JP5088963B2 - Nacelle turning mechanism - Google Patents

Description

  The present invention relates to a nacelle turning mechanism for turning a nacelle in a tower of a windmill.

  2. Description of the Related Art Conventionally, wind turbines used as wind power generators are often used that have a nacelle provided at the top of a tower to which blades (blades) are attached and a generator or the like is disposed inside. In such a windmill, as disclosed in Patent Document 1, a nacelle turning mechanism for turning the nacelle according to the wind direction by driving a yaw driving device is provided. In Patent Document 1, in addition to a nacelle, a yaw driving device including a ring gear fixed to an upper portion of a wind turbine tower, a pinion as an output shaft meshing with the ring gear, and a nacelle including an electric motor for transmitting driving force to the yaw driving device A swivel device is disclosed.

  In the windmill described above, since the space in the nacelle is limited, downsizing of the equipment in the nacelle is required, and downsizing of the electric motor and the yaw driving device is required. On the other hand, since the diameter of the blade tends to increase in recent years, there is a demand for a yaw driving device with a high output specification that improves the output torque. On the other hand, an eccentric type reduction gear disclosed in Patent Document 2 is known as a reduction gear capable of realizing a large reduction gear ratio necessary for improving output torque and downsizing. In the eccentric type speed reducer disclosed in Patent Document 2, a crankshaft formed as an input shaft (112) provided with an eccentric body (114) is arranged on the rotation center line. In this eccentric type reduction gear, an inner pin (140) is integrally provided on a first support flange (150), which is a carrier that rotatably holds a crankshaft, and is eccentrically rotated as the crankshaft rotates. Power transmission is performed through an inner roller (142) disposed between the inner pin hole (130) and the inner pin (140) of the toothed gear (116).

JP 2001-289149 A (page 4, FIG. 1) JP 2006-64128 A (page 3-4, FIG. 1)

  By using the eccentric reduction gear disclosed in Patent Document 2 as the yaw drive device for the nacelle turning mechanism disclosed in Patent Document 1, it is conceivable to improve the output torque of the yaw drive device and reduce the size. However, since the eccentric type speed reducer disclosed in Patent Document 2 has a configuration in which power is transmitted between an inner pin provided on the carrier and an external gear via an inner roller that is a sliding member, driving efficiency is reduced. This leads to a decrease in (drive energy transmission efficiency), and the electric motor is also increased in size.

  In view of the above circumstances, an object of the present invention is to provide a nacelle turning mechanism capable of reducing the size of equipment in a nacelle and improving the output torque and drive efficiency of a yaw drive device. .

  The nacelle turning mechanism according to the first invention for achieving the above object includes a nacelle that is rotatably arranged with respect to a tower of a windmill, a ring gear that is fixed to the tower of the windmill, and an output that is fixed to the nacelle. A shaft engaging with the ring gear, and a yaw driving device for turning the nacelle with respect to a tower of a windmill, and an electric motor for transmitting a driving force to the input shaft of the yaw driving device and controlling an input rotational speed, The yaw driving device is arranged in parallel with the case, the internal teeth arranged on the inner periphery of the case, the external gear provided with the external teeth meshing with the internal teeth, and the rotation center line of the yaw driving device A crankshaft that rotates the external gear eccentrically, a crankshaft bearing that rotatably holds one end side and the other end side of the crankshaft, and a front side through the crankshaft bearing. A carrier that holds the crankshaft and to which the output shaft is fixed, and the electric motor controls the input rotational speed so that the rotational speed of the output shaft is 0.1 rpm or more. The output of the yaw driving device is controlled so as to be 0 rpm or less.

  According to the present invention, the yaw drive device meshing with the ring gear and the output shaft is driven by the electric motor, and the nacelle turns. The yaw driving device is configured as an eccentric type speed reducer in which the external gear rotates eccentrically while meshing with the internal teeth as the crankshaft rotates, and the output shaft rotates together with the carrier that holds the crankshaft. For this reason, it is possible to secure a large reduction ratio and improve the output torque and reduce the size. Further, in the present invention, the power transmission to the carrier is provided in parallel with the rotation center line of the yaw driving device, unlike the one through the sliding member such as the inner roller disclosed in Patent Document 2. This is performed via a crankshaft bearing that rotatably holds one end side and the other end side of the crankshaft. For this reason, it is possible to suppress a decrease in drive efficiency (drive energy transmission efficiency). In particular, regarding the magnitude of the rotational speed of the output shaft, the drive efficiency can be improved at 0.1 rpm to 1.0 rpm where the frictional resistance is large due to the boundary lubrication region. Thereby, size reduction of an electric motor can be achieved. In addition, as a result of verification by the inventors of the present invention regarding the magnitude of the rotation speed of the output shaft, it was confirmed that the driving efficiency rapidly deteriorates because the speed approaches the solid lubrication region at less than 0.1 rpm. Moreover, when exceeding 1.0 rpm, while the energy loss at the time of braking accompanying a rotation speed increase became large, it has confirmed that the improvement effect of drive efficiency converged rapidly. Therefore, according to the present invention, in the nacelle turning mechanism, it is possible to reduce the size of equipment in the nacelle and improve the output torque and drive efficiency of the yaw drive device.

