JP2009275615A - Yaw driving device for wind mill - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a yaw driving device for a wind mill capable of improving an output torque, reducing the size, and increasing strength against the impact force by a gust. <P>SOLUTION: An eccentric type speed reduction gear 13 is provided in a case 11 disposed in a nacelle 102. The eccentric type speed reduction gear 13 has pin internal teeth 22, a crank shaft 23, a base part carrier 25, an end part carrier 26, a support post 27 and an external gear 28. A tooth width B of the external gear 28 is made to be ≥1.0 and ≤1.4 times larger than a diameter A of an eccentric part (23a, 23b) of the crank shaft 23. A pinion 112 meshing with a gear 101a fixed to a tower 101 is attached to an output shaft 14 fixed to the base part carrier 25. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a windmill yaw driving device that is a driving device for turning a nacelle of a windmill according to a wind direction.

  Conventionally, a windmill is used as a wind power generator. As this windmill, what is provided in the upper part of a tower and is equipped with the nacelle by which a blade | wing (blade | blade) is attached and a generator etc. is arrange | positioned inside is often used. And in such a windmill, as disclosed in Patent Document 1, a yaw drive device (windmill yaw drive device) that is a drive device for turning the nacelle of the windmill according to the wind direction is provided. Yes. Patent Document 1 discloses a yaw drive device that includes a pinion that meshes with a ring gear at the top of a tower. The pinion is rotationally driven by a motor, whereby the nacelle turns.

  In the wind turbine described above, since the diameter of the blade tends to increase in recent years, a high-output specification yaw driving device with improved output torque is required. On the other hand, since a part or all of the yaw drive device is arranged in the nacelle, it is necessary to have a configuration that can be arranged avoiding interference with other devices in the nacelle. It is also required that the configuration improves the mountability of the yaw drive device. For this reason, the yaw driving device is required to be downsized.

  On the other hand, as a reduction gear capable of realizing a large reduction ratio necessary for improving the output torque and downsizing, as disclosed in Patent Document 2, the industrial reduction gear is configured as an eccentric reduction gear. Robot joint drive devices are known. In the driving device (joint driving device for an industrial robot) disclosed in Patent Document 2, a crankshaft, an external gear, an internal gear, a base carrier, an end carrier, and the like are provided. The crankshaft is formed as an input shaft provided with an eccentric body, passes through a hole for a crank formed in the external gear, and rotates the external gear engaged with the internal gear eccentrically. The internal gear is provided with a plurality of pin internal teeth formed as pin-shaped members. The end carrier formed as the first output flange and the base carrier formed as the second output flange hold the crankshaft rotatably.

JP 2001-289149 A (page 4, FIG. 1) JP 2004-299000 A (page 7, FIG. 1)

  By using the drive device disclosed in Patent Document 2 as a yaw drive device for a windmill, it is conceivable that the yaw drive device can be reduced in size while improving output torque. On the other hand, in a windmill, when a gust of wind blows, a great impact force acts on the windmill yaw driving device, and the windmill yaw driving device often breaks. In particular, in Japan and Southeast Asia, winds from typhoons converge in the mountains, and wind gusts exceeding the expected level may blow to the windmills. There is a need for a windmill yaw drive device having high impact strength and excellent impact resistance. However, when the driving device disclosed in Patent Document 2 is used as a yaw driving device, the load is not distributed in a balanced manner in the crankshaft, the external gear, and the pin internal teeth when an impact force due to a gust of wind acts. As a result of the inventor's earnest research, it has been found that there is a possibility that the external gear may be damaged and the yaw driving device may be damaged.

  In view of the above circumstances, an object of the present invention is to provide a yaw drive device for a wind turbine that can improve the output torque and reduce the size, and can improve the strength against an impact force caused by a gust of wind.

  A windmill yaw drive device according to a first aspect of the present invention for achieving the above object is formed as a pin-like member disposed at a part of the nacelle of the windmill at least partially and disposed on the inner periphery of the case. A plurality of pin internal teeth, an external gear that is housed in the case and meshes with the pin internal teeth on the outer periphery, and a crank hole formed in the external gear, A crankshaft that rotates and rotates the external gear eccentrically, a base carrier that rotatably holds one end of the crankshaft, and an end carrier that rotatably holds the other end of the crankshaft And a post fixed to the base carrier and connecting the base carrier and the end carrier, and a pinion fixed to the base carrier and meshing with a gear fixed to the tower of the windmill. An output shaft, and a windmill yaw drive device for turning the nacelle of the windmill, wherein the crankshaft has a diameter of an eccentric portion formed so as to have a circular cross section eccentric to a rotation center line thereof. The dimension of the tooth width of the external gear is in the range of 1.0 to 1.4 times the dimension.

  According to the present invention, when the rotational driving force is transmitted to the crankshaft, the external gear rotates eccentrically while meshing with the inner pins of the case along with the rotation of the crankshaft, and is connected via the support column. The output shaft rotates together with the base carrier and the end carrier that rotatably hold the crankshaft. When the output shaft to which the pinion that meshes with the gear fixed to the tower of the windmill rotates, the nacelle in which the case is arranged turns. Therefore, according to the present invention, a large reduction ratio can be ensured by the yaw drive device configured as an eccentric type reduction gear, and output torque can be improved and downsized. In the present invention, the tooth width dimension of the external gear is configured to be in the range of 1.0 to 1.4 times the diameter dimension of the eccentric part of the crankshaft. For this reason, between the crankshaft and the external gear, and between the external gear and the pin internal teeth, the load is distributed in a balanced manner in an even state or in an almost equal state. As a result, when an impact force due to a gust of wind acts, the impact force acts on the crankshaft, the external gear, and the internal teeth of the pin in an equal or nearly equal state, and these components are damaged. This can prevent the yaw driving device from being damaged.

