmitting signals and/or power (see FIG. 16) are not twisted and therefore remain intact. At the lower end of the pitch pipe 90, a slip ring packet 90a is provided, in which the mutual cooperation of corresponding brushes and slip rings (not shown) connects the signal wires, control wires, and power cables for the pitch drive 12 in an electrically conductive fashion to corresponding control wires and power cables inside the tower 4, which then lead to the switchgear box 6.

(54) FIG. 9 also shows that the transmission 80 has a plurality of transmission stages, in the present case for example a first transmission stage 80a, a second transmission stage 80b, and a third transmission stage 80c. The first transmission stage 80a and second transmission stage 80b are each embodied as a planetary gear stage 81. The planetary gear stages 81 have respective planet gears 81a, which are each supported on a strut 81c by means of a flexible pin 81b. With their respective gears, the planet gears 81a engage simultaneously with a ring gear 81d and a sun gear 81e of the respective planetary gear stage 81. The sun gear 81e of the second transmission stage 80b is connected in a torque-transmitting way by means of a slip clutch 89a to a gear 81f of the third transmission stage 80c, which is embodied as a spur gear pair. The gear 81f engages with a pinion 81g of the third transmission stage 80c. The pinion 81g is connected in a torque-transmitting way to the drive shaft 82 for the generator 85.

(55) FIG. 1 shows a schematic perspective view of an embodiment according to the invention of the hub connection 79 of the vertical wind turbine 1. The hub connection 79 includes a cylindrical, drum-like integrally formed base body 91, which provides a feed-through 92 for accommodating a shaft bearing unit 93 (see FIG. 9) of the drive train 70. Supporting feet 94 are fastened equidistantly to the outer circumference side of the base body 91 and extend out radially from it. The supporting feet 94 each provide a horizontally oriented rest 95 for mounting the hub connection 80 onto the tower system 4. The supporting feet 94 can for example be composed of welded-together plates and be integrally connected to the base body 91 by welding or be flange-mounted to it; the base body can in turn also be composed of welded-together plates.

(56) The hub connection 79 can be composed of a plurality of identically shaped segments, which each provide two flange ends, at which they are connected to one another enclosing a circle and thus combine to form the feed-through 92 for accommodating the shaft bearing unit 93. Each of the segments 96 constitutes a supporting arm. At the distal end of each supporting arm oriented away from the feed-through 92, a vertically extending supporting tab can be formed, which lies in a respective radial plane relative thereto for being mounted onto the tower system 4. For example, the segments can be cast individually or in one piece, which can help to reduce manufacturing costs, particularly in mass production and can help to adapt material thicknesses of the segments in high-stress points and can also help to provide rounded regions on it in order to reduce stress concentrations, for example by having the flange ends transition into the supporting arms by forming a curved profile.

(57) The rotor hub 9 itself can likewise be composed of segments 95 or be integrally cast together with its segments 95. On each of the segments 95, there is a flange end 97 for fastening one of the rotor arms 10 to the rotor hub 9. Each flange end 97 can be formed onto a supporting arm 98, which is provided on the rotor hub 9 and extends away from the rotor rotation axis C.sub.2. The supporting arms 98 can be formed of one piece with the respective segment 95.

(58) The rotor arms 10 have an upper arm half 10a and a lower arm half 10b, which in the radial direction of the rotor 2 oriented toward the rotor hub 9, are brought together at a hub end 10c of the rotor arm 10. At the hub end 10c, a rotor arm hub flange 10d is provided for fastening the rotor arm 10 to one of the flange ends 97 of the rotor hub 9. Between the upper arm half 10a and lower arm half 10a extending along a longitudinal axis span of the rotor arm 10, a connecting segment 10e of the rotor arm 10 is provided, which connects the upper arm half 10a and lower arm half 10b to each other along their longitudinal span.