  According to the present invention, in the nacelle turning mechanism, it is possible to reduce the size of equipment in the nacelle and to improve the output torque and drive efficiency of the yaw drive device.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. The embodiment of the present invention can be widely applied as a nacelle turning mechanism for turning a nacelle in a tower of a windmill.

  FIG. 1 is a schematic diagram for explaining the outline of a nacelle turning mechanism 1 according to an embodiment of the present invention and a wind turbine 101 to which the nacelle turning mechanism 1 is applied. As shown in FIG. 1, the windmill 101 includes a tower 102, blades 103, a nacelle turning mechanism 1, and the like. The tower 102 is installed so as to extend vertically upward from the ground, and a plurality of (three in this embodiment) blades 103 extending radially at equal angles are rotatably attached to the upper portion of the tower 102. A nacelle turning mechanism 1 is arranged. The nacelle turning mechanism 1 includes a nacelle 2, a ring gear 3, a yaw drive device 4, an electric motor 5, and the like.

  The nacelle 2 is disposed so as to be rotatable with respect to the tower 102 and is installed so as to turn in a substantially horizontal plane by a yaw driving device 4 described later. Inside the nacelle 2, a power transmission shaft 61, a speed increasing device 62, a brake device 63, a generator 64, a transformer 65, a yaw driving device 4, an electric motor 5, and the like are arranged. The power transmission shaft 61 is connected to the blade 103 via a hub, and the power transmission shaft 61 also rotates when the blade 103 is rotated by wind power. Then, the rotational driving force of the power transmission shaft 61 is increased in speed by the speed increaser 62 and is appropriately adjusted by the brake device 63 and input to the generator 64. As a result, power is generated in the generator 64, and the generated power is transmitted to the substation facilities and the like on the ground through the transformer 65 and further through the cable laid so as to pass through the tower 101 and the ground. Will be.

  FIG. 2 is a plan view schematically showing a state in which a part of the nacelle 2 is viewed from above. In FIG. 2, elements other than the ring gear 3 and the yaw driving device 4 in the nacelle 2 are omitted. The ring gear 3 shown in FIGS. 1 and 2 is fixed to the upper portion of the tower 102, and teeth that mesh with a pinion 14a provided on an output shaft 14 of the yaw drive device 4 described later are provided on the inner periphery. The teeth of the ring gear 3 can be provided not only on the inner periphery but also on the outer periphery.

  FIG. 3 is a front view of the electric motor 5 and a cross-sectional view of the yaw driving device 4. The electric motor 5 shown in FIGS. 1 and 3 is attached to the yaw driving device 4, and its output shaft 5 a is connected to the input shaft 60 of the yaw driving device 4 by key coupling so that the driving force is transmitted to the input shaft 60. Is provided. Then, the electric motor 5 rotates at a predetermined rotational speed (predetermined rotational speed), thereby controlling the input rotational speed of the yaw driving device 4 (the rotational speed of the input shaft 60 of the yaw driving device 4 is controlled). As configured). The yaw driving device 4 shown in FIGS. 1 to 3 includes a case 11, a pin inner tooth 22, a front speed reduction unit 12, a rear speed reduction unit 13, an output shaft 14, and the like, and is configured as an eccentric type speed reducer. A plurality of yaw driving devices 4 are provided in the nacelle 2 so as to be arranged along the inner periphery of the ring gear 3 (four in this embodiment). (Not shown).