  When an impact force due to a gust of wind acts on the yaw drive device, a load is generated between the external gear, the crankshaft, and the pin internal teeth. However, if the rigidity of one component is strong, the other component Indentation as damage is likely to occur. However, according to the structure of this invention, since the load between an external gear, a crankshaft, and a pin internal tooth acts in an equal state or a state near equality, generation | occurrence | production of an impression can be reduced. Further, as a result of verification by the inventor of the present application, if the tooth width dimension of the external gear is less than 1.0 times the diameter dimension of the eccentric portion of the crankshaft, the surface pressure between the external gear and the pin internal teeth It was confirmed that the possibility of indentation in the external gear rapidly increased. On the other hand, if the tooth width dimension of the external gear exceeds 1.4 times the diameter dimension of the eccentric part of the crankshaft, when the base carrier and the end carrier connected by the column are inclined by impact force, The effect of uneven contact due to the long tooth width of the toothed gear becomes large, the surface pressure between the external gear and the pin internal teeth increases rapidly, and the possibility that indentations will occur in the external gear is rapid. It was confirmed that it was high. For this reason, by setting the tooth width dimension of the external gear to 1.0 to 1.4 times the diameter dimension of the eccentric part of the crankshaft, the external gear, the crankshaft, and the pin internal teeth And the load can be equalized, and the generation of indentations can be reduced.

  Therefore, according to the present invention, it is possible to provide a yaw drive device for a windmill that can improve the output torque and reduce the size and improve the strength against the impact force caused by the gust.

  A windmill yaw drive device according to a second aspect of the present invention is the windmill yaw drive device of the first aspect, wherein the windmill yaw drive device is disposed around the crankshaft disposed on the rotation center line of the yaw drive device, and is connected to the external gear. A guide crankshaft penetrating the formed guide crank hole and transmitting the rotational force of the external gear to the output shaft via the base carrier and the end carrier; and the guide crankshaft as the base carrier and A guide crank bearing rotatably held with respect to the end carrier, and a pitch circle diameter dimension that is a diameter of a circle connecting a center point of a bearing rolling member in the guide crank bearing, The diameter of the eccentric part of the crankshaft is in the range of 0.5 to 0.9 times the diameter.

  According to the present invention, in a yaw drive device including a guide crankshaft that is held by a guide crank bearing and transmits a rotational force to an output shaft through a base carrier and an end carrier, a pitch circle diameter (PCD) of the guide crank bearing is provided. : Pitch Circle Diameter) is configured to be in the range of 0.5 to 0.9 times the diameter of the eccentric part of the crankshaft. For this reason, the guide crank bearing that holds the guide crankshaft rotatably has sufficient strength in relation to the size of the eccentric portion of the crankshaft that causes the rotational force to act on the guide crankshaft via the external gear. It can be configured to a radial dimension. In the eccentric part of the crankshaft, it can be configured to have a diameter dimension having a strength capable of withstanding an impact force equivalent to that of the guide crank bearing. Furthermore, since the strength against impact force can be equalized between the guide crank bearing and the eccentric part of the crankshaft, these components are arranged in the radial direction of the yaw drive device (the direction perpendicular to the rotation center line of the yaw drive device). ), The structure reduced in the radial direction can be realized, and the diameter of the yaw driving device can be reduced.

  When an impact force due to a gust of wind acts on the yaw drive device, a load is generated between the crankshaft and the guide crankshaft via the external gear and the guide crankshaft, but the rigidity of one component is strong. In the other component, the surface pressure is increased and the impact resistance is lowered. However, according to the configuration of the second invention, the load between the eccentric portion of the crankshaft and the guide crank bearing acts in a balanced manner in an equivalent state or in a state close to the equivalent state. The decrease can be suppressed. Further, as a result of verification by the inventor of the present application, when the diameter of the pitch circle diameter of the guide crank bearing is less than 0.5 times the diameter of the eccentric part of the crankshaft, the guide crank bearing is used more than the eccentric part of the crankshaft. When the surface pressure at the bearing suddenly increases, and the size of the pitch circle diameter of the guide crank bearing exceeds 0.9 times the diameter of the eccentric portion of the crankshaft, the crankshaft is more than the guide crank bearing. It has been confirmed that the surface pressure at the eccentric portion of the plate increases rapidly. For this reason, the pitch circle diameter dimension of the guide crank bearing is set to 0.5 to 0.9 times the diameter dimension of the eccentric part of the crankshaft, so that the eccentric part of the crankshaft and the guide The load can be distributed in a balanced manner with the crank bearing, and the impact resistance can be further improved.

  ADVANTAGE OF THE INVENTION According to this invention, while improving the output torque and size reduction, the yaw drive device for windmills which can aim at the intensity | strength improvement with respect to the impact force by a gust of wind can be provided.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. The windmill yaw drive device according to the embodiment of the present invention can be widely applied as a swinging drive device for turning the nacelle of the windmill according to the wind direction.

(Configuration of windmill and nacelle)
FIG. 1 is a schematic diagram for explaining an outline of a wind turbine 100 to which a wind turbine yaw driving device 1 (hereinafter simply referred to as “yaw driving device 1”) according to an embodiment of the present invention is applied. As shown in FIG. 1, the windmill 100 includes a tower 101, a nacelle 102, a blade 103, devices such as a generator 107 arranged in the nacelle 102, and the like. In FIG. 1, the internal structure of the nacelle 102 is schematically shown. The tower 101 is installed so as to extend vertically upward from the ground, and a gear 101a formed as a ring gear having teeth provided on the outer periphery or the inner periphery is fixed to the upper portion of the tower 101. A nacelle 102 is installed on the top of the tower 101.