(59) The signaling and/or measuring unit 11 can be positioned on a covering cap 99 for the rotor hub 9 and for example includes a plurality of wind speed sensors 104 and wind direction sensors 105, which are each fastened to a rod 106 that extends away from the covering cap 99. Viewed in the axial direction of the vertical wind turbine 1, the rods 106 can each be positioned offset from the rotor arms 10 so that as much as possible, the respective wind speed sensors 104 and wind direction sensors 105 do not lie in the wind shadow of the blades 7 as the rotor 2 rotates around its rotor rotation axis C.sub.2 or in any case, only lie in their wind shadow for the shortest possible time intervals.

(60) FIG. 11 shows a schematic front view of a section of one of the rotor arms 10 of the rotor 2 of the vertical wind turbine 1. Here, it becomes clear that a rotor arm blade flange 10g and the mounting collar 42 for fastening the rotor arm to the blade 7 and to the respective motor flange 40 are provided at a distal rotor arm end 10f. The depicted section of the rotor arm 10 can be either the upper arm half 10a or the lower arm half 10b, which are shaped identically in order to facilitate the production of the rotor arms 10 and to minimize their production costs.

(61) FIG. 12 shows a schematic side view of the section shown in FIG. 11 of one of the rotor arms 10 of the vertical wind turbine 1. Here, it becomes clear that the rotor arms 10 taper in the vertical direction Z from the hub end 10c toward the rotor arm end 10f.

(62) FIG. 13 shows a schematic cross-sectional view of the section shown in FIGS. 11 and 12 of one of the rotor arms 10 of the vertical wind turbine 1, along the cross-sectional line A-A shown in FIG. 12. Here, it becomes clear that in the region of the hub end 10, the rotor arms 10 have a wall thickness that is sufficient for embodying the vane axis section 53 in such a way that the respective vane 19 can be fastened to the flange section 57.

(63) FIG. 14 shows a schematic top view of the section shown in FIGS. 11 to 13 of the rotor arm 10 of the vertical wind turbine 1. Here, it becomes clear that the rotor arms 10 likewise taper transversely to the vertical direction Z vertical direction Z from the hub end 10c toward the rotor arm end 10f.

(64) FIG. 15 shows a schematic top view of the vertical wind turbine 1 to illustrate angular positions and force conditions at the blades 7 during the operation of the vertical wind turbine 1. During the operation of the vertical wind turbine 1, the wind flows against the blades 7 at a wind speed v.sub.W. The rotation of the rotor 2 around the rotor rotation axis C.sub.2 produces an angular velocity ω of the rotor 2, which, multiplied by a radius R.sub.K of the circular path K that corresponds to half of the diameter D.sub.K of the circular path K, yields a circumferential speed v.sub.U of the blades 7 along the circular path K according to equation (1) below:
v.sub.U=ω×R.sub.K  (1)

(65) A difference between the wind speed v.sub.W and the circumferential speed v.sub.U yields a relative speed v.sub.R of the blade 7 moving along the circular path K in relation to the wind according to equation (2) below:
v.sub.R=u.sub.W−v.sub.U  (2)

(66) Between the vectors of the circumferential speed v.sub.U and the relative speed v.sub.R at the blade 7, there is an angle of incidence γ, which is calculated according to equation (3) below from a sum of a relative angle of incidence or angle of attack α and a gradient angle or pitch angle β:
γ=α+β  (3)

(67) The angle of attack α is respectively measured between the vector of the circumferential speed v.sub.U and a chord line 100 of the blades 7, which extends in a straight line between a leading edge 101 and a trailing edge 102. The pitch angle β is measured between the vector of the relative speed v.sub.R and the chord line 100. The blades 7 have a symmetrical blade profile, by means of which the blade chord forms a plane of symmetry of the blades 7 or their vanes.

