JP5938359B2 - Reduction gear used for wind power generation equipment - Google Patents

Description

  The present invention relates to a reduction gear used for wind power generation equipment.

  Patent Document 1 discloses a reduction gear used for a wind power generation facility.

  As a speed reducer used in wind power generation equipment, a yaw drive speed reducer for rotating a nacelle (power generation chamber) installed at the top of a support in a horizontal plane, or an angle of a windmill blade There is a reduction device for driving a pitch for changing.

  The nacelle of the wind power generation facility is located very high from the ground and only a very narrow space is secured. On the other hand, each reduction gear used for wind power generation facilities has a considerable weight. Therefore, handling etc. is difficult until it is carried into the nacelle.

  Therefore, in Patent Document 1, the casing of the speed reducer can be separated into a high speed side casing body including an orthogonal gear mechanism and a low speed side casing body including a final stage speed reducing mechanism. The structure enclosed in a casing body is disclosed. Thereby, the handleability of a reduction gear can be improved more.

Japanese Patent Laying-Open No. 2011-231749 (FIGS. 2 to 4)

  However, since the wind power generation facility is a facility installed in a natural environment, it sometimes receives a turbulent wind or a strong gust. Under such circumstances, a “power reverse flow phenomenon” occurs in which a huge wind load is input from the output side of the reduction gear. For this reason, the speed reducer or the like is sometimes placed in a very harsh state and may require maintenance.

  According to the technique disclosed in Patent Document 1, since the casing is separable into a high speed side casing body and a low speed side casing body, only the high speed side casing body is mounted while the low speed side casing body is mounted on the nacelle. It was possible to perform maintenance by separating (disassembling). However, in reality, it was still not easy to handle.

  The present invention has been made to solve such a conventional problem, and provides a reduction gear used for a wind power generation facility capable of performing maintenance work more easily in a narrow nacelle. It is an issue.

  The present invention is a reduction gear used for wind power generation equipment, comprising a hollow structure hollow shaft as a part of a power transmission system, and a power transmission member to the next stage is connected to the inside of the hollow shaft, The hollow shaft is configured such that one end portion of the hollow structure can be exposed from the casing, and the power transmission member is more susceptible to specific changes in transmission of power than other members constituting the power transmission system. The power transmission member is configured to be able to be taken out of the casing from the one end portion of the hollow shaft while the speed reducer itself is installed in the wind power generation facility. It has been solved.

  In the present invention, a hollow shaft having a hollow structure is provided as a shaft constituting the power transmission system. A power transmission member to the next stage is connected to the inside of the hollow shaft. The power transmission member is dared to be a weak part compared to other members constituting the power transmission system, and if a severe situation occurs regarding power transmission, the power transmission member constituting the weak part is Certain changes are made to occur.

  On the other hand, the hollow shaft can expose one end of the hollow structure from the casing. When the specific change occurs in the power transmission member, the power transmission member can be taken out of the casing from the one end of the hollow shaft while the speed reducer itself is installed in the wind power generation facility. Therefore, maintenance is extremely easy.

  ADVANTAGE OF THE INVENTION According to this invention, the reduction gear device used for the wind power generation equipment which can perform a maintenance operation | work more easily in a narrow nacelle can be obtained.

Whole sectional drawing of the reduction gear used for the wind power generation equipment which concerns on an example of embodiment of this invention 1 is an enlarged cross-sectional view of the main part of FIG. Exploded view when taking out the power transmission member of the reduction gear of FIG. The perspective view which shows a mode that the said speed reducer is incorporated in the said wind power generation equipment typically Sectional drawing of the reduction gear equivalent to FIG. 1 which concerns on an example of other embodiment of this invention. The principal part expanded sectional view of FIG. The principal part expanded sectional view equivalent to FIG. 2 which concerns on an example of other embodiment of this invention. FIG. 7 is an exploded view when the power transmission member of the speed reducer of FIG.

  Hereinafter, the configuration of a reduction gear used for a wind power generation facility according to an example of an embodiment of the present invention will be described in detail with reference to the drawings.

