JP5727331B2 - Yaw reduction device and yaw drive system used for yaw drive system of wind power generation equipment - Google Patents

Description

  The present invention relates to a yaw reduction device and a yaw drive system used in a yaw drive system of a wind power generation facility.

  Patent Document 1 discloses a yaw drive system for turning a nacelle of a wind power generation facility in a horizontal plane.

  In the yaw drive system according to Patent Document 1, one swivel gear is provided on the main body (cylindrical column) side of the wind power generation facility, and a plurality of electric motors including a brake mechanism and a yaw reduction device are provided on the nacelle side (in the disclosed example). 2) It is installed. The output pinion of each yaw reduction gear is simultaneously meshed with the swivel gear so that the nacelle (with the electric motor installed) swivels by the reaction received from the swivel gear side when the output pinion meshes with the swivel gear. It has become.

  By turning the entire nacelle with respect to the cylindrical column, the direction of the tip of the nacelle can be directed to a desired direction (for example, the windward direction), and the wind pressure can be efficiently received. In addition, by adopting a configuration in which each pinion of a plurality of yaw reduction gears is simultaneously meshed with the swivel gear, the size of each yaw reduction gear can be kept small, and the inside of a narrow nacelle at a high position from the ground It is possible to improve handling and the like when installing with.

Japanese Patent Laying-Open No. 2005-300891 (paragraphs [0020], [0021], FIG. 1 and FIG. 2)

  However, since wind power generation equipment is equipment installed in a natural environment, it sometimes receives turbulent winds and gusts. When a force to rotate the nacelle is exerted by such strong wind, a “power reverse flow phenomenon” occurs in which the wind load torque is input into the yaw reduction device from the turning gear side.

  Normally, when such a strong wind blows, each rotating element of the yaw drive system is brought into a state in which the rotation is stopped by the braking mechanism to prevent the nacelle from turning abnormally in an uncontrolled state. For this reason, the wind load torque input from the swivel gear side is applied to each element in the yaw reduction device in the stopped state, and the yaw reduction device is placed in a very severe state. As a result, there has been a problem that damage may occur in extreme cases.

  Increasing the overall size of the yaw reduction device in order to deal with this problem is a great demerit as a device installed in a narrow nacelle. In addition, the merit of reducing the size by dividing it into a plurality of yaw reduction devices is reduced. Above all, because it is a natural opponent's equipment, there is no clear indicator itself that it will not be destroyed to what extent, so there is a limit to expanding the size of the yaw reduction device in the dark clouds.

  The present invention has been made in order to solve such a conventional problem, and pays attention to a newly found intermediate problem (described later). By overcoming this intermediate problem, the yaw reduction device is consequently obtained. The original problem is to provide a yaw drive system and a yaw reduction device for wind power generation equipment that are less likely to be damaged without being unnecessarily large.

  The present invention is the yaw reduction device used in a yaw drive system of a wind power generation facility that meshes output pinions of a plurality of yaw reduction devices with a gear on the main body side of the wind power generation facility to drive the nacelle to turn, A hollow shaft incorporated in the power transmission system, inserted into the hollow shaft, connected to the hollow shaft on the inner periphery of the hollow shaft, and connected to other members at a position protruding from the hollow shaft. The shaft member is connected to the hollow shaft at a position opposite to the side where the shaft member protrudes from the hollow shaft with respect to the axial center of the hollow shaft. This solves the above problem.

  In addition, the present invention provides a wind power generation facility in which the output pinion of a plurality of yaw speed reduction devices including at least a first yaw speed reduction device and a second yaw speed reduction device is meshed with a gear on the main body side of the wind power generation facility, and the nacelle is driven to turn. The first yaw reduction device and the second yaw reduction device are arranged on the main body side of the output pinion of the first yaw reduction device when a load acting on the output pinion is a predetermined value or more. A shaft member that twists and deforms in the rotational direction, or a rotational angle difference in the rotational direction that is equal to or greater than an angle corresponding to the difference between the backlash with respect to the other gear and the backlash with respect to the gear of the output pinion of the second yaw reduction device. The above-described problem is solved by providing the twist generating mechanism in the power transmission system.

  In the present invention, the “main body” on the main body side of the wind power generation facility refers to a “member that moves relative to a member in which the yaw reduction device is incorporated”. In the case of a yaw drive system of a wind power generation facility, a cylindrical column that moves relative to a structural member of a nacelle in which a yaw reduction device is incorporated corresponds to a “main body”.

  Since the intermediate problem focused on the idea of the present invention is not a known problem, it will be briefly described below.

  When the yaw drive system is configured by a plurality of yaw reduction devices, the output pinions of the plurality of yaw reduction devices are uniformly meshed with the swivel gear with the same backlash so that all the yaw reduction devices have the same transmission torque. Need to be deployed.

  Even in a conventional yaw drive system, in the case of “normal driving” in which the outputs of a plurality of yaw reduction devices driven by a motor are applied to one swivel gear, the outputs of the respective yaw reduction devices are made equal. It is relatively easy to control. That is, even if the mechanical backlash amount of each yaw decelerator is uneven, feedback control of the current that actually flows through each yaw decelerator makes the generated torque of each yaw decelerator uniform. It is possible to do to some extent.

  However, this "equal distribution control by current feedback control" cannot be utilized when driven backward from the swivel gear by wind load torque. For this reason, in the conventional yaw drive system, the nacelle is moved by a strong wind, and the yaw reduction device in which the backlash is first packed is forced to bear a heavy burden.

  Furthermore, as described above, normally, in such a strong wind environment, in order to prevent abnormal turning in the uncontrolled state of the nacelle, each rotating element of the yaw reduction device may be maintained in a state stopped by the braking mechanism. Many. For this reason, the rotation of the nacelle is fixed by the yaw speed reduction device first packed with the backlash, and the other yaw speed reduction devices remain in a state where the backlash with the swivel gear is not filled, It can be inferred that the load cannot be received.

  In such a situation, the wind load torque is completely concentrated only on the “specific one yaw reduction gear” that is initially filled with backlash. If one particular yaw reduction device packed with backlash is damaged, the second yaw reduction device with first backlash among the remaining yaw reduction devices will be in the same state. It is thought that the chain will be damaged one after another.

  The present invention regards a phenomenon in which a wind load is applied to only one specific yaw reduction device as an intermediate issue, and reasonably eliminates this intermediate issue. It is configured to receive wind load torque from the side. Thereby, damage to the yaw reduction device can be significantly reduced without unnecessarily increasing the yaw reduction device.

  According to the present invention, it is possible to provide a yaw reduction device and a yaw drive system that are used in a yaw drive system of a wind power generation facility that is less likely to be damaged without unnecessarily increasing the yaw reduction device.

Whole sectional drawing of the yaw reduction gear used for the yaw drive system of the wind power generation equipment which concerns on an example of embodiment of this invention Sectional view along the line II-II in FIG. Front view of wind power generation equipment to which the yaw reduction device is applied The perspective view which shows typically a mode that the said yaw reduction gear is integrated in the nacelle in the yaw drive system of the said wind power generation equipment The top view which shows the state in which the output pinions of four yaw reduction gears are meshing | engaged with the turning external gear of the said yaw drive system Sectional drawing equivalent to FIG. 1 which concerns on an example of other embodiment of this invention Sectional drawing equivalent to FIG. 1 which concerns on an example of other embodiment of this invention. Sectional drawing which expands and shows the principal part of embodiment of FIG. Sectional drawing of the yaw reduction gear equivalent to FIG. 1 which concerns on an example of other embodiment of this invention. Sectional drawing which expands and shows the principal part of embodiment of FIG. Sectional drawing of the yaw reduction gear equivalent to FIG. 1 which concerns on an example of other embodiment of this invention. Sectional drawing which expands and shows the principal part of embodiment of FIG. Sectional drawing of the yaw reduction gear equivalent to FIG. 1 which concerns on an example of other embodiment of this invention. Sectional drawing which follows the arrow XIV-XIV line of FIG. 13 is an enlarged view of the main part of FIG.