  The nacelle 102 is installed so as to turn in a substantially horizontal plane with respect to the tower 101 by a yaw driving device 1 to be described later, to which a pinion 112 (see FIGS. 2 and 3) that meshes with the gear 101a on the upper portion of the tower 101 is attached. . A plurality of (three in this embodiment) blades 103 are rotatably attached to the nacelle 102, and these blades 103 are attached to the nacelle 102 so as to extend radially at equal angles. Further, inside the nacelle 102, a power transmission shaft 104, a speed increaser 105, a brake device 106, a generator 107, a transformer 108, the yaw driving device 1, and the like are arranged. The power transmission shaft 104 is connected to the blade 103 via the hub 109, and the power transmission shaft 104 is also rotated when the blade 103 is rotated by wind power. Then, the rotational driving force of the power transmission shaft 104 is increased in speed by the speed increaser 105 and appropriately adjusted by the brake device 106 and input to the generator 107. As a result, power is generated in the generator 107, and the generated power is transmitted to the substation facilities and the like on the ground via the transformer 108 and the cable 110 laid so as to pass through the tower 101 and the ground. Will be.

(Whole structure of windmill yaw drive device)
Next, the yaw driving device 1 according to this embodiment will be described. FIG. 2 is a plan view schematically showing a state in which a part of the nacelle 102 is viewed from above, and is a diagram showing an arrangement of the yaw driving device 1. In FIG. 2, elements other than the yaw driving device 1 and the gear 101a in the nacelle 102 are omitted. FIG. 3 is a cross-sectional view showing the yaw driving device 1.

  As shown in FIGS. 1 to 3, the yaw driving device 1 is arranged in a plurality of locations (four locations in the present embodiment) around the gear 101 a of the tower 101 in the nacelle 102. This yaw driving device 1 is configured to include a case 11, a planetary gear mechanism 12, an eccentric speed reducer 13, an output shaft 14, and the like. In the case 11, a bolt 113 (shown by a broken line in FIG. 3) is provided to the nacelle 102. Attached through. The yaw driving device 1 has a pinion 112 attached to the output shaft 14 positioned so as to protrude from the case 11 on one end side disposed on the lower side, and is attached to the case 11 on the other end side disposed on the upper side. On the other hand, a motor 111 is attached.

  In FIG. 3, the rotation center line P of the yaw driving device 1 (that is, the rotation center line of the motor 111 and the output shaft 14) is indicated by a one-dot chain line, and is represented on the left side with respect to the rotation center line P. Cross sections at different angles in the circumferential direction (circumferential direction around the rotation center line P) are illustrated for the cross section and the cross section shown on the right side. Similarly, in FIGS. 4 to 6 described later, cross sections having different angles in the circumferential direction on the left side and the right side with respect to the rotation center line P are illustrated. Further, in the following description, in the yaw driving device 1, the output side that is the lower side where the output shaft 14 is disposed is one end side, and the input side that is the upper side where the motor 111 is disposed is the other end side. To do.

  As shown in FIGS. 1 to 3, in the yaw drive device 1, rotation input from the motor 111 disposed on the upper side is transmitted via the planetary gear mechanism 12 and the eccentric speed reducer 13 disposed in the case 11. The motor is decelerated and transmitted to output to the pinion 112 attached to the output shaft 14. The pinion 112 is fixed to the output shaft 14 through spline coupling, and is further disposed so as to mesh with a gear 101 a fixed to the upper portion of the tower 101. Then, the yaw driving device 1 attached to the nacelle 102 in the case 11 operates and the pinion 112 rotates, so that the yaw driving device 1 moves along the periphery of the gear 101 a and the nacelle 102 is located above the tower 101. Will turn against.

  Further, the case 11 of the yaw driving device 1 is disposed in the nacelle 102 (see FIGS. 1 and 2), a cylindrical first case portion 11a, and a plurality of (in the present embodiment, three) rings. It is comprised with the 2nd case part 11b comprised by connecting a serial member in series, and these edge parts are connected with the volt | bolt (refer FIG. 3). The case 11 houses a planetary gear mechanism 12, an eccentric speed reducer 13, and the like. The planetary gear mechanism 12 is disposed inside the second case portion 11b, and the eccentric speed reducer 13 is disposed inside the first case portion 11a. The planetary gear mechanism 12, the eccentric speed reducer 13, and the output The shaft 14 is arranged in series along the axial direction which is the direction of the rotation center line P of the yaw driving device 1. Further, the case 11 has an opening at one end (the end of the first case 11a), and the motor 111 is fixed to the other end (the end of the second case 11b) as described above. Yes.

(Configuration of planetary gear mechanism)
4 is an enlarged cross-sectional view of the planetary gear mechanism 12 and its vicinity in FIG. As shown in FIGS. 3 and 4, the planetary gear mechanism 12 is provided as a two-stage planetary gear mechanism to which the rotational driving force from the motor 111 is transmitted, and includes a spline 15, a first carrier 16, and a first planetary gear 17. , Ring gear 18, sun gear 19, second carrier 20, second planetary gear 21 and the like.

  As shown well in FIG. 4, a plurality of (four in this embodiment) second planetary gears 21 are arranged around the rotation shaft 111 a of the motor 111 arranged so as to protrude toward the inside of the case 11. Thus, the yaw driving device 1 is positioned in the radial direction (a direction perpendicular to the rotation center line P) with respect to the rotation shaft 111a. Each second planetary gear 21 is connected to the rotation shaft 111a by meshing with a gear formed on the outer periphery of the end of the rotation shaft 111a. The second carrier 20 is formed as a planetary frame that rotatably holds the plurality of second planetary gears 21 at positions of equal angles along the circumferential direction around the rotation shaft 111a and performs a revolving operation. The sun gear 19 is disposed on the rotation center line P, meshes with the first planetary gear 17 at one end thereof, and is connected to the inner peripheral portion of the second carrier 20 by spline coupling at the other end.