  In the present embodiment, the present invention is applied to a reduction gear used for a yaw drive system of a wind power generation facility. The overall structure of the wind power generation facility will be described.

  Referring to FIG. 4, 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 10) 11. The nacelle 12 incorporates a yaw drive system 14 and a pitch drive system 16. The yaw drive system 14 controls the turning angle of the nacelle 12 with respect to the cylindrical column 11. The pitch drive system 16 controls the pitch angle of the three windmill blades 20 attached to the nose cone 18.

  The yaw drive system 14 includes four reduction gears G1 to G4 with a motor 22 and an output pinion 24, and one swivel gear 28 that meshes with each output pinion 24 (the swivel gear 28 is an output in this example). The pinion 24 is an internal gear with which the pinion 24 is inscribed, but it may be an external gear with which the output pinion 24 is circumscribed). Each reduction gear G1-G4 is being fixed to the predetermined position of the structure 12A of the nacelle 12 via the volt | bolt 29 (refer FIG. 1), respectively.

  With this configuration, when the output pinions 24 are simultaneously rotated by the motors 22 attached to the reduction gears G1 to G4, the output pinion 24 meshes with the turning gear 28 and the center 36 of the turning gear 28 (see FIG. 4). ). As a result, the nacelle 12 can be moved relative to the swivel gear 28 fixed to the cylindrical column 11, and the entire nacelle 12 is counteracted at the center 36 of the swivel gear 28 fixed to the cylindrical column 11. You can swivel around. 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 speed reducers G1 to G4 of the yaw drive system 14 have the same configuration, the speed reducer G1 will be described here.

  FIG. 1 is an overall cross-sectional view of a reduction gear G1 of a yaw drive system 14 used in a wind power generation facility according to an example of an embodiment of the present invention, and FIG. 2 is an enlarged cross-sectional view of a main part of FIG.

  In the reduction gear G1, the motor 22, the orthogonal gear reduction mechanism 40, the first and second parallel shaft reduction mechanisms 41 and 42, and the eccentric oscillating planetary gear reduction mechanism 44 are arranged in this order on the power transmission path. Among these, the orthogonal gear reduction mechanism 40 and the first and second parallel shaft reduction mechanisms 41 and 42 are accommodated in the front-stage casing 45.

  In the present embodiment, the front-side casing 45 includes a side cover 45A that also serves as a motor cover, a front-side casing body 45B, a lid body 45C, and a joint casing 45D that also serves as a bridge with the rear-stage casing 48, and is integrated by a bolt 43. Has been. The internal space P1 of the front-side casing 45 is sealed with oil seals (seal members) 71A to 71C and filled with a lubricant.

  The motor shaft 46 of the motor 22 also serves as an input shaft of the orthogonal gear reduction mechanism 40, and a hypoid pinion 47 is formed by cutting directly at the tip. 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 a hypoid pinion 47 and a hypoid gear 50. The first parallel shaft reduction mechanism 41 includes a spar pinion 54 and a spar gear 56. The second parallel axis reduction mechanism 42 includes a spar pinion 60 and a spar gear 64. The spur gear 64 is fixed to a hollow hollow shaft 66 (an output shaft of the second parallel shaft reduction mechanism 42).

  Thus, the power transmission system of this embodiment includes a hollow shaft 66 having a hollow structure in a part thereof. A connecting shaft (power transmission member) 70 to the next stage is connected to the inside of the hollow shaft 66.

  The configuration in the vicinity of the hollow shaft 66 and the connecting shaft 70 will be described in detail later. Here, the eccentric oscillating planetary gear speed reduction mechanism 44 disposed downstream of the hollow shaft 66 and the connecting shaft 70 will be described. I will explain it first.

  The planetary gear speed reduction mechanism 44 includes an input shaft 73 connected to a connecting shaft (power transmission member) 70 via a joint ring member 79, and two eccentric bodies 74 integrated with the input shaft 73 via a key 75. Two external gears 76 that are incorporated in the outer periphery of the eccentric body 74 and are swung by the eccentric body 74, and an internal gear 78 that is internally meshed while the external gear 76 is swung. This is an eccentric oscillating type deceleration mechanism called a so-called center crank type.