  Further, as shown in FIG. 3, the yaw driving device 4 has a pinion 14a on the output shaft 14 positioned so as to protrude from the case 11 on one end side arranged on the lower side, and the other end arranged on the upper side. On the side, the electric motor 5 is attached to the case 11. In the yaw drive device 4, the rotational force input from the electric motor 5 disposed on the upper side is decelerated and transmitted via the front-stage deceleration unit 12 and the rear-stage deceleration unit 13 disposed in the case 11 to output the output shaft. 14 pinions 14a. The output shaft 14 is disposed so as to mesh with the teeth on the inner periphery of the ring gear 3 at the pinion 14a (see FIG. 2). Then, the yaw driving device 4 is actuated by the driving force from the electric motor 5 to rotate the output shaft 14, so that the yaw driving device 4 moves along the inner periphery of the ring gear 3 and the nacelle with respect to the tower 102. 2 will turn. In the following description, in the yaw drive device 4, the lower output side where the output shaft 14 is arranged is one end side, and the upper input side where the electric motor 5 is arranged is the other end side. To do.

  As shown in FIG. 3, the case 11 of the yaw driving device 4 is composed of a cylindrical first case portion 11a and a second case portion 11b arranged on the other end side of the first case portion 11a. The edges are connected by bolts. The case 11 houses a front speed reduction unit 12, a rear speed reduction unit 13, and the like. The front speed reduction unit 12, the rear speed reduction unit 13, and the output shaft 14 are connected to a rotation center line P (in FIG. 1). They are arranged in series along the axial direction, which is the direction of the dotted line). The case 11 has an opening at one end (the end of the first case 11a), and the electric motor 5 is fixed to the other end (the end of the second case 11b) as described above.

  FIG. 4 is an enlarged cross-sectional view showing the rear-stage deceleration unit 13 and its vicinity in FIG. As shown in FIGS. 3 and 4, a plurality of pin internal teeth (internal teeth in the present embodiment) 22 are provided, and are attached to a pin groove formed on the inner periphery of the first case portion 11a. It is arranged on the inner periphery of the case 11. The pin internal teeth 22 (in FIG. 3 and FIG. 4, the external shape is not shown in cross section) is formed as a pin-shaped member (round bar-shaped member) and arranged so that the longitudinal direction thereof is parallel to the rotation center line P. In addition, they are arranged at equal intervals along the circumferential direction on the inner periphery of the case 11 and are configured to mesh with external teeth 31 of an external gear 28 described later.

  As shown in FIG. 3, the front speed reduction unit 12 is configured as a one-stage planetary gear mechanism to which the rotational driving force from the electric motor 5 is transmitted, and includes a sun gear 15, a carrier 16, a planetary gear 17, an internal gear 18, An input shaft 60 and the like are provided. The input shaft 60 is coupled to the output shaft 5a of the electric motor 5 at the other end side, and a gear is formed on the outer periphery of the one end side. A plurality of (three in this embodiment) planetary gears 17 are arranged around the input shaft 60 and mesh with a gear on one end side of the input shaft 60, and the radial direction (rotation) of the yaw driving device 4 with respect to the input shaft 60. (The direction perpendicular to the center line P). The carrier 16 is formed as a planetary frame that rotatably holds the plurality of planetary gears 17 at positions of equal angles along the circumferential direction around the input shaft 60 and performs a revolving operation. The internal gear 18 is provided as a ring-shaped gear in which teeth are formed on the inner periphery and the planetary gear 17 meshes, and is fixed to the second case portion 11b. As shown in FIGS. 3 and 4, the sun gear 15 is provided as a shaft-shaped gear member and is disposed on the rotation center line P. The sun gear 15 has a gear portion 15 a that meshes with a spur gear 49 described later on one end side, and a spline that is connected to the inner peripheral portion of the carrier 16 on the other end side.

  As shown in FIGS. 3 and 4, the rear speed reduction unit 13 includes a spur gear 49, a crankshaft 23, a base carrier 25, an end carrier 26, a support 27, an external gear 28, a crankshaft bearing (34, 35) and the like. It is prepared for.

  As shown in FIGS. 3 and 4, a plurality (three in this embodiment) of spur gears 49 are arranged around the sun gear 15 so as to mesh with the gear portion 15 a of the sun gear 15. On the other hand, it is located in the radial direction of the yaw driving device 4. The spur gear 49 is formed with a through hole in the central portion, and is fixed to the other end side of the crankshaft 23 by spline coupling in the through hole.