  The ring gear 18 is provided as a gear integrally formed on an inner peripheral portion of an intermediate member of the three ring-shaped members of the second case portion 11b, and is provided on the second planetary gear 21 and the first planetary gear 17. It is comprised so that it may mesh. A plurality of (four in this embodiment) first planetary gears 17 are arranged around the sun gear 19 so as to mesh with the sun gear 19, and are positioned in the radial direction of the yaw drive device 1 with respect to the sun gear 19. . The first carrier 16 is formed as a planetary frame that rotatably holds the plurality of first planetary gears 17 at positions of equal angles along the circumferential direction around the sun gear 19 and performs a revolving operation. The spline 15 is disposed on the rotation center line P, and is connected to a crankshaft 23 of an eccentric type reduction gear 13 described later on one end side thereof by spline coupling, and to the inner peripheral portion of the first carrier 16 on the other end side. They are connected by spline connection. The spline 15 is configured to rotate the crankshaft 23 by being fixed to the crankshaft 23, and is arranged on the same axis with the rotation center line coincident with the crankshaft 23 (that is, the spline). 15 and the crank 23 are also arranged on the rotation center line P).

(Configuration of eccentric type reducer)
As shown in FIG. 3, the eccentric speed reducer 13 is a speed reducer that is operated by a rotational driving force that is input from the motor 111 and transmitted through the planetary gear mechanism 12 to transmit rotation to the output shaft 14. Is provided. FIG. 5 is an enlarged cross-sectional view showing the eccentric speed reducer 13 and its vicinity in FIG. As shown in FIGS. 3 and 5, the eccentric speed reducer 13 includes a pin inner tooth 22, a crankshaft 23, a guide crankshaft 24, a base carrier 25, an end carrier 26, a support 27, an external gear 28, and a support bolt. 29 etc. are comprised. The eccentric speed reducer 13 is configured as a center crank type eccentric speed reducer in which a crankshaft 23 is disposed on a rotation center line P that is the center in the radial direction.

  As shown in FIGS. 3 and 5, the pin internal teeth 22 are formed as pin-shaped members (round bar-shaped members), and a plurality of pin internal teeth 22 are arranged along the inner periphery of the case 11. In FIGS. 3 and 5, the pin inner teeth 22 are shown not in cross section but in outer shape. The pin internal teeth 22 are arranged so that the longitudinal direction thereof is parallel to the rotation center line P, and are arranged in a state of being fitted into the case 11 at equal intervals on the inner periphery of the case 11, which will be described later. It is configured to mesh with the external teeth 31 of the external gear 28.

  As shown in FIGS. 3 and 5, the crankshaft 23 is arranged such that the rotation center line thereof coincides with the rotation center line P of the yaw driving device 1 (that is, arranged so that the axial directions thereof coincide). The spline 15 is arranged so as to coincide with the rotation center line. And this crankshaft 23 is arrange | positioned so that the hole 30 for cranks formed in the external gear 28 may be penetrated, and it is provided as a shaft member which rotates the external gear 28 eccentrically by rotating. Yes. 3 and 5, the crankshaft 23 is not a cross section, except for a part on the other end side.

  The crankshaft 23 includes 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 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 the center positions of the first eccentric portion 23a and the second eccentric portion 23b are the rotation center lines of the crankshaft 23 (first shaft portion). 23c and the center position of the second shaft portion 23d). That is, the first and second eccentric portions (23a, 23b) constitute the eccentric portion of the present embodiment formed to have a circular cross section that is eccentric with respect to the rotation center line of the crankshaft 23.

  A first shaft portion 23c disposed on one end side of the crankshaft 23 is rotatably held via a roller bearing 34 with respect to a base carrier 25 described later, and a second shaft disposed on the other end side. The portion 23d is rotatably held via a roller bearing 35 with respect to an end carrier 26 described later. A fitting hole into which one end side of the spline 15 of the planetary gear mechanism 12 is fitted is formed in the second shaft portion 23d on the other end side of the crankshaft 23 so as to open toward the other end side. The crankshaft 23 is fixed to the spline 15 by spline coupling at the inner peripheral portion.

  As shown in FIGS. 3 and 5, a plurality of guide crankshafts 24 (four in the present embodiment) are arranged at equal angular positions around the crankshaft 23 along the circumferential direction around the crankshaft 23. It is arranged so that its axial direction is parallel to the rotation center line P. Each guide crankshaft 24 is disposed so as to penetrate a guide crank hole 39 formed in the external gear 28. The guide crankshaft 24 performs a revolving operation while rotating (spinning) with the rotation of the external gear 28 accompanying the rotation of the crankshaft 23, and the rotational force of the external gear 28 is used as the base carrier 25 and the end carrier 26. It is provided as a shaft member that transmits to the output shaft 14 via the.

  Each guide crankshaft 24 includes a first eccentric portion 24a, a second eccentric portion 24b, a first shaft portion 24c, and a second shaft portion 24d, and the first shaft portion 24c and the first eccentric portion 24d are provided. The part 24a, the second eccentric part 24b, and the second shaft part 24d are provided in series in this order. The first eccentric portion 24a and the second eccentric portion 24b are formed such that a cross section perpendicular to the axial direction is a circular cross section, and the center positions of the first eccentric portion 24a and the second eccentric portion 24b are the rotation center lines of the guide crankshaft 24 (first shaft). Center portion of the portion 24c and the second shaft portion 24d). The first eccentric portion 24a and the second eccentric portion 24b are arranged so as to be eccentric at positions corresponding to the first eccentric portion 23a and the second eccentric portion 23b of the crankshaft 23, respectively.