  The planetary gear reduction mechanism 44 is accommodated in the rear casing 48. The rear casing 48 is mainly composed of a first casing body 48A, a second casing body 48B, an anti-load side cover body 48C, and a load side cover body 48D, and is connected to the structural body 12A of the nacelle 12 via bolts 29. It is fixed. The internal space P2 of the rear casing 48 is sealed with oil seals (seal members) 71D and 71E, and a lubricant is enclosed.

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

  A plurality of (in this example, 12) inner pins 80 penetrate the external gear 76 on the same circumference together with the sliding promotion member 81. The inner pin 80 is integrated with an output flange (carrier) 82, and the output flange 82 is integrated with the output shaft 84 of the reduction gear 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 78B of the internal gear 78, and supports an output flange 82 integrated with the output shaft 84, thereby rotatably supporting one end of the output shaft 84.

  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 (FIG. 4) already described.

  Here, a configuration in the vicinity of the hollow shaft 66 that is an output shaft of the second parallel shaft speed reduction mechanism 42 and the connecting shaft 70 that is connected to the inside of the hollow shaft 66 will be described in detail.

  Referring also to FIG. 2, the hollow shaft 66 can be exposed at the one end 66 </ b> A of the hollow structure from the front-side casing 45. Specifically, the hollow shaft 66 has a hollow structure having a hollow portion 66C penetrating in the axial direction. The hollow shaft 66 is rotatably supported by the front casing 45 via a pair of seal ball bearings 88 and 90, and one end portion 66 </ b> A of the hollow structure extends further outward in the axial direction than the one seal ball bearing 88. Exist. As a result, one end portion 66 </ b> A of the hollow shaft 66 can be exposed outside the front casing 45.

  In this embodiment, one end portion 66A of the hollow shaft 66 is actually closed by a dust-proof transparent lid member 67. However, the lid member 67 can be easily removed by removing the bolt 68, and the one end portion 66A can be easily exposed. Further, “exposed” does not require that the one end portion 66A protrudes outside the casing side surface, and the one end portion 66A may be located inside the casing side surface.

  A connecting shaft (power transmission member) 70 to the next stage is connected inside the hollow shaft 66.

  Specifically, the connecting shaft 70 includes a first connecting portion 70A connected to the hollow shaft 66 in the vicinity of one end portion 66A thereof, and is connected to the inside of the hollow shaft 66 at the first connecting portion 70A. In the present embodiment, the first connecting portion 70 </ b> A is provided inside the one end portion 66 </ b> A of the hollow shaft 66 via the bush 63. The connecting shaft 70 is a portion protruding from the other end 66B of the hollow shaft 66, and connects the input shaft 73 and the joint ring member 79 of the above-described eccentric oscillating planetary gear speed reduction mechanism 44, which is the next stage member. Are connected through.

  First, the structure in which the connecting shaft 70 is connected to the inside of the hollow shaft 66 will be described in detail.

  In this embodiment, the connecting shaft 70 is not directly connected to the hollow shaft 66 itself, but a bush 63 is interposed therebetween. That is, in the present embodiment, a bush 63 (cylindrical member) that engages with the inner periphery of the hollow shaft 66 via the key 69 in the rotation direction is provided, and the connecting shaft 70 is connected to the bush 63, The hollow shaft 66 is connected to the inside. Specifically, the connecting shaft 70 and the bush 63 are integrated as a single assembly A 1 including a retaining ring 77, and are engaged with the hollow shaft 66 by a key 69. That is, the connection between the bush 63 and the hollow shaft 66 is a “gap fitting” using the key 69.

  On the other hand, the connection between the first connecting portion 70A of the connecting shaft 70 and the bush 63 (integrated with the hollow shaft 66) is performed by “an interference fit”. The interference fit is realized by press fitting or shrink fitting. This interference fit is an interference fit in which relative slip occurs between the connecting shaft 70 and the hollow shaft 66 within the range of elastic deformation when a torque of the first predetermined value S1 or more is applied to the first connecting portion 70A. It is said that.