  Hereinafter, a configuration of a yaw drive system for a wind power generation facility according to an example of an embodiment of the present invention, in particular, a yaw reduction device therein will be described in detail with reference to the drawings.

  Referring to FIGS. 3 to 5, this wind power generation facility 10 includes a nacelle (power generation chamber) 12 at the top of a cylindrical column (main body of the wind power generation facility) 11. The nacelle 12 incorporates a yaw drive system 14 and a pitch drive system 16. The yaw drive system 14 is for controlling the turning angle of the entire nacelle 12 with respect to the cylindrical column 11, and the pitch drive system 16 is for controlling the pitch angle of the three windmill blades 20 attached to the nose cone 18. belongs to.

  The yaw drive system 14 includes four yaw reduction devices G1 to G4 with a motor 22 and an output pinion 24, and one swivel gear 28 that meshes with each output pinion 24 (see FIG. 4 and FIG. 5: swivel). In this example, the gear 28 is an internal gear with which the output pinion 24 is inscribed, but may be an external gear with which the output pinion is circumscribed). Each of the yaw reduction devices G1 to G4 is fixed to a predetermined position on the structure side of the nacelle 12 via a bolt 29.

  As shown in FIG. 5, in this embodiment, the output pinions 24 of the plurality of yaw reduction devices G <b> 1 to G <b> 4 mesh with the turning gear 28 at positions that are not equidistant in the circumferential direction. This is because when it is attempted to arrange the yaw reduction devices G1 to G4 in the narrow nacelle 12, it is actually difficult to arrange the yaw reduction devices G1 to G4 evenly in the circumferential direction. This is based on the fact that an arrangement with non-equal intervals is more advantageous. Note that the arrangement example in FIG. 5 is merely an example, and may be changed to an appropriate arrangement according to the actual situation in the nacelle, or may be equally spaced in the circumferential direction.

  With this configuration, when the output pinions 24 are simultaneously rotated by the motors 22 of the yaw reduction devices G1 to G4, the output pinion 24 is engaged with the turning gear 28 and the center 36 of the turning gear 28 (see FIG. 4). Revolves around. As a result, the nacelle 12 can be moved relative to the cylindrical column 11 (the swivel gear 28 fixed to the cylindrical column 11), and the entire nacelle 12 is rotated around the center 36 of the swivel gear 28 fixed to the cylindrical column 11. Can be swiveled. Thereby, the nose cone 18 can be directed in a desired direction (for example, the windward direction), and the wind pressure can be efficiently received.

  Since the yaw reduction devices G1 to G4 have the same configuration, the yaw reduction device G1 will be described here.

  Referring to FIG. 1, a yaw reduction device G1 includes a motor 22, an orthogonal gear reduction mechanism 40, first and second parallel shaft reduction mechanisms 41 and 42, and an eccentric oscillating planetary gear reduction mechanism 44 on a power transmission path. Arranged in this order.

  Hereinafter, description will be made in the order on the power transmission path. The motor shaft 46 of the motor 22 also serves as the input shaft of the orthogonal gear reduction mechanism 40, and a hypoid pinion 47 is formed by straight cutting at the load side end of the motor shaft 46 of the motor 22. A brake device (not shown) is provided at the end of the motor shaft 46 on the side opposite to the load.

  The orthogonal gear reduction mechanism 40 includes the hypoid pinion 47 formed by cutting directly at the tip of the motor 22 and the hypoid gear 50 that meshes with the hypoid pinion 47, and changes the rotation direction of the motor shaft 46 to a right angle direction. . The hypoid gear 50 is fixed to the first intermediate shaft 52.

  The first intermediate shaft 52 is directly formed with a spar pinion 54 of the first parallel shaft speed reduction mechanism 41. The first parallel shaft reduction mechanism 41 includes the spar pinion 54 and a spar gear 56 that meshes with the spar pinion 54. The spur gear 56 is fixed to the second intermediate shaft 58. A spar pinion 60 of the second parallel axis reduction mechanism 42 is directly formed on the second intermediate shaft 58.

  The second parallel shaft reduction mechanism 42 includes the spar pinion 60 and a spar gear 64 that meshes with the spar pinion 60. The spur gear 64 is fixed to a hollow output shaft (hollow shaft: the output shaft of the second parallel shaft reduction mechanism 42) 66. The hollow output shaft 66 is connected to the connecting shaft 70 through a spline 68. An eccentric body shaft (second hollow shaft) 72 that is also an input shaft of the eccentric oscillating planetary gear speed reduction mechanism 44 is connected to the load side of the connecting shaft 70 via a spline 92.

  The connection between the hollow output shaft 66, the connecting shaft 70, and the eccentric body shaft (second hollow shaft) 72 will be described in detail later.

  Reference numeral 73 denotes a joint casing that is connected to an anti-load side cover 48C of a planetary gear reduction mechanism 44 described later via a bolt 75.

  The planetary gear reduction mechanism 44 includes two external gears 76, an internal gear 78 in which the external gear 76 oscillates and meshes internally, and the external gear 76 at the axial center position O 1 of the internal gear 78. And an eccentric body shaft 72 having an eccentric body 74 that swings the external gear 76 and an eccentric oscillating type reduction mechanism called a so-called center crank type.

  The two external gears 76 have an eccentric phase shifted by exactly 180 degrees, and rotate and rotate while maintaining an eccentric state in directions away from each other. The casing 48 of the planetary gear speed reduction mechanism 44 is mainly composed of first and second casing bodies 48A and 48B and anti-load side and load side cover bodies 48C and 48D. It is fixed to 12 structures 12A.

  The internal gear 78 includes an internal gear main body 78B integrated with the first casing body 48A, and a cylindrical external gear that is rotatably held by the internal gear main body 78B and functions as internal teeth. A pin 78A is used. The number of internal teeth of the internal gear 78 (the number of external pins 78A) is slightly larger (only 1 in this example) than the number of external teeth of the external gear 76.

  As shown in FIG. 2, the external gear 76 has a plurality of (in this example, 10) inner pins 80 penetrating on the same circumference together with the sliding promotion member 81. The inner pin 80 is integrated with the output flange (carrier) 82 by press fitting, and the output flange 82 is integrated with the output shaft 84 of the yaw reduction device G1.

  Each inner pin 80 is supported at its end by a pressing plate 86, and the pressing plate 86 has a very small gap that makes contact only when a strong radial load is applied to the pressing plate 86. It has and opposes the step part 48C1 of the anti-load side cover body 48C.

  The output shaft 84 is supported by a self-aligning roller bearing 85 incorporated in the inner periphery of the second casing body 48B and a roller 83 disposed on the inner periphery of the first casing body 48A. The roller 83 is disposed coaxially with the outer pin 78A constituting the internal teeth of the internal gear 78, and supports an output flange 82 integrated with the output shaft 84, so that one end of the output shaft 84 is rotatable. I support it.

  The output pinion 24 is connected to the output shaft 84 via a spline 87, and the output pinion 24 is configured to mesh with the swivel gear 28 (FIGS. 4 and 5) already described.

  Here, the configuration of the coupling portion of the hollow output shaft (hollow shaft) 66 -the coupling shaft (shaft member) 70 -the eccentric body shaft (second hollow shaft) 72 of the second parallel shaft reduction mechanism 42 will be described in detail. To do.

  The configuration of the connecting portion between the hollow output shaft 66 and the connecting shaft 70 will be described. A connecting portion between the hollow output shaft 66 and the connecting shaft 70 includes a hollow output shaft 66 of the second parallel shaft reduction mechanism 42 incorporated in a power transmission system (an output stage of the second parallel shaft reduction mechanism 42), Inserted into the hollow output shaft 66, connected to the hollow output shaft 66 on the inner periphery of the hollow output shaft 66, and at the position protruding from the hollow output shaft 66 (which is another member) The connecting shaft 70 is connected to the eccentric body shaft 72 of the planetary gear speed reduction mechanism 44.