  As shown in FIGS. 3 and 4, a plurality of crankshafts 23 (three in the present embodiment) are arranged at equal angular positions along the circumferential direction around the rotation center line P. It is arranged so that (the direction of the rotation center line Q) is parallel to the rotation center line P. Each of the crankshafts 23 (in FIG. 3 and FIG. 4, the outer shape is not shown in cross section) is disposed so as to penetrate a crank hole 30 formed in an external gear 28 described later, and rotates to external teeth. It is provided as a shaft member that rotates the gear 28 eccentrically. And the crankshaft 23 will perform a revolution operation | movement with rotation of the external gear 28 accompanying self rotation (autorotation). Further, the crankshaft 23 is formed with a first eccentric portion 23a, a second eccentric portion 23b, a first shaft portion 23c, and a second shaft portion 23d, and the first shaft portion 23c and the first eccentric portion are formed from one end side. 23a, the second eccentric portion 23b, and the second shaft portion 23d are provided in series in this order. The first eccentric portion 23a and the second eccentric portion 23b are formed such that a cross section perpendicular to the axial direction is a circular cross section, and each center position is provided to be eccentric with respect to the rotation center line Q of the crankshaft 23. It has been. The first eccentric portion 23 a and the second eccentric portion 23 b are disposed in the crank hole 30 of the external gear 28.

  The crankshaft bearings (34, 35) are configured as roller bearings that rotatably hold one end side and the other end side of the crankshaft 23, respectively. The crankshaft bearing 34 holds a first shaft portion 23 c provided on one end side of the crankshaft 23 so as to be rotatable with respect to the base carrier 25. On the other hand, the crankshaft bearing 35 holds the second shaft portion 23 d provided on the other end side of the crankshaft 23 so as to be rotatable with respect to the end carrier 26. Note that a spur gear 49 is fixed to the second shaft portion 23d at an end portion protruding from the crankshaft bearing 35 to the other end side.

  As shown in FIGS. 3 and 4, the external gear 28 includes a first external gear 28 a and a second external gear 28 b that are accommodated in the case 11 in a state of being arranged in parallel. The first external gear 28a and the second external gear 28b are respectively formed with a crank hole 30 through which the crankshaft 23 passes and a column through hole 48 through which the column 27 passes. The first external gear 28a and the second external gear 28b are arranged so that the positions of the crank hole 30 and the column through hole 48 correspond to each other in the direction parallel to the rotation center line P. The crank hole 30 of the external gear 28 (28a, 28b) is formed as a circular hole, and a plurality of (in the present embodiment, at the same angle position along the circumferential direction of the external gear 28 corresponding to the crankshaft 23). 3) Arranged. The column through holes 48 are formed as holes corresponding to the cross-sectional shape of the column 27, and a plurality (three in this embodiment) are arranged at equal angle positions along the circumferential direction of the external gear 28 corresponding to the columns 27. Has been. Further, the support through holes 48 are alternately formed with the crank holes 30 in the circumferential direction of the external gear 28. In addition, the support | pillar 27 has penetrated the support | pillar through-hole 48 in the loose-fit state.

  In addition, external teeth 31 that mesh with the pin internal teeth 22 are provided on the outer circumferences of the first external gear 28a and the second external gear 28b. In the present embodiment, the number of teeth of the external teeth 31 of the first external gear 28 a and the second external gear 28 b is provided to be one less than the number of teeth of the pin internal teeth 22. For this reason, each time the crankshaft 23 rotates, the meshing between the meshing external teeth 31 and the pin internal teeth 22 is shifted, and the external gears 28 (28a, 28b) are eccentrically rotated. The difference in the number of teeth between the external teeth 31 and the pin internal teeth 22 may be plural.

  In addition, the external gear 28 rotatably holds the crankshaft 23 in the crank hole 30 via the external gear bearings (53, 54). The external tooth bearing 53 holds the first eccentric portion 23a with respect to the first external gear 28a, and the external tooth bearing 54 holds the second eccentric portion 23b with respect to the second external gear 28b. ing. The external tooth bearings (53, 54) are each provided with a plurality of roller members (53a, 54a) configured as needle roller members or cylindrical roller members.

  The base carrier 25 and the end carrier 26 constitute a carrier in this embodiment in which the crankshaft 23 is held via the crankshaft bearings (34, 35) and the output shaft 14 is fixed. The base carrier 25 shown in FIGS. 3 and 4 has an output shaft 14 integrally formed at one end thereof and disposed in the case 11 (the output shaft 14 is integrally formed and fixed to the base carrier 25. Have been). The base carrier 25 has a crank holding hole 50 formed on the other end side thereof, and the crank holding hole 50 holds one end side of each crankshaft 23 rotatably at the first shaft portion 23c via the crankshaft bearing 34. doing. The crank holding hole 50 is formed at a position of an equal angle along the circumferential direction around the rotation center line P. Further, the base carrier 25 is rotatably held on the outer peripheral side with respect to the inner peripheral side of the first case portion 11a via the roller bearing 36. A positioning member 44 provided as a ring-shaped member disposed along the outer periphery of the base carrier 25 is fixed. The roller bearing 36 is positioned with one end side engaged with the positioning member 44 and the other end side engaged with one end side of the first case portion 11a.