  The first predetermined value S1 is set to a value obtained by converting a predetermined load in a range larger than the rated torque equivalent load of the motor 22 and smaller than the extreme load into a load of the first connecting portion 70A. The rated torque equivalent load means a load applied to the output shaft 84 when the connected motor 22 outputs the rated torque. The extreme load is a load that is not destroyed even if it is applied only once to the output shaft 84 during the service life (20 years in the case of a reduction gear of a wind power generation facility). In this embodiment, the extreme load is slightly more than twice the load equivalent to the rated output torque (although the width is slightly larger).

  In this embodiment, the first connecting portion 70A of the connecting shaft 70 is a “fragile portion that easily undergoes a specific change in transmission of power compared to other members constituting the power transmission system” according to the present invention. Yes. Here, “specific change” means “when a torque greater than a specific torque (in this example, the first predetermined value S1 or more) is applied to the power transmission member, the applied torque can be transmitted as it is. It means "change that will disappear". In this embodiment, when a torque greater than or equal to the first predetermined value S1 is applied to the connecting shaft 70 due to the setting of the interference fit, a “relative slip” occurs in the first connecting portion 70A, and the torque cannot be transmitted as it is. . Therefore, this “relative slip” corresponds to a specific change, and the first connecting portion 70A in which the relative slip is likely to occur (compared to other members of the power transmission system) becomes the “fragile portion”. It corresponds. In other words, since the first connecting portion 70A of the connecting shaft 70 constitutes the “fragile portion” according to the present invention, the connecting shaft 70 has a specific change (with the hollow shaft 66 and It can also be understood that the relative slippage is likely to occur.

  In the present embodiment, a detection mechanism D1 capable of detecting from the outside that the specific change (relative slip) has occurred is provided. Specifically, in the detection mechanism D1, the end surface 63A of the bush 63 integrated with the hollow shaft 66 and the end surface 70D of the connecting shaft 70 are arranged in substantially the same plane, and straddle both end surfaces 63A, 70D. It is composed of, for example, red markings (continuous marks) drawn in the radial direction (or a sharp line with a sharp point, a thin copper wire, etc. straddling both end faces 63A and 70D. It may be the same). By making the marking visible through the transparent lid member 67, when a specific change (relative slip) occurs between the hollow shaft 66 (bush 63) and the connecting shaft 70, the marking is shifted, It can be visually recognized from the outside that the specific change has occurred.

  Next, a connection configuration between the connection shaft 70 and the input shaft 73 of the planetary gear speed reduction mechanism 44, which is the next stage member, will be described.

  The connecting shaft 70 includes a second connecting portion 70B at the end of the portion protruding from the other end 66B of the hollow shaft 66, and the planetary gear speed reduction mechanism 44, which is a member of the next stage, is provided via the second connecting portion 70B. The input shaft 73 is connected. Specifically, this connection is made via a joint ring member 79. The joint ring member 79 includes an inner spline 79A. The second connecting portion 70B includes an outer spline 70B1 and is engaged with a portion 79A1 of the inner spline 79A of the joint ring member 79 on the axial hollow shaft 66 side. On the other hand, an outer spline 73A is formed at the end of the input shaft 73 of the eccentric swing planetary gear speed reduction mechanism 44 at the next stage, and the outer spline 73A of the input shaft 73 is the inner spline 79A of the joint ring member 79. Is engaged with the other part 79A2 on the side opposite to the hollow shaft 66. Therefore, in this embodiment, the power is transmitted as it is through the joint ring member 79 between the second connecting portion 70 </ b> B of the connecting shaft 70 and the input shaft 73. That is, it is not regarded as a “fragile part”.

  In addition, the axial direction length of the joint ring member 79 is set long, and the entire length of the connecting shaft 70 is configured to be wrapped by the hollow shaft 66 and the joint ring member 79.