  In this embodiment, the hollow shaft 66 has an axial dimension L1 and is supported at both ends by a pair of bearings 88 and 90. The hollow output shaft 66 is connected to the connecting shaft 70 through a spline 68. The connecting shaft 70 is closer to the side opposite to the side where the connecting shaft 70 protrudes from the hollow output shaft 66 (the lower side in the drawing in the example of FIG. 1) than the center C1 in the axial direction of the hollow output shaft 66 (in this example, the axial direction). It is connected to the hollow output shaft 66 via the spline 68 at a position closer to the upper side than the center C1.

  More specifically, one end portion of the hollow output shaft 66, specifically, an end portion on the opposite side to the connection shaft 70 protruding toward the eccentric body shaft 72 (that is, the connection shaft 70 is the hollow output shaft 66). A female spline portion 66B, which is one of the splines 68, is provided on the inner periphery of the other member (the end portion on the opposite side to the end connected to the eccentric body shaft 72 in this embodiment). A male spline portion 70 </ b> A that is the other of the splines 68 is provided at one end portion of the connecting shaft 70. The connecting shaft 70 is inserted into the hollow portion 66A of the hollow output shaft 66, and the male spline portion 70A is connected to the female spline portion 66B provided on the hollow output shaft 66. Further, the other end portion of the connecting shaft 70 is projected from the end portion on the opposite side to the female spline portion 66B of the hollow output shaft 66.

  A plate 100 is fixed to the end surface of the one end of the connecting shaft 70 by bolts 98. The plate 100 is fixed to the axial end surface of the hollow output shaft 66 by bolts 102. Thereby, inspection and replacement | exchange of the connection shaft 70 can be easily performed only by attachment and removal with the volt | bolts 98 and 102. FIG. In the present embodiment, the cover 101 that covers the connecting portion of the hollow output shaft 66 and the connecting shaft 70 is fixed to the casing 103 of the first parallel shaft speed reducing mechanism 41 and the second parallel shaft speed reducing mechanism 42.

  On the other hand, an eccentric body shaft (second hollow shaft) 72 that is also an input shaft of the planetary gear reduction mechanism 44 is connected to the load side of the connecting shaft 70 via a spline 92. The eccentric body shaft 72 has an axial dimension of L2 and is supported by a pair of bearings 94 and 96. In the connecting portion between the connecting shaft 70 and the eccentric body shaft 72 of the eccentric oscillating type planetary gear speed reduction mechanism 44, the connecting structure between the hollow output shaft 66 and the connecting shaft 70 is simply reversed. In the same connection configuration, the connection shaft 70 is connected to an eccentric body shaft 72 that is the second hollow shaft.

  That is, the connecting shaft 70 is closer to the side opposite to the side where the connecting shaft 70 projects from the eccentric body shaft 72 (in this example, the upper side in the drawing) than the center C2 of the eccentric body shaft 72 (in this example, from the center C2 in the axial direction). Is also connected to the eccentric body shaft 72 via the spline 92.

  Specifically, a male spline portion 70B which is one of the splines 92 is provided at the other end portion of the connecting shaft 70, and the other end of the spline 92 is provided at the inner periphery of the end portion of the eccentric body shaft 72 far from the hollow shaft 66. A female spline portion 72B is provided. The connecting shaft 70 is inserted into the hollow portion 72A of the eccentric body shaft 72 from the end closer to the hollow output shaft 66, and is connected via the spline 92 including the male spline portion 70B and the female spline portion 72B. .

  Further, since the connecting shaft 70 is surrounded by the long hollow portions 66A and 72A formed inside the hollow output shaft 66 and the eccentric body shaft 72, there is a problem that the connecting shaft 70 may be significantly bent even if it is strongly twisted. Considered not to.

  As a result, the connecting portion of the hollow output shaft 66 -the connecting shaft 70 -the eccentric body shaft (second hollow shaft) 72 of the second parallel shaft speed reducing mechanism 42 according to the present embodiment is a single (identical) connecting shaft 70. In common, the “two sets” of connecting structures according to the present invention are combined. In this embodiment, the female spline for connecting the connecting shaft 70 to the end of the hollow output shaft 66 far from the eccentric shaft 72 and the end of the eccentric shaft 72 far from the hollow shaft 66. Portions 66B and 72B are provided. That is, the effective axial length L4 of the connecting shaft 70, that is, the connecting portion (spline) between the eccentric body shaft 72 and the connecting shaft 70 from the connecting portion (the axial center of the spline 68) between the hollow output shaft 66 and the connecting shaft 70. The distance to the center of 92 in the axial direction can be secured to the maximum without increasing the size of the device (in the axial direction).

  As a result, the effective axial length of the connecting shaft 70 (the distance from the connecting portion between the hollow output shaft 66 and the connecting shaft 70 to the connecting portion between the eccentric body shaft 72 and the connecting shaft 70) L4 is the same as that of the hollow output shaft 66. It is a long dimension close to the length obtained by adding the axial dimension L1 of the hollow output shaft 66 and the axial dimension L2 of the eccentric body shaft 72 to the dimension L3 between the eccentric body shaft 72 and the eccentric body shaft 72.

  Such a connecting portion configuration is such that the connecting shaft 70 has a predetermined amount of twist deformation (rotational angle phase difference) in the rotation direction under a predetermined condition while ensuring a necessary strength for the torque to be transmitted. ) Only to twist.

  That is, the connecting shaft 70 according to this embodiment has a “backlash difference” with respect to the turning gear 28 of the output pinion 24 in each of the yaw reduction devices G1 to G4 when the load acting on the output pinion 24 is a predetermined value or more. Torsional deformation in the rotational direction over a predetermined angle corresponding to.

  Here, the “predetermined value” of “when the load acting on the output pinion is greater than or equal to the predetermined value” means that the purpose of the present invention is “when a strong wind load torque is applied, each yaw reduction device applies a load evenly. It is determined in consideration of the fact that the load does not concentrate only on a specific yaw reduction device by taking charge.

  Specifically, “a torque equivalent value applied to the output pinion 24 when the motor 22 outputs a rated torque (for example, 1250 kgf in the present embodiment)” is one index. In order to reliably realize the load equal distribution, the maximum value should be set to not more than twice the rated torque equivalent value (for example, 2500 kgf). That is, when a torque twice as large as the rated torque of the motor 22 is generated, the torque applied to the output pinion is the “predetermined value upper limit”.

  On the other hand, the “lower limit of the predetermined value” is not particularly limited in the present invention. However, if the torsional deformation is generated from a too low level, not only the response when driving by the motor 22 is deteriorated but also the required strength is difficult to secure, so that the motor 22 has a fatigue equivalent load (the rated torque of the motor). The value applied to the output pinion 24 when a torque of about half of the torque is output is substantially the lower limit.

  In other words, when only a torque equal to or less than the predetermined value is applied to the output pinion, it is preferable to set so as not to cause a large torsional deformation. As described above, the “predetermined value” of the present invention is equal to or greater than the torque applied to the output pinion when the motor 22 outputs half the rated torque, and the motor 22 has a torque twice the rated torque. Is preferably set to be equal to or lower than the torque applied to the output pinion. In the present embodiment, the torque is set to a value corresponding to the torque applied to the output pinion 24 when the motor 22 outputs the rated torque.

  The “backlash difference” ideally means the backlash amount of the yaw reduction device (the first yaw reduction device or any one of G1 to G4) having the smallest backlash between the turning gear 28 and the output pinion 24; This is the difference from the backlash amount of the yaw reduction device (second yaw reduction device, any of G1 to G4) having the largest backlash. More specifically, “the yaw reduction device having the maximum backlash after the backlash of the yaw reduction device with the smallest backlash is clogged (becomes zero) due to the rotation of the nacelle by the wind load torque. The angle at which the output pinion 24 of the yaw reduction gear having the maximum backlash rotates until the backlash of the motor is eliminated.

  However, if the output pinion 24 of the yaw reduction device with the next smallest backlash meshes with the swivel gear 28 by twisting the connecting shaft 70 of the yaw reduction device with the smallest backlash, it is evenly distributed by the two yaw reduction devices alone. The effect is obtained, and further, when the output pinion 24 of the next yaw reduction device meshes with the turning gear 28 by twisting the connecting shaft 70 of the two yaw reduction devices, an even distribution effect is obtained. Then, after all, the “difference in backlash” may be regarded as a difference in backlash between any two yaw decelerators (the first yaw decelerator and the second yaw decelerator).