  As shown in FIGS. 3 and 4, the end carrier 26 is connected to the base carrier 25 via a support 27 and is provided as a disk-shaped member. The end carrier 26 is rotatably held with respect to the inner peripheral side of the case 11 via a ball bearing 37 on the outer peripheral side thereof. The ball bearing 37 has one end engaged with the other end of the first case 11 a of the case 11, and the other end engaged with the edge 26 a protruding in a flange shape on the other end of the end carrier 26. It is arranged in the state. Further, the end carrier 26 is formed with a crank through-hole 43 in which the second shaft portion 23d on the other end side of the crankshaft 23 is disposed at an equal angle position along the circumferential direction with the rotation center line P as the center. Has been. In the crank through-hole 43, the other end side of the crankshaft 23 is rotatably held by a second shaft portion 23d via a crankshaft bearing 35.

  As shown in FIGS. 3 and 4, the support column 27 is disposed between the base carrier 25 and the end carrier 26 and is provided as a columnar portion that connects the base carrier 25 and the end carrier 26. A plurality (three in this embodiment) of the support columns 27 are arranged at equal angular positions along the circumferential direction around the rotation center line P, and are arranged so that the axial direction thereof is parallel to the rotation center line P. ing. In addition, the support | pillar 27 and the crankshaft 23 are alternately arrange | positioned along the circumferential direction centering on the rotation centerline P. As shown in FIG. Each support column 27 is formed integrally with the base carrier 25 and is provided so as to protrude on the other end side of the base carrier 25. The support column 27 is formed with a support pin hole 51 that opens to the other end side of the end carrier 26 and extends to the support column 27 and into which a round bar (columnar) support pin 40 is press-fitted. As the support pins 40 are press-fitted into the support pin holes 51, the circumferential positions of the base carrier 25 and the end carrier 26 are matched.

  Further, the support column 27 is formed with a support bolt hole 47 that opens to the other end side of the end carrier 26 and extends to the base carrier 25 and into which a support bolt 29 indicated by a broken line in the drawing is inserted. An internal thread portion is formed on the back side of the support bolt hole 47. The column bolt 29 has a screw portion formed as a male screw portion on one end side and a head portion on which the hexagonal hole for tightening is provided on the other end side. The column bolt 29 is configured to couple the end carrier 26 and the base carrier 25 via the column 27 by screwing the screw portion with the female screw portion of the column bolt hole 47. When the base carrier 25 and the end carrier 26 are connected by the coupling with the support bolt 29, the positioning member 44 fixed to the base carrier 25 and the end carrier 26 are rolled by the tightening force generated at that time. The case 11 is clamped via the bearing 36 and the ball bearing 37 (held so as to be clamped). By this clamping, the base carrier 25 and the end carrier 26 are held rotatably with respect to the case 11.

  Next, the operation of the nacelle turning mechanism 1 described above will be described. When the operation of the electric motor 5 is started, the input shaft 60 connected to the output shaft 5a rotates, and the planetary gear 17 meshing with the input shaft 60 rotates and revolves while meshing with the internal gear 18, whereby the carrier 16 rotates, and the sun gear 15 connected to the carrier 16 rotates. When the sun gear 15 rotates, each crankshaft 23 rotates together with each spur gear 49 that meshes with the sun gear 15, and the first and second eccentric portions (23a, 23b) also rotate. With this rotation, a load acts on the external gears 28 (28a, 28b) from the first and second eccentric portions (23a, 23b), and the external gears 28 (28a, 28b) are pin internal teeth 22. And rotate eccentrically so as to swing while shifting the mesh. Then, along with the eccentric rotation of the external gear 28, the crankshaft 23 rotated and held with respect to the external gear 28 by the external tooth bearings (53, 54) rotates around the rotation center line P while rotating. I do. The revolving operation of the crankshaft 23 causes the output shaft 14 to rotate together with the base carrier 25 and the end carrier 26 that are connected by the support column 27 and rotatably hold the crankshaft 23, and a large torque is output from the pinion 14a. Will be. The output of the yaw driving device 4 is controlled by controlling the input rotational speed of the yaw driving device 4 (controlling the rotational speed of the input shaft 60 of the yaw driving device 4) by rotating the electric motor 5 at a predetermined rotational speed. The electric motor 5 controls the rotational speed of the output shaft 14 to be in a range of 0.1 rpm to 1.0 rpm.