  In this embodiment, the outer diameter of the first connecting portion 70A (with the hollow shaft 66) of the connecting shaft 70 is d1, and the outer diameter of the second connecting portion 70B (with the next-stage member) is d2. is there. Further, the diameter of the intermediate portion 70 </ b> C constituting between the connecting portion with the hollow shaft 66 and the connecting portion with the next stage is d <b> 3, and d <b> 2> d <b> 1> d <b> 3. That is, an intermediate portion 70C between the first connecting portion 70A and the second connecting portion 70B is a diameter d3 smaller than the outer diameters d1 and d2 of the connecting portions 70A and 70B.

  Further, the space P3 in the hollow portion 66C of the hollow shaft 66 is separated from the space P1 in which the lubricant in the front casing 45 of the reduction gear G1 is sealed by oil seals 71B and 71C (seal members). ing. That is, in the present embodiment, the hollow shaft 66 passes through the front casing 45. Oil seals 71B and 71C are disposed between the hollow shaft 66 and the front casing 45, and the lubricant in the space P1 of the front casing 45 cannot enter the space P3 in the hollow shaft 66. . An oil seal 71D is also disposed between the rear casing 48 and the bush 72 that is press-fitted into the outer periphery of the input shaft 73 protruding from the rear casing 48. The lubricant in the rear casing 48 is It is configured such that it cannot enter the space P4 in the joint ring member 79. After all, the space P3 in the hollow shaft 66 and the space P4 in the joint ring member 79 are completely separated from the spaces P1 and P2 in which the lubricant of the reduction gear G1 is sealed by the oil seals 71B, 71C, and 71D. Thus, the lubricant of the reduction gear G1 does not adhere to the connecting shaft 70.

  In this embodiment, the hollow shaft 66 has an axial dimension L1. On the other hand, the connecting shaft 70 is connected to the vicinity of one end portion 66A of the hollow shaft 66, and is an input shaft of the planetary gear speed reduction mechanism 44 that is a member of the next stage at a portion protruding from the other end portion 66B of the hollow shaft 66. 73. Therefore, the connecting shaft 70 has a considerably long total length L2. Further, as described above, the connecting shaft 70 has the outer diameter d3 of the intermediate portion 70C between the first connecting portion 70A and the second connecting portion 70B smaller than the outer diameters d1 and d2 at the connecting portions 70A and 70B. It is said that.

  The reason why the connecting shaft 70 has such a configuration is that the connecting shaft 70 is intended to be twisted and deformed by a predetermined amount of twist deformation (rotational angle phase difference) in the rotational direction under a predetermined condition. is there.

  Since this configuration is not publicly known, it will be described in a little more detail.

  In the connecting shaft 70 according to this embodiment, when the load acting on the output pinion 24 becomes equal to or greater than the second predetermined value S2, which is smaller than the load corresponding to the first predetermined value S1, each of the reduction gears G1 to G4. The output pinion 24 is twisted and deformed in the rotational direction by a predetermined angle or more corresponding to each “difference in backlash” of the output pinion 24 with respect to the turning gear 28.

  Here, “the second predetermined value S2” when “the load acting on the output pinion 24 becomes equal to or larger than the second predetermined value S2 smaller than the load corresponding to the first predetermined value S1” is “the strong wind load is When applied, before each specific change (relative slip) occurs in the first connecting portion 70A, each reduction gear is equally loaded, so that the load does not concentrate only on the specific reduction gear. Determined.

  Specifically, “a load equivalent to the rated torque applied to the output pinion 24 when the motor 22 outputs the rated torque is one index. Note that the second predetermined value S2 may be low, but too low. If the torsional deformation is generated from a low level, the responsiveness when driven by the motor 22 is deteriorated and it is difficult to secure the necessary strength. Therefore, the motor 22 is subjected to fatigue equivalent load (about half of the rated torque of the motor). ), The value applied to the output pinion 24 when the torque is output is substantially the lower limit.

  The “backlash difference” is ideally the difference between the backlash amount of the speed reducer with the smallest backlash between the swivel gear 28 and the output pinion 24 and the backlash amount of the speed reducer with the largest backlash. is there. More specifically, “After the nacelle 12 is rotated by the wind load, the backlash of the reduction gear with the minimum backlash is clogged (becomes zero), and the backlash of the reduction gear with the maximum backlash is reduced. The angle at which the output pinion 24 of the reduction gear having the maximum backlash rotates until it disappears ”.