  The “corresponding angle” to the difference in backlash means an angle obtained by multiplying the reduction ratio (speed increase ratio when viewed from the output pinion) by the position of the target connecting shaft on the power transmission system. In this embodiment, since the speed increasing ratio of the planetary gear speed reduction mechanism viewed from the output pinion 24 is 43, the angle is 43 times. However, as an actual problem, the actual “difference in backlash” of the output pinion 24 of each yaw reduction device G1 to G4 with respect to the turning gear 28 is not limited to the manufacturing error of the tooth profile of the output pinion 24, and the yaw reduction devices G1 to G4 are nacelle. 12 is also greatly affected by the assembly error when assembled to 12. Therefore, this “difference in backlash” is unknown at the stage of design or manufacture of the yaw reduction gears G1 to G4.

  With regard to the problem of “unknown when designing or manufacturing the yaw reduction gears G1 to G4”, for example, calculating an average value by sampling a plurality of examples of the backlash of the yaw reduction gears G1 to G4 actually attached. This method can be used.

  For example, the inventors measured the average value of the backlash of the most popular wind power generation equipment of 1.5 MW to 3.0 MW class in this viewpoint, and it was about 0.1 mm. Specific design numerical examples based on this value are shown below.

<Regarding the degree of twisting of the connecting shaft 70>
In the case of the present embodiment, the torque equivalent value T1 applied to the output pinion 24 when the motor 22 outputs the rated torque is 1250 kgf, so that the torsional moment T2 acting on the connecting shaft 70 that tends to cause twisting. (N · mm) is because the reduction ratio of the planetary gear reduction mechanism 44 is 43 and the efficiency η is 0.93.
T2 = (1250 kgf / 43) × 0.93
= 27.03 kgf = 264894 N · mm (1)
It becomes.

Here, the torsion angle θ (rad) of the connecting shaft 70 is
θ = (32 · T · L) / (π · G · d ⁴ ) (2)
It can be expressed as T is a torsional moment (N · mm), L is an axial length (mm), G is a shear (lateral) elastic modulus (MPa), and d is an axial diameter (mm).

In this embodiment, the effective axial length L4 = 400 mm is secured as the axial length L of the connecting shaft 70. Now, 8300 kgf / mm ² (81340 MPa), which is a general value of mild steel, is used as the diameter d of the connecting shaft 70, d2 = 20 mm, and the shear (lateral) elastic modulus G. When the magnitude of the twist angle θ (rad) at the connecting shaft 70 is confirmed, the torsional moment T2 (N · mm) acting on the connecting shaft 70 is (32 × 264894 × 400) / (3.14 × 81340 × 20 ⁴ ) = 0.0829 (rad).

  0.0829 (rad) is 4.75 degrees in terms of frequency. That is, when a torque corresponding to the output torque of the motor 22 is applied to the output pinion 24, the connecting shaft 70 in this embodiment is twisted by 4.75 degrees.

  On the other hand, the backlash of 0.1 mm corresponds to 0.1 mm / 88 = 0.00114 (rad) when the number of teeth of the turning gear 28 is 88. In terms of frequency, it is 0.065 degrees. This is the rotation angle of the output pinion 24 with respect to the backlash of 0.1 mm. When the reduction ratio (speed increase ratio) 43 is taken into consideration and converted into the rotation angle at the connecting shaft 70, it becomes 0.065 × 43 = 2.8 degrees, which is smaller than the 4.75 degrees. This is because the backlash (0.1 mm) between the turning gear 28 and the output pinion 24 is eliminated (disappeared) while the connecting shaft 70 is twisted, and the second yaw reduction device can share the load. That means getting.

<About load resistance of connecting shaft 70>
The shear stress τ (MPa) due to twisting in this type of shaft member is expressed by the following equation.
τ = 16T / (π · d ³ ) (3)

When T = T2 = 264894 (N · mm) and d = d2 = 20 (mm) are substituted into the equation (3), the axial shear stress τ1 (MPa) at the connecting shaft 70 is (16 × 264894) / ( 3.14 × 20 ³ = 168.7 MPa, which corresponds to 17.2 kgf / mm ² .

Generally, in the case of the SCM material, the shear stress is about 19 kg / mm ² , and in the case of the carburized material, about 40 kg / mm ² can be secured. Therefore, it is sufficiently possible to ensure the strength that can withstand the shear stress (17.2 kg / mm ² ) generated in the connecting shaft 70.

  In summary, in the apparatus according to the present embodiment, the backlash between the swivel gear 28 and the output pinion 24 is eliminated while maintaining a sufficient load-bearing strength as the connecting shaft 70 by the above configuration and dimension setting. From the above, it can be seen that the amount of twist of the connecting shaft 70 can be secured.

  By the way, in the above calculation example, the torsion and the strength are estimated based on the actual average value of the backlash, but the actual backlash size is the size of the wind power generation facility (more specifically, the rotation gear and the output pinion). Different sizes may be different. For this, for example, a parameter correlated with the “backlash difference” may be selected and used as an index for specifying the “backlash difference”.

  More specifically, the “backlash difference” can be defined by using, for example, a single pitch error of the output pinion 24 of each yaw reduction gear. Here, the “single pitch error” of a gear is defined in JIS B1702-1 and ISO1328-1. “It is defined on the measurement circumference having the same center as the gear shaft near the center of toothpaste. The difference between the actual pitch on the plane perpendicular to the axis and the corresponding theoretical pitch ”can be obtained by measuring the output pinion 24 with a gear tester or the like.

Next, the single pitch error of the output pinion 24 of the first yaw reduction device is P1, the single pitch error of the output pinion 24 of the second yaw reduction device is P2, the single pitch error of the swivel gear 28 is PS, and the output pinion BB is the reference backlash between the gear 24 and the swivel gear 28, and the single pitch error is a positive value for an error in one of the clockwise and counterclockwise directions, and a negative value for an error in the other direction. Shall be taken. The backlash B1 between the output pinion 24 of the first yaw reduction gear and the turning gear 28 and the backlash B2 between the output pinion 24 of the second yaw reduction gear and the turning gear 28 are expressed by the following equations.
B1 = BB- (P1 + PS)
B2 = BB- (P2 + PS)

  Then, the difference between the backlash B1 and B2 is B2−B1 = P1−P2. That is, the difference between the backlash between the output pinion 24 of the first yaw reduction gear and the turning gear 28 and the backlash between the output pinion 24 of the second yaw reduction gear and the turning gear 28 is the first yaw reduction device. Can be defined as the difference between the single pitch error of the output pinion 24 and the single pitch error of the output pinion 24 of the second yaw reduction gear.

  That is, the connecting shaft 70 according to the present embodiment has a single pitch error between the output pinions 24 of the two yaw reduction devices when the load acting on the output pinion 24 of the yaw reduction devices G1 to G4 is equal to or greater than a predetermined value. The manufacturing method including the outer diameter, the total length, the material, and the heat treatment of the connecting shaft 70 is selected so as to be twisted and deformed by an angle obtained by multiplying the difference by the speed increasing ratio from the output pinion to the connecting shaft 70.

  According to this method, the connecting shaft 70 and the like can be designed depending on only the parameters belonging to the yaw reduction device alone, so that it is not necessary to check the actual backlash one by one.

  Note that “backlash” here basically means “backlash related to a dimensional gap between the turning gear 28 and the output pinion 24 of each yaw reduction gear G1 to G4”. Preferably, from the output pinion 24 to the brake mechanism (which can brake the rotation of the output pinion), a backlash associated with a dimensional gap between the turning gear 28 and the output pinion 24 of each yaw reduction gear G1 to G4 is reached. It is better to use the concept of “correction backlash” that takes into account the backlash of the entire power transmission system up to the above.