(68) Through the rotation of the rotor 2 around the rotor rotation axis C.sub.2, the relative speed v.sub.R is a function of an azimuth angle Θ of the rotor 2, which is measured for example for the respective rotor arm 10 starting from a zero point at a position 90° from the wind direction, facing into the wind and rotating relative to a main axis of the vertical wind turbine 1. A tangent of the angle of incidence γ is calculated as a function of the wind speed v.sub.W, the relative speed v.sub.R, and the azimuth angle Θ or as a function of a tip speed ratio λ and the azimuth angle Θ according to equation (4) below:

(69) $\begin{array}{cc}\tan \gamma =\frac{v_W\sin \theta }{v_R+v_W\cos \theta }=\frac{\sin \theta }{\mathrm{\lambda cos\theta }},& \left(4\right)\end{array}$
where the tip speed ratio λ in turn, according to equation (5) below, corresponds to a ratio of the circumferential speed v.sub.U to the wind speed v.sub.W and according to the invention, is to be set as optimally as possible and kept constant by means of the respective pitch drive 12 or more precisely, its pitch motor 27, in accordance with the respective wind conditions with varying pitch angles β in order to maximize an energy yield or performance of a vertical wind turbine 1 according to the invention:

(70) $\begin{array}{cc}\lambda =\frac{v_U}{v_W}& \left(5\right)\end{array}$

(71) In order to minimize an adjusting torque of the pitch drive 12—which is required to vary the pitch angle β by rotating the blade 7 around the rotor rotation axis C.sub.7—, it is advantageous if a static center of gravity of the blade 7 lies on or as close as possible to the rotor rotation axis C.sub.7. For example, the rotor rotation axis C.sub.7 is positioned on the chord line 100 at 20 to 23%, preferably 21.5%, of a rotor blade depth measured from the leading edge 101. In order to position the center of gravity on the rotor rotation axis C.sub.7, the counterweight 56a is provided in the region of the pitch drive 12 and if need be, an additional counterweight 103 is positioned in the region of the leading edge 101 in the blade 7. For example, the additional counterweight 103 is composed of rod segments, preferably of a round steel rod with diameters of between 60 and 100 mm, most preferably 80 mm. The rod segments are fastened to the ribs 54. The segments can be advantageously connected to one another in an electrically conductive fashion. As a result, the additional counterweight 103 can perform a double function in that it also serves as a lightning rod.

(72) In addition, the vertical wind turbine 1 has at least one wind speed sensor 104 and/or wind direction sensor 105. The wind speed sensor 104 and/or wind direction sensor 105 is positioned at the upper end of the signaling and/or measuring mast 11 and/or on at least one of the blades 7 or on all of the blades 7. The wind speed sensor 104 and/or wind direction sensor 105 is preferably fastened to the blade 7 in the region of the pitch drive 12 because wind speeds and/or directions measured there are highly relevant for the control of the pitch drive 12.

(73) In order to keep the wind speed sensor 104 and/or wind direction sensor 105 outside of air turbulence caused by the blade 7, the wind speed sensor 104 and/or wind direction sensor 105 is positioned at the distal end of a rod 106, which is fastened to the blade 7 or pitch drive 12 and, oriented radially away from the rotor rotation axis C.sub.2, protrudes beyond the circular path K into a region in the vicinity of the vertical wind turbine 1, which lies as far as possible outside of air flow boundary layers that are formed around the rotor 2 and its components, i.e. largely outside of the influence range of the blade 7.

(74) FIG. 16 shows a schematic diagram to illustrate the function of a control device according to the invention 107 of the vertical wind turbine 1. The control device 107 includes a supply unit 108, which is on the one hand connected to a motor control unit 109 that includes a power section 110 and on the other hand, is connected to a choke 111 and a filter 112 in order to ensure the most malfunction-free and error-free power supply possible. For example, the power unit 110 is embodied as an inverter.

(75) Via lines 113 for transmitting signals and/or power, the motor control unit 109 is connected to the pitch drive 12, a power supply unit 114, and a control unit 115 for monitoring and controlling the vertical wind turbine 1. The power supply unit 114 includes a main power supply unit 116 and an auxiliary power supply unit 117, the latter ensuring an emergency power supply to the control device 107 if the main power supply unit 116 fails or is not available.

(76) In addition, the control device 107 includes a motor protection unit 118 and a data transmission unit 119. The pitch drive 12 also includes a rotary position transducer 120 with a position sensor 121 for monitoring a rotation position of the rotor ring 30 relative to the stator ring 29. The pitch motor 27 also includes a motor unit 122, which includes at least the stator ring 29 and the rotor ring 30, and a temperature measuring unit 123, which has a first temperature sensor 124 and at least one other temperature sensor 125. For example, the first temperature sensor 124 is embodied as a resistance-dependent temperature sensor (KTY), whereas the other temperature sensor 125 is embodied for example as a temperature sensor with a positive temperature coefficient (PTC).