  Further, the first shaft portion 24c disposed on one end side of the guide crankshaft 24 is rotatably held with respect to the base carrier 25 via a guide crank bearing 41 formed as a roller bearing. On the other hand, the second shaft portion 24d disposed on the other end side of the guide crankshaft 24 is rotatably held with respect to the end carrier 26 via a guide crank bearing 42 formed as a roller bearing. . As described above, the guide crankshaft 24 is rotatably held with respect to the base carrier 25 and the end carrier 26 by the guide crank bearings (41, 42).

  As shown in FIGS. 3 and 5, the base carrier 25 is formed integrally with the output shaft 14 on one end side and is disposed in the case 11. The base carrier 25 holds one end side of the crankshaft 23 at its first shaft portion 23c via a roller bearing 34 in a central portion on the other end side so as to be rotatable. In addition, at the other end side, one end side of the support column 27 is press-fitted into the base carrier 25, and a support column holding hole 33 for holding the support column 27 and the first shaft portion 24 c of the guide crankshaft 24 are connected to the guide crank bearing 41. A guide crank holding hole 49 is formed. The support column holding hole 33 and the guide crank holding hole 49 are formed at equal angular positions along the circumferential direction around the rotation center line P, and the support column holding hole 33 and the guide crank holding hole 49 are alternately arranged in the circumferential direction. Has been placed. The base carrier 25 holds the one end side of each guide crankshaft 24 through the guide crank bearing 41 via the guide crank bearing 41 by the guide crank holding hole 49.

  Further, the base carrier 25 is rotatably held with respect to the inner peripheral side of the first case portion 11a in the case 11 via the roller bearing 36 on the outer peripheral side thereof. The roller bearing 36 is provided as a ring-shaped member disposed along the outer periphery of the base carrier 25 and is positioned with respect to the base carrier 25 by a positioning member 44 fixed to the base carrier 25. And the roller bearing 36 is arrange | positioned in the state which the one end side engaged with the positioning member 44, and the other end side engaged with the one end side of the 1st case part 11a. In the present embodiment, the output shaft 14 that rotates together with the base carrier 25 is fixed to the base carrier 25 by being integrally formed with the base carrier 25.

  As shown in FIGS. 3 and 5, the end carrier 26 is connected to the base carrier 25 via a support column 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 in the case 11, and the other end engaged with an edge protruding in a flange shape on the other end of the end carrier 26. Arranged in a state. The end carrier 26 is formed with a central through-hole 43 in which the second shaft portion 23d on the other end side of the crankshaft 23 is disposed at the center thereof. The other end side is rotatably held by the second shaft portion 23d via a roller bearing 35. Further, the end carrier 26 has a guide crank through hole 50 in which the second shaft portion 24d on the other end side of the guide crankshaft 24 is disposed, and a column hole in which the other end side of the column 27 is engaged in a penetrating state. 32 are alternately arranged around the center through-hole 43 at equal angular positions along the circumferential direction around the rotation center line P. In addition, the end carrier 26 holds the other end side of each guide crankshaft 24 by the second shaft portion 24d via the guide crank bearing 42 through the guide crank through hole 50.

  As shown in FIGS. 3 and 5, the column 27 is provided as a cylindrical member that connects the base carrier 25 and the end carrier 26, and a through hole that penetrates the center is a column bolt through which a column bolt 29 is inserted. It is formed as a hole 47. A plurality of (four in the present embodiment) support columns 27 are arranged at equal angular positions around the crankshaft 23 along the circumferential direction around the crankshaft 23, and the axial direction is the rotation center line. It is arranged so as to be parallel to P. In addition, the support | pillar 27 and the guide crankshaft 24 are alternately arrange | positioned along the circumferential direction centering on the crankshaft 23. FIG. Further, each column 27 is arranged such that an end portion on one end side thereof is press-fitted into a column holding hole 33 formed in the base carrier 25. Each column 27 is provided with an outer peripheral portion 45 formed as a cylindrical peripheral side surface extending from the end portion on one end side toward the end carrier 26 from the other end side, and on the end portion on the other end side. A large-diameter portion 46 formed as a portion whose diameter is larger than that of the outer peripheral portion 45 and is enlarged is formed.

  As shown in FIGS. 3 and 5, the column bolt 29 has a screw portion 29 a formed as a male screw portion on one end side and a head portion provided with a hexagon hole for tightening with a hexagon wrench or the like on the other end. On the side. The base carrier 25 and the end carrier 26 are connected by the support bolt 29 and the support 27. When connecting the base carrier 25 and the end carrier 26, first, the support column 27 is inserted into the support hole 32 from one end side. The support hole 32 is formed with step portions corresponding to the outer periphery 45 and the outer diameter 46 of the support 27, and the outer periphery 45 is inserted into the support hole 32, and the large diameter part 46 is connected to the support hole 32. Engage with the stepped portion of the hole 32. In this state, an external gear 28 described later is appropriately disposed, and one end side of the support 27 is press-fitted into the support holding hole 33 of the base carrier 25.

  In the above state, the support bolt 29 is inserted into the support bolt hole 47 of the support 27. Further, a screw hole portion as a female screw portion is further formed in the center portion of the column holding hole 33 of the base carrier 25, and the screw portion 29a on one end side of the column bolt 29 is screwed into this screw hole portion. The head of the support bolt 29 is engaged with a stepped portion formed on the other end side of the support bolt hole 47. The column 27 is fixed to the base carrier 25 at the end on one end side by the tightening force by the column bolt 29 at this time, and the large-diameter portion 46 at the end on the other end side is used as a step portion of the column hole 32. The base carrier 25 and the end carrier 26 are connected to each other by applying a tightening force to the end carrier 26 by being engaged. The positioning member 44 fixed to the base carrier 25 and the end carrier 26 are connected to the case 11 via the roller bearing 36 and the ball bearing 37 by the above-described tightening force for connecting the base carrier 25 and the end carrier 26. Thus, the base carrier 25 and the end carrier 26 are rotatably held with respect to the case 11.