  In this embodiment, since the motor shaft 46 of the motor 22 is provided with a brake mechanism (not shown), this “correction backlash” is the backlash between the turning gear 28 and the output pinions 24 of the yaw reduction devices G1 to G4. In addition, each backlash of gears and the like in the eccentric rocking planetary gear speed reduction mechanism 44, the second parallel shaft speed reduction mechanism 42, the first parallel shaft speed reduction mechanism 41, and the orthogonal gear speed reduction mechanism 40, and further, a rotation mechanism of the motor 22 “Correction backlash” is also taken into account including backlash in a bearing back that supports the motor shaft 46. Incidentally, when the brake mechanism is realized by, for example, the self-lock function of the worm speed reduction mechanism as in the embodiment described later, the backlash from the output pinion to the worm speed reduction mechanism is “correction”.

  By using the concept of correction backlash, more accurate and reliable equal distribution can be achieved.

  Next, the operation of the yaw reduction device G1 will be described.

  Referring to FIG. 1 again, the rotation of the motor shaft 46 of the motor 22 is decelerated at the first stage by the meshing of the hypoid pinion 47 and the hypoid gear 50 of the orthogonal gear reduction mechanism 40, and at the same time, the direction of the rotation shaft is changed 90 degrees. It is transmitted to the first intermediate shaft 52 of the parallel shaft reduction mechanism 41.

  The rotation of the first intermediate shaft 52 is transmitted to the second intermediate shaft 58 by the engagement of the spur pinion 54 and the spur gear 56 of the first parallel shaft speed reduction mechanism 41, and further the spur pinion 60 of the second parallel shaft speed reduction mechanism 42 and It is transmitted to the hollow output shaft 66 through the spur gear 64. The rotation of the hollow output shaft 66 is transmitted to the eccentric body shaft 72 of the eccentric oscillating planetary gear reduction mechanism 44 through the spline 68, the connecting shaft 70, and the spline 92. The operation of this part will be described in detail later.

  When the eccentric body shaft 72 of the eccentric oscillating planetary gear speed reduction mechanism 44 rotates, the external gear 76 oscillates and rotates through the eccentric body 74 (while being in contact with the internal gear 78). For this reason, a phenomenon occurs in which the meshing positions of the external gear 76 and the internal gear 78 are sequentially shifted. As a result, each time the eccentric body shaft 72 of the planetary gear speed reduction mechanism 44 rotates, the external gear 76 swings once, and the internal gear 78 (which is fixed to the nacelle 12) is swung. The phase shifts by one tooth (by the number of teeth difference) (rotation component is generated).

  By taking out the rotation component from the output shaft 84 via the inner pin 80 and the output flange (carrier) 82, the planetary gear reduction mechanism 44 can reduce the speed.

  The rotation of the output shaft 84 is transmitted to the output pinion 24 through the spline 87. Since the output pinion 24 meshes with the swivel gear 28, and the swivel gear 28 is fixed to the cylindrical column 11, the output pinion 24 eventually rotates while rotating and the center 36 of the swivel gear 28 is rotated. Revolves around.

  Since the yaw reduction devices G1 to G4 are fixed to the nacelle 12, the nacelle 12 rotates (turns) in the horizontal direction with respect to the axis 36 of the turning gear 28 on the cylindrical column 11 side.

  Here, for example, a huge “wind load torque” that tries to force the nacelle 12 to turn when a gust or the like acts on the windmill blade 20 or the nacelle itself is generated from the output pinion 24 side of the yaw reduction gears G1 to G4. Suppose that it is input. In this case, this huge wind load torque drives the yaw drive system 14 from the reverse and tries to rotate the output pinion 24 of the yaw reduction gear G1 via the swivel gear 28.

  In general, when a strong wind is blowing, the rotating elements of the yaw reduction gears G1 to G4 are made non-rotatable by a brake mechanism provided on the non-load side of the motor 22, and the nacelle 12 is not controlled by the strong wind. Prevents turning. Therefore, in the conventional yaw drive system, the yaw speed reduction device (for the sake of convenience, the first yaw speed reduction device G1) in which the backlash is first packed by the movement of the nacelle 12 is “only one” and the swivel gear 28 is In order to prevent further rotation, the output pinions 24 of the other yaw reduction gears G2 to G4 remain in a state where backlash with the swivel gear 28 is not filled, and wind load torque from the swivel gear 28 side is left. Can not receive.

  Therefore, after all, the wind load torque is concentrated only on the “first yaw reduction gear G1” first packed with the backlash, and the situation where the first yaw reduction gear G1 is easily damaged is likely to occur. Conceivable. If the first yaw reduction device G1 is damaged, the second yaw reduction device with the first backlash among the remaining yaw reduction devices will be in the same state. It is thought that the yaw reduction device has fallen into a situation where it is damaged in a chain.

  However, according to the present embodiment, when a load greater than a predetermined value is applied from the swivel gear 28 to the output pinion 24 of the first yaw reduction gear G1 that is initially packed with backlash (in this embodiment, the motor 22 has a rated torque). When a load greater than the load applied to the output pinion 24 is applied), the connecting shaft 70 is twisted and deformed by this load. For this reason, the output pinion 24 is further left as it is due to the torsional deformation of the connecting shaft 70 (although the rotation of the rotation elements of the speed reduction devices G1 to G4 is basically stopped by the brake mechanism). The rotation can continue, and the swivel gear 28 can also follow the rotation and continue to rotate.

  The amount of torsional deformation at the connecting shaft 70 is set so as to secure a difference of backlash when a load of a predetermined value or more is applied from the output pinion 24 side. Therefore, the backlash of another yaw reduction device (for example, the second yaw reduction device G2) having the second smallest backlash is packed while the turning gear 28 performs the following rotation, and the load from the turning gear 28 is reduced. 2 can also be received by the yaw reduction device G2. As a result, a part of the load from the swivel gear 28 side that has been applied only to the first yaw reduction device G1 as it is in the prior art is distributed to the second yaw reduction device G2.

  Since the second yaw reduction device G2 can also be twisted and deformed at the connecting shaft 70, similarly, the third yaw reduction device G3 is also filled with backlash so as to handle the load from the swivel gear 28. Become. And finally, the torsional deformations at the connecting shafts 70 of the yaw reduction devices G1 to G4 are balanced so that the respective connecting shafts 70 of the yaw reduction devices G1 to G4 are subjected to substantially the same reaction force. To do.

  In a state in which the twist deformation is balanced, regardless of whether the backlash is large or small (regardless of whether the reaction force is applied to the swivel gear 28 is early or late), all the yaw reduction devices G1 to G4 are swung. The load from the gear 28 is evenly distributed.

  If necessary, for example, when the yaw drive system 14 is configured by four yaw reduction devices G1 to G4 as in the present embodiment, the wind load torque is substantially (compared to the conventional one). Is reduced to almost 1/4 (windproof load torque characteristics are expanded by about 4 times). As a result, breakage (especially chain breakage) of each of the yaw decelerators G1 to G4 can be extremely effectively prevented while using the yaw decelerators G1 to G4 having the same size as the conventional one.

  As in this embodiment, when the yaw reduction devices G1 to G4 are not arranged at equal intervals in the circumferential direction of the swivel gear 28, it is particularly preferable that the yaw reduction devices G1 to G4 receive the wind load torque evenly. difficult. For this reason, all the yaw reduction devices G1 to G4 mounted can share and receive the wind load torque from the swivel gear 28 side by substantially equal magnitude by the function of torsional deformation. The benefits are extremely large.

  Needless to say, the shaft member (connecting shaft 70) for transmitting power needs to have a certain strength (rigidity or thickness) in order to reliably transmit the torque to be transmitted without damaging it. In order to ensure a large “torsional deformation amount” according to the present invention under a condition in which this strength is ensured, the shaft member must have a corresponding “axial length”. For this reason, if designed simply, the yaw reduction devices G1 to G4 become large.

  In the present embodiment, the connecting shaft 70 is inserted into the hollow output shaft 66 of the second parallel shaft speed reduction mechanism 42 and is connected to the hollow output shaft 66 on the inner periphery of the hollow output shaft 66. Then, the connecting shaft 70 is connected to the hollow output shaft 66 on the side opposite to the side where the connecting shaft 70 protrudes from the hollow output shaft 66 with respect to the axial center C1 of the hollow output shaft 66. It is configured.