(77) During operation of the vertical wind turbine 1, the power section 110 of the motor control unit 109 of the control device 107 inverts—for example continuously—a current that is required to drive the pitch motor 27. For example, the power element 110 can output a continuous current of 100 to 200, preferably 150 A.sub.RMS, and produce a peak current of 200 to 250, preferably 210 A.sub.RMS, so that it is possible to quickly obtain a maximum torque of the pitch motor 27. The control unit 115 cyclically calculates a set-point value S for the adjustment of each of the blades 7, for example in the form of a set-point pitch angle β.sub.s, and supplies it via the corresponding line 113 to the motor control unit 109.

(78) With the aid of the rotary position transducer 120, an actual value I such as an actual pitch angle β.sub.I is determined and is transmitted via the corresponding line 113 to the motor control unit 109. Based on the set-point value S and the actual value I, the motor control unit 109 determines a differential value d, for example an angular deviation δ, and based on it, derives a control value U, for example in the form of a control current A, which is transmitted to the respective drive unit 12 and/or the motor unit 122 of the pitch motor 27. Correspondingly, the motor control unit 109 adjusts the pitch angle β according to the invention with the least possible angular deviation β.

(79) With the aid of the temperature sensor 124 and the other temperature sensor 125, the temperature measuring unit 123 detects a first temperature measurement value T and at least one other temperature measurement value T.sub.x, which are determined for redundancy reasons and/or for different uses. Thus, the temperature measurement value T is transmitted via one of the lines 113 to the motor protection unit 118. The motor protection unit 118 compares the temperature measurement value T to a temperature limit value and if the temperature limit value is exceeded, can transmit an alarm signal via the corresponding line 113 to the motor control unit 109, where preventive measures for protecting the respective pitch drive 12 are initiated, for example an emergency shut-off or interruption of the power supply. At the same time, the motor protection unit 118 can use the corresponding line 113 to transmit temperature values for relaying temperature data to the motor control unit 109 and/or control unit 115 and the data transmission unit 119.

(80) The other temperature measurement value T.sub.X is transmitted via corresponding lines 113 directly to the motor control unit 109 in order to keep a temperature of the drive unit 12 and the components thereof within the scope of a predetermined or specified operating temperature. In the motor control unit 109, immediate temperature control measures can be initiated, whereas in the control unit 115, longer-term temperature control measures can be carried out. Thus with the aid of the alarm signal sent by the motor protection unit 118 on the basis of the temperature measurement value T, a rapid temperature control can be carried out in order to protect the drive unit 12, whereas the temperature data that are related to the control unit 115 can be used to perform a long-term temperature control and through the direct relaying of the other temperature measurement value T.sub.X to the motor control unit 109, a middle-term temperature control is possible.