  According to the nacelle turning mechanism 1 described above, since the yaw driving device 4 is configured as an eccentric type reduction gear, it is possible to secure a large reduction ratio and improve the output torque and reduce the size. Further, in the yaw drive device 4, power transmission to the carriers (25, 26) is parallel to the rotation center line P, unlike the one via a sliding member such as an inner roller disclosed in Patent Document 2. This is performed via crankshaft bearings (53, 54) that rotatably hold one end side and the other end side of the crankshaft 23 provided in the shaft. For this reason, a decrease in drive efficiency can be suppressed. And since the magnitude | size of the rotational speed of the output shaft 14 is controlled by the electric motor 5 from 0.1 rpm to 1.0 rpm, the driving | running in the lubrication state which avoided the fixed lubrication area | region with a large frictional resistance is attained. Further, the driving efficiency can be improved. Thereby, size reduction of the electric motor 5 can be achieved. Moreover, it can suppress that drive efficiency deteriorates in the fixed lubrication area | region where the magnitude | size of the rotational speed of the output shaft 14 is less than 0.1 rpm. Further, since the magnitude of the rotational speed of the output shaft 14 is 1.0 rpm or less, an increase in energy loss at the time of braking accompanying an increase in the rotational speed can be suppressed, and the effect of improving the driving efficiency can be fully enjoyed. . Therefore, according to this embodiment, in the nacelle turning mechanism 1, it is possible to reduce the size of the equipment in the nacelle 2 and improve the output torque and drive efficiency of the yaw drive device 4. Furthermore, by setting the reduction ratio of the front stage reduction unit 12 to 1/6 to 1/10 and the reduction ratio of the rear stage reduction unit 13 to 1/50 to 1/140, the rotation speed of the crankshaft is set to 5 rpm to 140 rpm, The driving efficiency can be further improved.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made as long as they are described in the claims. For example, the output shaft may not be integrated with the carrier but may be provided as a separate member from the carrier. Moreover, the support | pillar which connects a base carrier and an edge part carrier does not need to be integrally formed in a base carrier, and may be formed as a member different from a carrier. Also, the number of crankshafts and struts may be two or less or four or more. Further, the number of eccentric parts of the crankshaft and the number of external gears need not be two.

  The present invention can be widely applied as a nacelle turning mechanism for turning a nacelle in a tower of a windmill.

It is a mimetic diagram of a nacelle turning mechanism and a windmill concerning one embodiment of the present invention. It is a top view which shows typically a part in nacelle of the nacelle turning mechanism shown in FIG. It is the front view of the electric motor shown in FIG. 1, and sectional drawing of a yaw drive device. FIG. 4 is an enlarged cross-sectional view illustrating a part of the yaw driving device illustrated in FIG. 3.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Nacelle turning mechanism 2 Nacelle 3 Ring gear 4 Yaw drive device 5 Electric motor 11 Case 14 Output shaft 22 Pin internal tooth (internal tooth)
23 Crankshaft 25, 26 Base carrier 28, 28a, 28b External gear 34, 35 Crankshaft bearing

Claims (1)

A nacelle that is rotatably arranged with respect to the tower of the windmill,
A ring gear fixed to the tower of the windmill,
A yaw driving device fixed to the nacelle, an output shaft meshing with the ring gear, and turning the nacelle with respect to a tower of a windmill;
An electric motor that transmits a driving force to the input shaft of the yaw driving device and controls the input rotational speed;
With
The yaw driving device is arranged in parallel with the case, the internal teeth arranged on the inner periphery of the case, the external gear provided with the external teeth meshing with the internal teeth, and the rotation center line of the yaw driving device A crankshaft that rotates the external gear eccentrically, a crankshaft bearing that rotatably supports one end side and the other end side of the crankshaft, and the crankshaft via the crankshaft bearing. Holding the carrier with the output shaft fixed thereto,
The electric motor controls the output of the yaw driving device by controlling the input rotation speed so that the rotation speed of the output shaft is 0.1 rpm or more and 1.0 rpm or less. The nacelle turning mechanism.

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