  As shown in FIGS. 3 and 5, 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 overlapped in parallel. . The first external gear 28a and the second external gear 28b are respectively provided with a crank hole 30 through which the crankshaft 23 penetrates, a guide crank hole 39 through which the guide crankshaft 24 penetrates, and a pillar penetration through which the pillar 27 penetrates. A hole 48 is formed. The first external gear 28a and the second external gear 28b are arranged so that the positions of the crank hole 30, the guide crank hole 39, and the column through hole 48 correspond to each other in the direction parallel to the rotation center line P. Has been.

  The crank hole 30 of the external gear 28 is formed as a circular hole, and is disposed at the center of the external gear 28 corresponding to the crankshaft 23. The crank hole 30 holds the first eccentric portion 23a in the first external gear 28a and the second eccentric portion 23b in the second external gear 28b via the needle bearing 38, respectively. The guide crank holes 39 are formed as circular holes, and a plurality (four in this embodiment) of the guide crank holes 39 are arranged at equal angular positions along the circumferential direction of the external gear 28 corresponding to the guide crankshaft 24. The guide crank hole 39 holds the first eccentric portion 24a in the first external gear 28a and the second eccentric portion 24b in the second external gear 28b via the needle bearing 40, respectively. The column through-holes 48 are formed as circular holes, and a plurality (four in this embodiment) are arranged at equal angular positions along the circumferential direction of the external gear 28 corresponding to the columns 27. The support through holes 48 are alternately formed in the circumferential direction of the guide crank holes 39 and the external gear 28. In addition, the support | pillar 27 has penetrated the support | pillar through-hole 48 in the loose-fit state.

  Since the external gear 28, the crankshaft 23, and the guide crankshaft 24 are arranged as described above, when the rotational driving force is transmitted from the spline 15 and the crankshaft 23 is rotated, the rotation of the crankshaft 23 is performed. Accordingly, a load acts on the external gear 28 from the first eccentric portion 23a and the second eccentric portion 23b. Due to this load, the external gear 28 (the first external gear 28 a and the second external gear 28 b) swings and rotates, and the guide crankshaft 24 rotates in response to the swing rotation of the external gear 28. The revolving operation will be performed. The phases of the eccentric portions (23a, 23b, 24a, 24b) of the crankshaft 23 and the guide crankshaft 24 are appropriately adjusted so that the revolution operation of the guide crankshaft 24 is performed around the rotation center line P. Yes.

  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. The number of teeth of the external teeth 31 of the external gear 28 (the first external gear 28a and the second external gear 28b) is provided to be one or several less than the number of teeth of the pin internal teeth 22. Yes. Therefore, every 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 (the first external gear 28a and the second external gear 28b) are decentered and oscillated. It is configured to rotate dynamically.

  Here, the relationship among the crankshaft 23, the guide crankshaft 24, and the external gear 28 will be described in more detail. FIG. 6 is an enlarged cross-sectional view similar to FIG. 5 showing the eccentric type reduction gear 13 and the vicinity thereof. In FIG. 6, the dimension A of the diameter of the first and second eccentric parts (23a, 23b) of the crankshaft 23, the dimension B of the tooth width of the first and second external gears (28a, 28b), the guide crank bearing. A dimension C of a pitch circle diameter (PCD) of (41, 42) is indicated by a broken line with double-ended arrows. Here, the tooth width dimension B of the first and second external gears (28a, 28b) is in the direction of the tooth trace of the external teeth 31 extending in parallel with the pin internal teeth 22 arranged in parallel with the rotation center line P. The length dimension. Further, the dimension C of the pitch circle diameter of the guide crank bearings (41, 42) is the dimension of the diameter of a circle connecting the center point of the bearing rolling member 41a in the guide crank bearing 41 and the guide crank bearing 42. It means the dimension of the diameter of a circle connecting the center points of the bearing rolling members 42a. The bearing rolling member 41a and the bearing rolling member 42a are formed as tapered roller members. The center point of each bearing rolling member (41a, 42a) is the bearing rolling in the direction parallel to the axial direction of the guide crank bearing (41, 42) (that is, the axial direction of the guide crankshaft 24). Each bearing rolling member (in the center of the members (41a, 42a) and in the radial direction of the guide crank bearings (41, 42) (that is, the radial direction around the rotation center line of the guide crankshaft 24) 41a, 42a) is a point located at the center.

  As shown in FIG. 6, in the yaw drive device 1, the first and second external gears (28 a, 28 a, 28) with respect to the dimension A of the diameter of the first and second eccentric parts (23 a, 23 b) of the crankshaft 23. The tooth width dimension B of 28b) is set to a dimension in the range of 1.0 to 1.4 times. In the present embodiment, the case where the value of B / A, which is the dimensional ratio, is set to 1.27 is illustrated. In the yaw driving device 1, the pitch circle diameter dimension C of the guide crank bearings (41, 42) is larger than the diameter dimension A of the first and second eccentric portions (23a, 23b) of the crankshaft 23. Thus, the dimension is set in the range of 0.5 times or more and 0.9 times or less. In the present embodiment, the case where the value of C / A, which is the dimensional ratio, is set to be 0.63 is illustrated.