(81) The control device 107 is configured and set up to implement the following ten operating modes M0 to M9 of the vertical wind turbine 1: M0: The vertical wind turbine 1 is switched off in a zeroth operating mode M0. M1: Start-up readiness of the vertical wind turbine 1 from still air in a first operating mode M1 at wind speeds below a starting wind speed v.sub.1, i.e. with 0<v.sub.W<v.sub.1, for example where v.sub.1=3 m/s; M2: Start-up of the vertical wind turbine 1 in a second operating mode M2 at wind speeds above the starting wind speed v.sub.1 and below a nominal wind speed v.sub.2, i.e. with v.sub.1≤v.sub.W<v.sub.2, for example where v.sub.2=12 m/s; M3: Switching of the vertical wind turbine 1 from a resistance mode where λ≤1 starting into a fast mode where λ>1 in a third operating mode M3 or start-up mode at wind speeds above the starting wind speed v.sub.1 and below a first cut-out wind speed v.sub.3, i.e. with v.sub.1≤v.sub.W<v.sub.3, for example with a minimum rotation speed of the rotor of 4 [rpm] and a first cut-out wind speed v.sub.3=20 m/s (average measured over 10 minutes); M4: Shut-down of the vertical wind turbine 1 in a fourth operating mode M4 at wind speeds above the first cut-out wind speed v.sub.3 or a further cut-out wind speed v.sub.4, i.e. with v.sub.W>v.sub.3 or v.sub.W>v.sub.4, respectively, for example where v.sub.4=30 m/s (average measured over 3 seconds); M5: Restarting of the vertical wind turbine 1 in a fifth operating mode M5 when the wind speed falls below a restart wind speed v.sub.5 after a shut-down in the fourth operating mode M4, for example where v.sub.5=18 m/s; M6: Operation of the vertical wind turbine 1 at a constant tip speed ratio λ in a sixth operating mode M6 or partial load mode for wind speeds above the starting wind speed v.sub.1 and below a nominal wind speed v.sub.2, i.e. with v.sub.1≤v.sub.W≤v.sub.2, for example with a tip speed ratio λ between 2 and 2.6, preferably between 2.2 and 2.4, most preferably 2.3 at a nominal wind speed v.sub.2 of 12 m/s and a circumferential speed of the blades 7 on the circular path K of v.sub.U=27.6 m/s; M7: Operation of the vertical wind turbine 1 with a variable tip speed ratio λ in a seventh operating mode M7 or nominal operation mode or also full-load operation with a nominal speed of the rotor of for example 16.5 [rpm] at wind speeds above the nominal wind speed v.sub.2 and below the first cut-out wind speed v.sub.3 or the further cut-out wind speed v.sub.4, i.e. in a nominal wind speed range with v.sub.2<v.sub.W<v.sub.3 or v.sub.2<v.sub.W<v.sub.4; for example with a tip speed ratio λ between 1 and 1.8, preferably between 1.3 and 1.5, most preferably 1.38 at a first cut-out wind speed v.sub.3 of 20 m/s; M8: Emergency shut-down of the vertical wind turbine 1 in an eighth operating mode M8 at extreme wind speed increase gradients dv.sub.W/dt greater than a shut-down gradient of the wind speed; and M9: Switching-off of the vertical wind turbine 1 in a ninth operating mode M9 to switch the vertical wind turbine 1 into the zeroth operating mode from one of the operating modes M1 to M8.

(82) FIG. 17 shows a schematic diagram of a sample torque characteristic curve of the pitch motor 27. The diagram shows a maximum torque Tp, a nominal torque Ti, and continuous torque Tc of the pitch motor 27 over the rotation speed of the pitch motor 27. The pitch motor 27 can rapidly produce the maximum torque Tp in order to spontaneously, i.e. within a very short, extremely limited time, perform a quick adjustment of the respective blade 7. When the maximum torque Tp is exceeded, i.e. when an overload occurs, the motor slips and is thus inherently safe, i.e. no damage to the motor occurs. The nominal torque Ti can be used continuously until a temperature limit value is exceeded. As a rule, the continuous torque Tc is available on an ongoing basis and does not lead to temperature limit values being exceeded.

(83) FIG. 18 shows a schematic diagram with sample cam disks for controlling the pitch motor 12, namely a first cam disk S1, which is provided for example for the nominal wind speed v.sub.2 of for example 12 m/s, and a further cam disk S2, which is provided for the first cut-out wind speed v.sub.3 of for example 20 m/s. Between these two wind speeds, for example a nominal-load operation or full-load operation of the vertical wind turbine 1 in the seventh operating mode M7 is provided, in which the rotor 2 rotates at a nominal speed and the generator 85 outputs its nominal power. For each cam disk S1, S2, the set-point value S of the pitch angle β is represented as the set-point pitch angle β.sub.S in dependence of the azimuth angle Θ.

(84) At the nominal wind speed v.sub.2, the set-point pitch angle β.sub.S at an azimuth angle Θ of 0° is less than 0°, for example in the range from −2 to −3°. On the way to an azimuth angle Θ of 90°, the set-point pitch angle β.sub.S first passes through a local maximum of −2 to −3° at an azimuth angle Θ of approx. 20° and then passes through an inflection point between −3 and −4° at an azimuth angle Θ of approx. 20° until the set-point pitch angle Θ.sub.S at an azimuth angle Θ of approx. 50° reaches an absolute minimum of approx. −10°.