  A similar configuration is also adopted between the connecting shaft 70 and the eccentric body shaft (second hollow shaft) 72.

  For this reason, the axial length L1 of the hollow output shaft 66 and the axis of the eccentric body shaft 72 are set to the dimension L3 between the hollow output shaft 66 and the eccentric body shaft 72 (without substantially increasing the overall length of the reduction gear G1). It is possible to incorporate a connecting shaft 70 having an extremely long effective axial direction length L4 close to the length plus the direction length L2.

  Incidentally, if the connecting shaft of the same power transmission system is designed by the conventional method without changing the overall length of the yaw reduction device, regardless of the method of the present embodiment, the length of the connecting shaft 70 is the hollow length. The distance L3 + α between the output shaft 66 and the eccentric body shaft 72, that is, about 1/2 the length of the present embodiment. For this reason, for example, if the same trial calculation is performed in the calculation example using the above-described formulas (1) to (3), the torsional magnitude obtained by the connecting shaft is only 2.75 degrees. For this reason, there is a possibility that the 2.8 degree of twist necessary for eliminating the backlash between the turning gear 28 and the output pinion 24 cannot be secured. In other words, it is necessary to make the outer diameter d2 of the connecting shaft 70 smaller (thin) in order to secure the “intended twist amount” of the present embodiment with this length of the connecting shaft. Then, there is a possibility that the load resistance of the connecting shaft is not sufficient.

  According to the connection configuration of the connection shaft 70 of the present embodiment, a predetermined torque transmission is performed on the connection shaft 70 while maintaining the compactness of the entire size of the yaw reduction gear G1 (to G4). A sufficient amount of torsional deformation can be ensured while maintaining the strength.

  In the above embodiment, the motor 22, the orthogonal gear reduction mechanism 40, the first and second parallel shaft reduction mechanisms 41 and 42, and the planetary gear reduction mechanism 44 are arranged in this order on the power transmission path. In the present invention, the specific configuration of the speed reduction mechanism of the yaw speed reduction device is not particularly limited to the above configuration.

  FIG. 6 shows a configuration example of a yaw reduction device G1a that employs a worm reduction mechanism 110 in place of the orthogonal gear reduction mechanism 40, the first parallel axis reduction mechanism 41, and the second parallel axis reduction mechanism 42 in the previous embodiment. . The other three yaw reduction devices G2a to G4a have the same configuration as the yaw reduction device G1a.

  In this embodiment, the motor is mounted in a direction perpendicular to the paper surface. However, in FIG. 6, the motor itself is not displayed, and only the motor mounting hole 114 is displayed.

  The worm reduction mechanism 110 includes a worm 116 and a worm gear 118. The worm gear 118 is integrated with a worm output shaft 120 (which is an output shaft of the worm reduction mechanism 110). The worm output shaft 120 is hollow and has the same configuration as the hollow output shaft 66 of the second parallel axis reduction mechanism 42 in the previous embodiment, and is connected to the connection shaft 70 in the same connection configuration as in the previous embodiment. It is connected. The configuration after the connecting shaft 70 is the same as that of the previous embodiment.

  In this embodiment, the reduction ratio of the worm reduction mechanism 110 is set to 30 or more (preferably 40 or more). When the reduction ratio of the worm reduction mechanism 110 is set to 30 or more (preferably 40 or more), the self-lock function (function that does not rotate due to a load from the load side) of the worm reduction mechanism 110 itself is used as a “brake mechanism”. be able to. For this reason, the brake mechanism attached to the motor 22 which was essential in the previous embodiment can be omitted, and the cost can be reduced accordingly.

  Also in this embodiment, the worm output shaft (hollow shaft) 120, the connecting shaft 70, and the eccentric body shaft 72 of the worm speed reduction mechanism 110 are connected in the same manner as in the previous embodiment. The same effect as the embodiment can be obtained.

  In the yaw reduction device G1b (G2b to G4b) of FIGS. 7 and 8, the worm reduction mechanism 110 of FIG. 6 is left, and the eccentric oscillating planetary gear reduction mechanism (44) is replaced by a second stage. A configuration example in which the first and second simple planetary gear reduction mechanisms 130 and 140 are replaced is shown.

  The first simple planetary gear reduction mechanism 130 includes a sun gear 132, a planetary gear 134, and an internal gear 136. The sun gear 132 functions as an input member, and the carrier 138 that supports the planetary gear 134 functions as an output member. Yes.

  The second simple planetary gear reduction mechanism 140 includes a sun gear 142, a planetary gear 144, and an internal gear 146 connected to the carrier 138 via a spline 139. The sun gear 142 supports the input member and the planetary gear 144. The carrier 148 functioning as an output member.

  The connection structure between the worm output shaft 120 and the connection shaft 150 is the same as the connection structure between the worm output shaft 120 and the connection shaft 70 in the embodiment of FIG. The sun gear 132 has a tooth part 132A and an extension part 132B extending from the tooth part 132A toward the axial load side, and a hollow part 132C penetrating in the axial direction. On the inner periphery of the hollow portion, a female spline portion 132D, which is one of the splines 139 for connecting to the connecting shaft 150, is formed at the end of the tooth portion 132A far from the worm output shaft 120. The female spline portion 132D is formed across the center of the sun gear 132 in the axial direction, but the region opposite to the side where the connecting shaft 150 protrudes toward the worm output 120 is larger. Therefore, even in such a case, the sun gear (hollow shaft or second hollow shaft) 132 is connected to the male spline 150A, which is the other of the splines 139 of the connecting shaft 150, on the opposite side of the connecting shaft 150 protruding. Will be.

  The carrier 148 of the second simple planetary gear reduction mechanism 140 is taken out from the output shaft 160 via the spline 154 and transmitted to the output pinion 162. In this embodiment, the output shaft 160 and the output pinion 162 are integrated from the beginning.

  FIG. 9 shows an example of still another embodiment of the present invention. FIG. 10 is an enlarged view of the main part.

  In this embodiment, the yaw reduction device G1c (the same applies to the other yaw reduction devices G2c to G4c) includes two eccentric oscillating planetary gear reduction mechanisms 170 and 180 as the reduction mechanism. The basic configuration of the power transmission system of the planetary gear speed reduction mechanism 170 of the front stage and the planetary gear speed reduction mechanism 180 of the rear stage is the same as that of the planetary gear speed reduction mechanism 44 of the previous embodiment. The same reference numerals as those in FIG. 5 are denoted by P in the preceding stage and S in the subsequent stage. Other substantially identical members are denoted by the same reference numerals.

  In this embodiment, as shown in FIG. 10, the output shaft 84P integrated with the front output flange 82P is the shaft member (connection shaft) of the present invention, and the rear eccentric shaft 72S is the hollow shaft of the present invention. Is functioning as That is, the output shaft 84P is inserted into the eccentric body shaft 72S, connected to the eccentric body shaft 72S via the spline 190 on the inner periphery of the eccentric body shaft 72S, and at a position protruding from the eccentric body shaft 72S (others) And is connected to the inner pin 80P of the eccentric rocking type planetary gear reduction mechanism 170 of the preceding stage. That is, in this embodiment, the output shaft 84P slightly protrudes from the eccentric body shaft 72S to the lower side of the paper in FIGS. 9 and 10, but on the paper surface connected to another member (inner pin 80P). The side corresponds to the “projecting side” in the present invention.

  The output shaft 84P is closer to the side opposite to the side where the output shaft 84P protrudes from the eccentric body shaft 72S (the upper side in FIG. 9 and FIG. 10) than the center C3 in the axial direction of the eccentric body shaft 72S. It is connected to the eccentric body shaft 72S via the spline 190 at a position closer to the lower side of the paper than C2. Specifically, the eccentric body shaft 72S is connected at the inner periphery of the end portion farther from the inner pin 80P.

  Therefore, the output shaft 84P as the connecting shaft has a structure that can ensure a length substantially the same as the length L5 of the eccentric body shaft 72S and is likely to be twisted.