(Operation of yaw drive device for windmill)
Next, the operation of the above-described yaw driving device 1 will be described. In the wind turbine 100, the yaw driving device 1 causes the control device (not shown) to issue a turning command for turning the nacelle 102 in accordance with the wind direction based on the detection result of an anemometer (not shown), for example. Operates by driving. When the operation of the motor 111 is started based on the turning command, the rotating shaft 111a of the motor 111 rotates. When the rotating shaft 111a rotates, the second planetary gear 21 connected thereto rotates and revolves while meshing with the ring gear 18, whereby the second carrier 20 rotates and the sun connected to the second carrier 20 rotates. The gear 19 rotates. When the sun gear 19 rotates, the first planetary gear 17 meshing with the sun gear 19 rotates and revolves while meshing with the ring gear 18. As a result, the first carrier 16 rotates and the spline 15 connected to the first carrier 16 rotates.

  When the spline 15 rotates, the crankshaft 23 to which the spline 15 is fixed at the other end is rotated, and the first eccentric portion 23a and the second eccentric portion 23b rotate together with the crankshaft 23. With this rotation, as described above, the first external gear 28 a and the second external gear 28 b rotate eccentrically while shifting the mesh with the pin internal teeth 22. As the first external gear 28a and the second external gear 28b rotate eccentrically, the guide crankshaft 24 held rotatably on the external gear 28 by the needle bearing 40 also revolves around the rotation center line P. Perform the action. As a result, the output shaft 14 rotates together with the base carrier 25 and the end carrier 26 that are connected by the support column 27 and the support column bolt 29 and rotatably hold the crankshaft 23 and the guide crankshaft 24, and a large torque is generated from the pinion 112. Will be output. Then, the pinion 112 rotates while meshing with the gear 101a fixed to the tower 101, whereby the turning operation of the nacelle 102 to which the yaw driving device 1 is attached is performed.

(Effects of windmill yaw drive)
According to the yaw drive device 1 described above, the yaw drive device 1 configured as an eccentric speed reducer can ensure a large reduction ratio, and can improve the output torque and reduce the size. In this yaw driving device 1, the tooth width dimension B of the external gear 28 is in the range of 1.0 to 1.4 times the diameter dimension of the eccentric portion (23a, 23b) of the crankshaft 23. It is comprised so that. For this reason, the load is distributed in a balanced manner between the crankshaft 23 and the external gear 28 and between the external gear 28 and the pin internal teeth 22 in an even state or near equal state. As a result, when an impact force due to a gust of wind acts, the impact force acts on the crankshaft 23, the external gear 28, and the pin internal teeth 22 in an equal or nearly equal state. 22, 23, 28) can be prevented from being damaged and causing the yaw driving device 1 to be damaged. Furthermore, the generation of indentations between the needle bearing 38 and the crankshaft 23 or the external gear 28 can be reduced. Further, even when an impact force due to a gust of wind is not acting, the load acting on the needle bearing 38, the crankshaft 23, the external gear 28 and the pin internal teeth 22 can be reduced, and the service life thereof can be extended.

  When an impact force due to a gust of wind acts on the yaw driving device 1, loads are generated between the external gear 28, the crankshaft 23, and the pin inner teeth 22, but if one component is strong, the other Indentation as damage is likely to occur in the components. However, according to the yaw drive device 1, the load between the external gear 28, the crankshaft 23, and the pin internal teeth 22 acts in an equal state or in an almost equal state, so that the generation of indentations can be reduced. Can do. Further, since the tooth width dimension B of the external gear 28 is 1.0 or more times the diameter dimension A of the eccentric portion (23a, 23b) of the crankshaft 23, the external gear 28 and the pin internal teeth 22 are provided. It is possible to suppress an increase in surface pressure between the external gear and the surface of the external tooth 31 in the external gear 28, and to suppress the occurrence of indentations. Further, since the tooth width dimension B of the external gear 28 is 1.4 times or less than the diameter dimension A of the eccentric portion (23a, 23b) of the crankshaft 23, the base carrier 25 connected by the support column 27. When the end carrier 26 is tilted by the impact force, the effect of uneven contact due to the long tooth width of the external gear 28 is increased, and the surface pressure between the external gear 28 and the pin internal teeth 22 is high. It is possible to suppress the occurrence of indentation on the surface of the external tooth 31 of the external gear 28. As described above, in the yaw driving device 1, it is possible to equalize the load between the external gear 28, the crankshaft 23, and the pin internal teeth 22, and to reduce the generation of indentations.

  Therefore, according to the present embodiment, it is possible to provide the windmill yaw driving device 1 that can improve the output torque and reduce the size and improve the strength against the impact force caused by the gust.

  Further, according to the yaw driving device 1, the pitch circle diameter dimension C of the guide crank bearings (41, 42) is 0.5 times or more than the diameter dimension A of the eccentric part (23a, 23b) of the crankshaft 23. The range is 0.9 times or less. Therefore, a guide that rotatably holds the guide crankshaft 24 in relation to the size of the eccentric portion (23a, 23b) of the crankshaft 23 that causes the rotational force to act on the guide crankshaft 24 via the external gear 28. The crank bearings (41, 42) can be configured to have a sufficient diameter. The eccentric portions (23a, 23b) of the crankshaft 23 can also be configured to have a diameter having a strength capable of withstanding an impact force equivalent to that of the guide crank bearings (41, 42). Furthermore, since the strength against impact force can be equalized between the guide crank bearings (41, 42) and the eccentric portions (23a, 32b) of the crankshaft 23, these components are enlarged in the radial direction of the yaw drive device 1. Therefore, a structure that is reduced in the radial direction can be realized, and the diameter of the yaw driving device 1 can be reduced.