  However, if the connecting shaft 70 of the speed reducer with the smallest backlash is twisted, and the output pinion 24 of the speed reducer with the next smallest backlash meshes with the swivel gear 28, the even distribution effect by the two speed reducers can be obtained. Further, when the connecting shafts 70 of the two reduction gears are twisted, and the output pinion 24 of the next reduction gear meshes with the swivel gear 28, a further equal distribution effect is obtained. Then, after all, the “backlash difference” may be regarded as a difference in backlash between any two reduction gears.

  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) depending on the position of the target connecting shaft 70 on the power transmission system. It is. For example, in this embodiment, since the speed increasing ratio of the planetary gear speed reduction mechanism 44 as viewed from the output pinion 24 is 43, the angle is 43 times.

  The tap hole 70T formed in the end surface 70D of the connecting shaft 70 in FIGS. 1 to 3 is for screwing a screw of a drawing jig when the connecting shaft 70 is difficult to pull out. is there.

  Next, the operation of the reduction gear G1 will be described.

  Referring to FIG. 1, the rotation of the motor shaft 46 of the motor 22 is first-stage decelerated by the engagement of the hypoid pinion 47 and the hypoid gear 50 of the orthogonal gear reduction mechanism 40, and then the first parallel axis reduction mechanism 41 and the second parallel axis It is transmitted to the hollow shaft 66 via the speed reduction mechanism 42.

  The rotation of the hollow shaft 66 is transmitted to the input shaft 73 of the eccentric oscillating planetary gear reduction mechanism 44 via the connecting shaft 70. The operation of this part will be described in detail later.

  When the input shaft 73 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). As a result, every time the input shaft 73 rotates once, the external gear 76 swings once, and the phase shifts by one tooth (by the number of teeth difference) with respect to the internal gear 78. (Rotation component is generated).

  By taking out the rotation component from the output shaft 84 via the sliding promotion member 81, 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. The output pinion 24 meshes with the swivel gear 28, and the swivel gear 28 is fixed to the cylindrical column 11. Therefore, due to the reaction, the output pinion 24 revolves around the center 36 of the turning gear 28 while rotating, and the nacelle 12 rotates in a horizontal direction (turning) with respect to the axis 36 of the turning gear 28 on the cylindrical column 11 side. )

  Here, for example, it is assumed that a “wind load” is generated in which the nacelle 12 is forced to turn due to a gust of wind or the like. This wind load drives the yaw drive system 14 from the reverse and tries to rotate the output pinion 24 of the reduction gear G1 via the swivel gear 28. If the wind load is a torque within a normally assumed range (smaller than the first predetermined value S1), no relative slip occurs between the connecting shaft 70 and the hollow shaft 66 (the bush 63 integrated with the connecting shaft 70). (There will be no specific change). That is, the torque is further transmitted to the second parallel shaft reduction mechanism 42 side of the reduction gear G1 through the hollow shaft 66 as it is, and finally received by a brake device (not shown) attached to the motor 22. As a result, the movement of the nacelle 12 due to the wind is reliably braked. Of course, no abnormality occurs in each part of the yaw drive system 14 including the reduction gear G1.

  However, since the wind power generation facility is a facility installed in a natural environment, it sometimes receives a very strong turbulent wind or gust. In general, when a strong wind is blowing, the rotating elements of the reduction gears G1 to G4 are made non-rotatable by a brake device provided on the non-load side of the motor 22, and the nacelle 12 turns uncontrolled by the strong wind. To prevent it. Therefore, each component of the yaw drive system 14 including the speed reducer G1 receives this strong wind load properly almost in a stopped state, and is placed under a very severe condition.

  Therefore, if no measures are taken, there is a possibility that a portion that cannot withstand the wind load in any part of the yaw drive system 14 including the speed reducer G1 may be plastically deformed. In this case, when the plastic deformation portion is, for example, the swivel gear 28 of the yaw drive system 14, the restoration work becomes very large and enormous costs are required.