  Also in this embodiment, when the wind load torque is input from the output pinion 24 side, the output shaft 84P is twisted more than the rotation angle corresponding to the difference in backlash between the turning gear 28 and the output pinion 24. Is set to occur. Therefore, also in this embodiment, the same operation effect as the previous embodiment (the operation effect that all the yaw reduction devices G1c to G4c receive the load from the output pinion 24 side by almost the same amount) is obtained.

  FIG. 11 shows an example of still another embodiment of the present invention. FIG. 12 is an enlarged view of the main part.

  The yaw reduction device G1d (the same applies to the other yaw reduction devices G2d to G4d) includes an external gear 200, an internal gear 202 in which the external gear 200 swings and meshes internally, and an internal gear 202. A plurality of eccentric shafts (only three are shown in this example) having eccentric bodies 204 that are disposed through the external gear 200 at positions shifted from the axis O2 and swing the external gear 200. And a distribution type eccentric oscillating speed reduction mechanism 208.

  A joint shaft 210 is attached to the motor shaft of the motor (both not shown), and a pinion 212 is integrally formed at the tip of the joint shaft 210. The pinion 212 is meshed with a plurality of sorting gears 214 (three in this example: only one is shown in the example) provided on the same circumference. The sorting gear 214 is connected to the connecting shaft 216 via a spline 217. In this embodiment, the connecting shaft 216 is arranged / connected to all three eccentric body shafts 206, but the connecting shaft 216 is not arranged / connected to one or two eccentric body shafts 206, and the rest. The connecting shaft 216 may be arranged and connected only to the eccentric body shaft 206.

  The connecting shaft 216 is connected to the eccentric body shaft (hollow shaft) 206 via the spline 220. In this embodiment, the lower side of the connection shaft 216 in FIGS. 11 and 12 is not connected to other members at the protruding position, and the upper side is connected to the distribution shaft 214 which is another member, so the upper side is The side protrudes from the eccentric body shaft (hollow shaft) 206. The eccentric body shaft 206 is supported by a pair of bearings 222 and 224, and the spline 220 is provided at an axial position overlapping the bearing 224 on the side where the connecting shaft 216 does not protrude.

  As a result, also in this embodiment, the connecting shaft 216 is closer to the side opposite to the side from which the connecting shaft 216 protrudes from the eccentric shaft 206 than the axial center C4 of the eccentric shaft 216 (which is a hollow shaft) (see FIG. 11, near the lower side of the sheet of FIG. 12, and is connected to the eccentric body shaft 206 via the spline 220.

  More specifically, the end of the eccentric body shaft 206 opposite to the distribution gear 214 is supported by the output flange 231 (the output flange 231 is extended and the output pinion 230 is fixed) by the bearing 224. The output flange 231 is disposed. A female spline portion 206A, which is one of the splines 220 for connecting to the connecting shaft 216, is formed on the inner periphery of the end portion of the eccentric body shaft 206 that passes through the output flange 231. The connecting shaft 216 is inserted into the hollow portion of the eccentric body shaft 206, and one end is connected to the female spline portion 206A via the male spline portion 216A which is the other of the splines 220, and the other end portion is connected to the hollow portion. Projecting and the sorting gear 214 is fixed.

  That is, by arranging the eccentric body shaft 206 through the output flange 231, the length of the eccentric body shaft 206 is made as large as possible, and by connecting the connecting shaft 216 to the inner periphery of the end of the eccentric body shaft 206, The length of the connecting shaft 216 (the distance from the connecting portion between the connecting shaft 216 and the eccentric body shaft 206 to the connecting portion between the connecting shaft and the sorting gear (other member) 214) can be increased without increasing the axial dimension of the apparatus. Secure as long as possible.

  In this embodiment, as the axial length L6 of the connecting shaft 216, a length longer than the axial length L7 of the eccentric body shaft 106 can be ensured, and the strength for transmitting the necessary torque is maintained. However, when the load acting on the output pinion 230 is equal to or greater than a predetermined value, the rotation direction is greater than the rotation angle corresponding to the difference in backlash between the yaw reduction devices G1d to G4d with respect to the turning gear (28) of the output pinion 230. Can be twisted and deformed.

  In this embodiment, similarly to the previous embodiments, it is possible to realize the load distribution between the yaw reduction devices G1d to G4d when the wind load torque is applied to the output pinion 230, and the three eccentric body shafts 206. Is designed so that torsional deformation occurs with respect to the connecting shaft 216 that drives the motor, and in the bidirectional torque transmission of torque transmission from the motor side and wind load torque transmission from the output pinion 230 side, It is also possible to obtain an equal distribution function of torque transmission between the eccentric shafts 206 of the book.

  Although not shown, in this sort-type eccentric oscillating speed reduction mechanism, a part (for example, only one) of a plurality of eccentric body shafts is driven to drive an external gear. A reduction mechanism that is used as an eccentric body shaft and that is used as a driven eccentric body shaft that only supports the oscillation of the external gear is known for other eccentric body shafts, and is applicable to such a reduction mechanism. .

  By the way, in all of the embodiments so far, a single shaft member is incorporated as a component that twists and deforms, but a plurality of members may have the same function. In short, the present invention provides a power transmission system with a predetermined amount or more in the rotational direction between the connecting portion with the front stage side and the connecting portion with the rear stage side when the load acting on the output pinion is a predetermined value or more. It is only necessary to have a twist generating shaft member or a twist generating mechanism having a function capable of generating the rotational angle phase difference.

  An example of this is shown in FIG. 14 is a cross-sectional view taken along the line XIV-XIV in FIG. 13, and FIG. 15 is an enlarged view of a main part of FIG.

  The basic structure of the speed reduction mechanism of the power transmission system of the yaw reduction device G1e (G2e to G4e is the same) according to this embodiment is the same as that of the previous embodiment of FIG. What is different from the embodiment of FIG. 1 is the structure of the connecting portion between the second parallel shaft speed reduction mechanism 42 and the eccentric oscillating planetary gear speed reduction mechanism 44. That is, in this yaw reduction device G1e, the component that generates the rotation angle phase difference when the wind load torque is applied from the output pinion 24 side is not the front side (not by the connecting shaft 70 that is a single shaft member). The torsion generating mechanism 248 that allows a rotation angle difference of a predetermined value or more between the connecting portion and the connecting portion on the rear stage side.

  In more detail, in the yaw reduction device G1e according to this embodiment, the hollow output shaft 250 of the second parallel shaft reduction mechanism 42 is connected to the connection member 254 via the key 252. A connecting portion by the key 252 constitutes a connecting portion on the front stage side of the twist generating mechanism 248. The twist generation mechanism 248 is mainly configured by a connecting member 254, a spring 260, and a block body 262. The connecting member 254 integrally has a circular spring accommodating portion 256 having an outer diameter d1 on the load side. As shown in FIGS. 14 and 15, the spring accommodating portion 256 has a groove portion 256 </ b> A, and accommodates a plurality of (four in the illustrated example) springs 260 in the groove portion 256 </ b> A. The spring 260 is fixed to the block body 262. The block body 262 is connected to the input shaft 264 of the eccentric rocking planetary gear speed reduction mechanism 44 via a spline 266. The connecting portion by the spline 266 constitutes a connecting portion on the rear stage side of the twist generating mechanism 248. The input shaft 264 is further connected to an eccentric body shaft 272 having an eccentric body 270 via a key 268.

  Since the other configuration is the same as the configuration of FIG. 1, the same reference numerals as those of the embodiment of FIG.

  With this configuration, when the hollow output shaft 250 tries to rotate by driving the motor, the spring accommodating portion 256 of the connecting member 254 rotates via the key 252 and rotates in the circumferential direction with respect to the spring 260 accommodated in the groove portion 256A. Power is applied. As a result, the block body 262 to which the spring is fixed is rotated, and the rotation of the hollow output shaft 250 is slightly delayed (with a phase difference of a predetermined rotation angle), and the planetary gear reduction of the eccentric oscillation type It is transmitted to the input shaft 264 of the mechanism 44.