  When an impact force due to a gust of wind acts on the yaw driving device 1, a load is generated between the crankshaft 23 and the guide crank bearings (41, 42) via the external gear 28 and the guide crankshaft 24. If the rigidity of one component is strong, the surface pressure is increased in the other component and the impact resistance is lowered. However, according to the yaw driving device 1, the load between the eccentric parts (23a, 23b) of the crankshaft 23 and the guide crank bearings (41, 42) is distributed in a well-balanced state in an equivalent state or a state close to the equivalent state. Therefore, it is possible to suppress a decrease in impact resistance. In addition, since the pitch circle diameter dimension C of the guide crank bearings (41, 42) is 0.5 or more times the diameter dimension A of the eccentric part (23a, 32b) of the crankshaft 23, the crankshaft It can suppress that the surface pressure in the bearing (41, 42) for guide cranks becomes higher than the eccentric part (23a, 23b) of 23. Further, since the dimension C of the pitch circle diameter of the guide crank bearings (41, 42) is 0.9 times or less than the diameter A of the eccentric part (23a, 32b) of the crankshaft 23, the guide crank It can also be suppressed that the surface pressure at the eccentric portions (23a, 23b) of the crankshaft 23 becomes higher than the bearings (41, 42). As described above, in the yaw drive device 1, the load can be distributed in a balanced manner between the eccentric portions (23a, 23b) of the crankshaft 23 and the guide crank bearings (41, 42), thereby further improving the shock resistance. Can be improved.

(Modification)
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 following modifications can be implemented.

(1) In the present embodiment, the center crank type yaw driving device in which the crankshaft is disposed on the rotation center line of the yaw driving device has been described as an example, but this need not be the case. That is, a plurality of crankshafts are arranged along the circumferential direction centered on the rotation center line, and the tooth width of the external gear is 1. with respect to the diameter of the eccentric part of the crankshaft. The yaw driving device may be configured to have a size in the range of 0 times to 1.4 times.

(2) In the present embodiment, the yaw driving device fixed by the output shaft being provided integrally with the base carrier has been described as an example. However, this need not be the case, and the output shaft may be the base carrier. And a yaw drive device provided as a separate member and fixed to the base carrier.

(3) In the present embodiment, the yaw driving device in which the support column is provided and fixed as a separate member with respect to the base carrier has been described as an example. It may be a yaw driving device that is fixed by being integrally formed.

(4) In the present embodiment, the external gear on which two components are stacked has been described as an example. However, this need not be the case, and the external gear may be a stack of three or more components. May be. In this case, the crankshaft and the guide crankshaft can be implemented by providing an eccentric portion corresponding to the number of components of the external gear.

(5) In the present embodiment, the yaw driving device in which four guide crankshafts and four columns are provided has been described as an example, but this need not be the case, and three or five or more guide crankshafts and columns are provided. It may be a yaw drive device.

  The present invention can be widely applied as a yaw driving device for a windmill that is a driving device for turning a nacelle of a windmill according to the wind direction.

It is a schematic diagram for demonstrating the outline of the windmill to which the yaw drive device for windmills which concerns on one embodiment of this invention is applied. It is a top view which shows typically the state which looked at the part in the nacelle of the windmill shown in FIG. 1 from upper direction. It is sectional drawing of the yaw drive device for windmills shown in FIG. It is sectional drawing which expands and shows the planetary gear mechanism and its vicinity in the yaw drive device for windmills shown in FIG. It is sectional drawing which expands and shows the eccentric type reduction gear in the yaw drive device for windmills shown in FIG. 3, and its vicinity. It is sectional drawing which shows the same cross section as FIG. 5, Comprising: It is a figure explaining the relationship between a crankshaft, a guide crankshaft, and an external gear.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Windmill yaw drive 11 Case 14 Output shaft 22 Pin internal tooth 23 Crankshaft 23a, 23b Crankshaft eccentric part 25 Base carrier 26 End carrier 27 Strut 28 External gear 30 Crank hole 31 External tooth 100 Windmill 101 Tower 101a gear 102 nacelle 112 pinion

Claims (2)

A case in which at least a part is arranged in the nacelle of the windmill,
A plurality of pin internal teeth disposed on the inner periphery of the case and formed as a pin-shaped member;
An external gear that is housed in the case and has external teeth that engage with the pin internal teeth on the outer periphery; and
A crankshaft that passes through a hole for a crank formed in the external gear and rotates the external gear eccentrically by rotating;
A base carrier for rotatably holding one end side of the crankshaft;
An end carrier for rotatably holding the other end of the crankshaft;
A post fixed to the base carrier and connecting the base carrier and the end carrier;
An output shaft to which a pinion fixed to the base carrier and engaged with a gear fixed to a wind turbine tower is attached;
A windmill yaw drive device for turning the nacelle of the windmill,
With respect to the dimension of the diameter of the eccentric portion formed so as to have a circular cross section that is eccentric with respect to the rotation center line in the crankshaft, the dimension of the tooth width of the external gear is 1.0 or more and 1 A yaw driving device for a windmill characterized by having a size in a range of 4 times or less. It is a yaw drive device for windmills of Claim 1, Comprising:
It is arranged around the crankshaft arranged on the rotation center line of the yaw driving device, passes through a guide crank hole formed in the external gear, and the rotational force of the external gear is transferred to the base carrier and A guide crankshaft that transmits to the output shaft via the end carrier;
A guide crank bearing for rotatably holding the guide crankshaft with respect to the base carrier and the end carrier;
Further comprising
In the guide crank bearing, the pitch circle diameter, which is the diameter of a circle connecting the center points of the bearing rolling members, is 0.5 times 0.9 times the diameter of the eccentric portion of the crankshaft. A yaw drive device for wind turbines, characterized in that the dimensions are in the range of twice or less.

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