(85) At an azimuth angle Θ of 180°, the set-point pitch angle β.sub.S for the nominal wind speed v.sub.2 is once again approx. 2 to −3° and then, at an azimuth angle Θ of approx. 200°, reaches a value of 0°. At an azimuth angle Θ of approx. 250°, the set-point pitch angle β.sub.S for the nominal wind speed v.sub.2 reaches its absolute maximum of approx. 2 to 3° and then at an azimuth angle Θ of approx. 290° once again reaches a value of 0° and at approximately the same time, passes through an inflection point. Then the set-point pitch angle β.sub.S passes through a local minimum of approx. −3 to −4° at an azimuth angle Θ of approx. 330° and finally, at an azimuth angle Θ of approx. 360°, returns once again to its initial range of −2 to −3°.

(86) At the first cut-out wind speed v.sub.3, the set-point pitch angle β.sub.S at an azimuth angle Θ of 0° is less than 0°, for example in the range from −1 to −2°, and is thus less than the set-point pitch angle β.sub.S at an azimuth angle Θ of 0° at a nominal wind speed v.sub.2. On the way to an azimuth angle Θ of 90°, without a local maximum, the set-point pitch angle β.sub.S passes through an inflection point between −14 and −16° at an azimuth angle Θ of approx. 45° until, at an azimuth angle Θ of approx. 100°, the set-point pitch angle β.sub.S passes through another inflection point at approx. −30° and then, at an azimuth angle Θ of approx. 100°, reaches an absolute minimum of approx. −37° to −38°.

(87) At an azimuth angle Θ of 180°, the set-point pitch angle β.sub.S for the first cut-out wind speed v.sub.3, like the set-point pitch angle β.sub.S for the nominal wind speed v.sub.2, is approx. −2 to −3° and then, at an azimuth angle Θ of approx. 170°, reaches a value of 0° earlier than the set-point pitch angle β.sub.S for the nominal wind speed v.sub.2. At an azimuth angle Θ of approx. 230 to 240°, the set-point pitch angle β.sub.S reaches its absolute maximum of approx. 35° and then, at an azimuth angle Θ of approx. 270°, reaches an inflection point at approx. 25°. Then the set-point pitch angle β.sub.S passes through an inflection point at approx. 15° at an azimuth angle Θ of approx. 320° and finally, at an azimuth angle Θ of approx. 360°, returns once again to its initial range of −1 to −2°.

(88) FIG. 19 shows a schematic perspective view of a test bench 200 for determining a positioning error of the pitch motor 27 of the vertical wind turbine 1. On the test bench 200, a frame structure 201 is provided, to which is attached a holding arm 202 for holding the pitch drive 12 or pitch motor 27 and a transverse arm 203. The pitch drive 12 together with a section of the blade 7 is mounted on the holding arm 202 of the test bench 200 by means of the motor flange 40 similarly to how it would be mounted to the rotor arm 10 of the vertical wind turbine 1. The transition section 52 protruding out from the pitch motor 27 is accommodated in a shaft mount 204 of the test bench 200 so that it is able to rotate around the blade rotation axis C.sub.7.

(89) The shaft mount 204 is positioned in the middle of a swing arm 205, which is likewise held so that it is able to rotate around the blade rotation axis C.sub.7 in an extension 206 of the frame structure 201. A weight 207 is secured at each of the two ends of the swing arm 205 oriented away from the blade rotation axis C.sub.7. The weights 207 simulate a total mass of the blade 7. In addition, the ends of the swing arm 205 are connected to the transverse arm 203 by means of spring elements 208 in the form of coil spring packs and articulating linkages 209 fastened thereto. The spring elements 208 simulate wind forces.

(90) FIG. 20 shows a schematic diagram of a positioning error, which has been determined by means of the test bench 200 shown in FIG. 19, in the form an angular deviation δ of the pitch motor 27 in ° over time tin seconds for a plurality of control cycles during which a simulated azimuth angle Θ passes through a respective rotor rotation of 360°. After an initial transient response, which does not occur in the vertical wind turbine 1, the angular deviation δ reaches an absolute value of less than 1.5° for set-point pitch angles β.sub.S with absolute values of at most 30 to 40°.