  Conversely, when wind load torque is input from the output pinion 24 side, the input shaft 264 of the planetary gear speed reduction mechanism 44 tries to rotate, and the block body 262 connected to the input shaft 264 via the spline 266. Tries to rotate. This movement is transmitted to a spring 260 fixed to the block body 262. As a result, the “joining portion with the front side by the key 252” of the torsion generating mechanism 248 that maintains the stopped state by a brake mechanism (not shown) attached to the motor 22, The “connecting portion” can be moved by the amount of deformation of the spring 260 within the groove portion 256A (becomes a state having a rotational angle phase difference). As a result, the output pinion 24 can continue to rotate further from the position where the backlash of the turning gear 28 and the output pinion 24 is filled.

  And while this further rotation is permitted, the backlash of the other yaw reduction gears G2e to G4e is filled, and in the other yaw reduction gears G2e to G4e, similar further rotation occurs, and eventually the wind load Torque is evenly distributed.

  As described above, in the present invention, the intended object can also be obtained by dividing the originally-integrated member into the front stage side and the rear stage side and connecting them in the rotational direction with an elastically deformable mechanism such as a spring mechanism. Can be realized. The specific configuration of the twist generating mechanism is not limited to this example.

  In the above embodiment, the present invention is applied to a yaw driving system including four yaw reduction devices in a wind power generation facility, but the number of yaw reduction devices is limited to four. Instead, it may be more or less than four.

  In the embodiment, both ends of the connecting shaft (shaft member) are connected to the hollow shaft (the hollow shaft, the second hollow shaft), but one end of the connecting shaft is not necessarily connected to the hollow shaft. For example, the sun gear 132 may be integrally formed at one end of the connecting shaft 150 as long as it is connected to a solid shaft or has the structure shown in FIGS.

  Further, when both ends of the connecting shaft (shaft member) are connected to the hollow shaft (the hollow shaft, the second hollow shaft), in the embodiment, for any hollow shaft, the connecting shaft is more than the axial center. It is connected to the connecting shaft on the opposite side of the protrusion, but it is not limited to this, and if the necessary twist amount can be secured, about the connecting position with one of the hollow shafts Further, it may be connected closer to the side where the connecting shaft protrudes than the center in the axial direction.

  In the embodiment, it is connected to the connecting shaft at the inner periphery of the end of the hollow shaft, and the effective axial length of the connecting shaft (the distance from the connecting portion of the connecting shaft and the hollow shaft to the connecting portion of the connecting shaft and other members). However, it is not limited to connecting at the end of the hollow shaft, and the connecting shaft (shaft member) is connected to other members from the axial center of the hollow shaft. As long as it is closer to the opposite side, the connection may be performed at any position.

10 ... wind power generation equipment 11 ... cylindrical support 12 ... nacelle (power generation room)
DESCRIPTION OF SYMBOLS 14 ... Yaw drive system 16 ... Pitch drive system 18 ... Nose cone 20 ... Windmill blade 22 ... Motor 24 ... Output pinion 44 ... Planetary gear reduction mechanism 66 ... Hollow output shaft (hollow shaft)
70: Connecting shaft (shaft member)
72: Eccentric body shaft (second hollow shaft)
76 ... External gear (planetary gear)
78 ... Internal gear 80 ... Inner pin (planetary pin)
82 ... Output flange (carrier)
84 ... Output shaft G1-G4 ... Yaw reduction device

Claims (14)

The yaw reduction device used in a yaw drive system of a wind power generation facility that meshes output pinions of a plurality of yaw reduction devices with a gear on the main body side of the wind power generation facility to drive the nacelle to turn,
A hollow shaft built into the power transmission system;
A shaft member inserted into the hollow shaft, connected to the hollow shaft at the inner periphery of the hollow shaft, and connected to another member at a position protruding from the hollow shaft;
The shaft member is connected to the hollow shaft closer to the side opposite to the side where the shaft member protrudes from the hollow shaft than the axial center of the hollow shaft. Yaw speed reducer used in the system. In claim 1,
The other member is a second hollow shaft;
The shaft member is inserted into the second hollow shaft, and is connected to the second hollow shaft on the inner periphery of the second hollow shaft. Yaw speed reducer. In claim 2,
The shaft member is connected to the second hollow shaft closer to the opposite side of the hollow shaft than the center in the axial direction of the second hollow shaft. Yaw speed reducer used for. In any one of Claims 1-3,
The shaft member is connected at an axial end portion of the hollow shaft. A yaw reduction device used in a yaw drive system of a wind power generation facility. In any one of Claims 1-4,
The yaw reduction device used for a yaw drive system of a wind power generation facility, wherein the shaft member is replaceable without removing the yaw reduction device from a nacelle of the wind power generation facility. In any one of Claims 1-5,
The yaw reduction device is disposed at an axial center position of the external gear, an internal gear that is internally meshed while the external gear is swinging, and swings the external gear. A center crank type eccentric oscillating type speed reduction mechanism having an eccentric body shaft having an eccentric body, wherein the eccentric body shaft is the hollow shaft. Yaw reducer used in yaw drive system. In any one of Claims 1-5,
The yaw reduction device is disposed at a position shifted from an external gear, an internal gear that is internally meshed while the external gear is swung, and an axis of the internal gear, and the external gear. A distributed-type eccentric oscillating speed reduction mechanism having a plurality of eccentric body shafts having a rocking eccentric body, and at least one of the plurality of eccentric body shafts is connected to the hollow shaft; A yaw reduction device used for a yaw drive system of a wind power generation facility. In any one of Claims 1-5,
The yaw reduction device has a simple planetary gear reduction mechanism including a sun gear, a planetary gear, and an internal gear, and the sun gear serves as the hollow shaft. Yaw speed reducer used in drive systems. A wind power generation system yaw drive system for rotating a nacelle by engaging output pinions of a plurality of yaw speed reduction devices including at least a first yaw speed reduction device and a second yaw speed reduction device with a gear on the main body side of the wind power generation facility. And
The first yaw reduction device and the second yaw reduction device are:
When the load acting on the output pinion is a predetermined value or more,
Twist deformation in the rotational direction by an angle corresponding to the difference between the backlash of the output pinion of the first yaw reduction gear with respect to the gear on the main body side and the backlash of the output pinion of the second yaw reduction gear with respect to the gear on the main body side. A twist generating mechanism that generates a rotation angle difference in the shaft member or the rotation direction,
A yaw drive system for wind power generation equipment, which is provided in the power transmission system. In claim 9,
The shaft member or the twist generating mechanism is twisted and deformed by an angle corresponding to a difference between a single pitch error of the output pinion of the first yaw reduction device and a single pitch error of the output pinion of the second yaw reduction device. Alternatively, a yaw drive system for a wind power generation facility characterized by generating a difference in rotation angle. In claim 9 or 10,
The shaft member or the twist generation mechanism has a backlash portion of the entire power transmission system from the output pinion to the brake mechanism capable of braking the rotation of the output pinion, due to the backlash between the output pinion and the gear on the main body side. A yaw drive system for a wind power generation system, characterized in that a torsional deformation or a rotation angle difference more than an angle corresponding to the added correction backlash is generated. In any one of Claims 9-11,
The predetermined value is set to be equal to or less than twice the rated torque of a motor that drives the yaw reduction device. A first yaw reduction device and a second yaw reduction device that are used in a yaw drive system of a wind power generation facility that meshes output pinions of a plurality of yaw reduction devices with a gear on the main body side of the wind power generation facility to rotate the nacelle. A device,
When the load acting on the output pinion is a predetermined value or more, this corresponds to the difference between the single pitch error of the output pinion of the first yaw reduction device and the single pitch error of the output pinion of the second yaw reduction device. A shaft member that twists and deforms in the rotational direction beyond the angle to be rotated or a twist generating mechanism that generates a rotational angle difference in the rotational direction is provided in the power transmission system. Yaw speed reducer and second yaw speed reducer. In claim 13,
The predetermined value is set to be equal to or less than twice the rated torque of the motor that drives the yaw reduction device. The first yaw reduction device used in the yaw drive system for wind power generation equipment and the second Yaw speed reducer.

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