(91) FIG. 21 shows a schematic diagram of a positioning error of the pitch motor 27 in the form of the angular deviation δ in ° over time tin seconds over one control cycle for the nominal wind speed v.sub.2. At a nominal wind speed v.sub.2, the angular deviation δ has an absolute value of always less than 0.5° and reaches a maximum absolute value of approx. 0.25° after respective local and absolute minima and maxima of the set-point pitch angle β.sub.S. In the vicinity of the inflection points of the set-point pitch angle β.sub.I, the angular deviation δ fluctuates around 0°.

(92) FIG. 22 shows a schematic diagram of a positioning error of the pitch motor 27 in the form of the angular deviation δ in ° over time tin seconds over one control cycle for the first cut-out wind speed v.sub.3. At the first cut-out wind speed v.sub.3, the angular deviation δ has an absolute value of always less than 1.5° and reaches a maximum absolute value of approx. 1.45° after respective local and absolute minima of the set-point pitch angle β.sub.S and reaches a maximum of approx. 0.6 at local and absolute maxima thereof. In the vicinity of the inflection points of the set-point pitch angle β.sub.I, the angular deviation δ likewise fluctuates around 0°. In general, therefore, the angular deviation δ turns out to be slightly higher at the first cut-out wind speed v.sub.3 than at the nominal wind speed v.sub.2.

(93) Deviations from the above-described embodiments and implementation examples are possible within the scope of the concept of the invention. A person skilled in the art will therefore recognize that characteristic values and parameters of the vertical wind turbine 1 and its components as well as values for controlling the components are dependent on the dimensions of the vertical wind turbine 1 and are subject to change. Consequently, all of the above-mentioned absolute values of physical variables, e.g. wind speeds, are chiefly indicated for a design instance of the vertical wind turbine 1 described here, with a nominal power of 750 KW, a nominal height of 105 m, a rotor diameter of 32 m, a length of the blades 7 of 54 m, a height of the blades 7 over the ground of 51 m, a height of the middle of the blades 7 above the ground of 78 m, a survival wind speed of 59.5 m/s, and an annual average speed of 8.5 m/s and can be varied in accordance with other design instances, which can in turn result in deviations of relative physical variables such as tip speed ratios.

(94) Also within the scope of the concept of the invention, unlike in the exemplary embodiment described here, more than two pitch drives 12 can be provided for each blade 7 or, for example, one pitch drive 12 can be provided for each blade section 13. In other words, two respective blades 7 or blade sections 13 can be provided, which are driven in a vertically separate way from each other. Thus for example, two pitch drives 12 can be positioned between two blades 7 or blade sections 13 and, as an upper and lower pitch drive 12, can be respectively associated with an upper and lower of the two blades 7 or blade sections 13. The upper blade or blade section 13 can thus be rotated around its blade rotation axis C.sub.7 independently of the lower blade 7 or blade section 13.

(95) Each of the two blades 7 or blade sections 13 can be associated with at least one wind speed sensor 104 and/or wind direction sensor 105. The at least one wind speed sensor 104 and/or wind direction sensor 105 is advantageously positioned in the middle of the respective blade 7 or blade section 13 and can be mounted on a rod 106 there as described above. Consequently, for each of the blades 7 or blade sections 13 positioned one above the other vertically, optimal pitch angles β can be separately set in order to take wind flow conditions that change in the vertical direction Z along the blade 7 into account during operation of the vertical wind turbine 1 and thus improve the efficiency of the turbine. This must be taken into consideration particularly for circular path diameters D.sub.K that are larger than 32 m, for example 45 m, in which case a total length L.sub.7 of the blades 7 would then be approx. 73 m, for example.

(96) TABLE-US-00001 Reference Signs List  1 vertical wind turbine  30 rotor ring  2 rotor  31 cooling body  3 nacelle  32 cooling fins  4 tower system  33 rim  5 footings  34 fastening element  6 switchgear box  35 motor housing  7 blade  35a upper housing half  8 blade mount  35b lower housing half  9 rotor hub  36 motor interior  10 rotor arm  37 wall/top  10a upper arm half  38 wall/bottom  10b lower arm half  39 bearing seat  10c hub end  40 motor flange  10d rotor arm hub flange  40a open space  10e connecting segment  41 end surface  10f rotor arm end  41a upper flange half  10g rotor arm blade flange  41b lower flange half  11 signaling and/or  42 mounting collar measuring unit  43 counterpart end surface  12 pitch drive  44 connecting element  13 blade section  45 reinforcing rib  13a upper end section  46 sensor element  13b upper middle section  46a first rotary position  13c lower middle section transducer  13d lower end section  46b second rotary position  13e upper blade section transducer  10f lower blade section  47 motor bearing  14 bearing point  48 bearing receiving chamber  19 vane  49 sealing element  25 motor shaft  50 inner ring  26 blade axis  51 outer ring  27 pitch motor  52 transition section  27a motor-braking and/or  53 vane axis section motor-locking unit  55 connecting end  27b locking bolt  56 compensation weight holder  27c locking opening  56a compensation weight  28 clearance  57 flange section  29 stator ring  58 positive-fit element  60 outer skin  59 further connecting element  61 casing  85 generator  62 upper shell  86 intended break point  63 lower shell  87 transmission housing  64 drive gap  88 flange bell  65 cooling opening  89 double-tooth clutch  66 extension  90 pitch pipe  67 end cap  90a slip ring packet  68a intake socket/opening  91 base body  68b discharge opening  92 feed-through  69 cooling air duct  93 shaft bearing unit  70 drive train  94 supporting feet  71 drive shaft  95 rest  72 pedestal  96 segment  73 stud  97 flange end  74 hub shoulder  98 supporting arm  75 transition ring  99 covering cap  76 rotor bearing system 100 chord line  76a first rotor bearing 101 leading edge  76b second rotor bearing 102 trailing edge  76c third rotor bearing 103 additional counterweight  77 bearing bush 104 wind speed sensor  78 rotor shaft 105 wind direction sensor  79 hub connection 106 rod  80 hub connection 107 control device  80′ hub connection 108 supply unit  80 transmission 109 motor control unit  80a first transmission stage 110 power section  80b second transmission stage 111 choke  80c third transmission stage 112 filter  81 planetary gear stage 113 line  81a planet gear 114 power supply unit  81c strut 115 control unit  81d ring gear 116 main power supply unit  81e sun gear 117 auxiliary power supply unit  81f gear 118 motor protection unit  81g pinion 119 data transmission unit  82 output shaft 120 rotary position transducer  83 clutch unit 121 position sensor  84 generator shaft 122 motor unit 124 temperature sensor 123 temperature measuring unit 125 other temperature sensor S2 further cam disk. 200 test bench T temperature measurement 201 frame structure value 202 holding arm T.sub.x other temperature meas. 203 transverse arm value 204 shaft mount Tc continuous torque 205 swing arm Ti nominal torque 206 extension Tp maximum torque 207 weight U control value 208 spring element R.sub.K radius of the circular path 209 articulating linkage X longitudinal direction i transmission step-up factor Y transverse direction d differential value Z vertical direction, upward t time direction v.sub.W wind speed α angle of attack v.sub.U circumferential speed β pitch angle v.sub.R relative speed β.sub.I set-point pitch angle v.sub.1 starting wind speed β.sub.S actual pitch angle v.sub.2 nominal wind speed δ angular deviation v.sub.3 first cut-out wind speed γ angle of incidence v.sub.4 further cut-out wind speed λ tip speed ratio v.sub.5 restart wind speed Θ azimuth angle A control current ω angular velocity B.sub.4 maximum width of the tower system C.sub.2 rotor rotation axis C.sub.7 blade rotation axis C.sub.71 drive rotation axis D.sub.K diameter of the circular path L.sub.7 length of the blades K circular path I actual value P1 resistance force P2 lifting force S set-point value S1 first cam disk