  However, according to the present embodiment, the connection shaft 70 (the first connection portion 70A thereof) is intentionally compared with other members constituting the power transmission system in a specific change (hollow shaft 66) when transmitting power. Relative slippage) is a “fragile part”. Therefore, when the wind load is applied from the output pinion 24 side and the torque related to the first connecting portion 70A of the connecting shaft 70 exceeds the first predetermined value S1, (before other members cause any change in power transmission) In the first connecting portion 70A of the connecting shaft 70, “relative slip with the hollow shaft 66” occurs as a specific change between the first connecting portion 70A and the hollow shaft 66.

  Then, since the torque greater than or equal to the first predetermined value S1 is not transmitted in the first connecting portion 70A, the torque greater than or equal to the torque corresponding to the first predetermined value S1 is automatically transmitted to all components of the yaw drive system 14. Is prevented from being applied.

  That is, in the present embodiment, when the wind load is excessive, “relative slip with the hollow shaft 66” occurs as a specific change in the connecting shaft 70 first in each member of the power transmission system. Therefore, so-called serious damage does not occur, and first, maintenance is easy in this respect.

  In the present embodiment, even when it is detected that a specific change has occurred, when the excessive wind load is eliminated (because an interference fit in elastic deformation is employed), in many cases, again The connection shaft 70 can continue to be used (as before certain changes have occurred). However, when such a specific change occurs (or when the specific change occurs several times), it is considered that the connecting shaft 70 is showing some signs of abnormality. It is preferable to inspect the connecting shaft 70.

  In this case, in this embodiment, as shown in FIG. 3, the hollow member 66 </ b> A of the hollow structure of the hollow shaft 66 is exposed to the outside of the front-side casing 45 simply by removing the cover member 67 by removing the bolt 68. Is possible. Further, the connecting shaft 70 can be taken out of the front casing 45 from the one end 66A (while the speed reducer G1 itself is installed on the nacelle 12 of the wind power generation facility 10). That is, the connecting shaft 70 can be taken out without disassembling the front casing 45 and the rear casing 48 at all.

  If there is no problem as a result of the inspection, if an abnormality is found as it is with the inspected connecting shaft 70, a new replacement part can be assembled from the exposed end portion 66A of the hollow structure of the hollow shaft 66. For this reason, maintenance is also simple in this respect.

  In addition to these basic functions and effects, in the above-described embodiment, as described above, in particular, the first connecting portion 70A with the hollow shaft 66 is a fragile portion, and as a specific change, the connecting shaft 70 and the hollow shaft Since the configuration in which relative slip to 66 occurs is adopted, not only can each member of the yaw drive system 14 be protected from excessive torque, but also the connecting shaft 70 itself (having a weak portion and Even if a specific change occurs, it does not necessarily have to be replaced immediately.

  In the above embodiment, since the first connecting portion 70A between the connecting shaft 70 and the hollow shaft 66 is connected by an interference fit, each elastic deformation of the connection shaft 70 and the hollow shaft 66 due to the interference fit is prevented. By adopting such a configuration, it is possible to maintain the transmission of torque corresponding to the first predetermined value S1 in the first connecting portion 70A even during the slipping. Therefore, for example, the nacelle 12 fluctuates in a disorderly manner compared to a method in which the transmission of power in the reduction gear is completely cut off by simply disengaging the clutch or the like (the state in which the direction is not determined while leaving to the wind without the function of the brake) Can be further prevented.

  In the above embodiment, the bush (tubular member) 63 that engages with the inner periphery of the hollow shaft 66 in the rotational direction is provided, and the connecting shaft 70 is connected to the bush 63 by an interference fit. . This provides many benefits. That is, if the connection shaft 70 is to be directly connected to the inside of the hollow shaft 66 by interference fitting, the connection shaft 70 once taken out from the hollow shaft 66 is inserted into the hollow shaft 66 again and connected. When repairing, assembly is performed while performing connection by interference fitting, which entails great difficulty. However, since the connecting shaft 70 according to the present embodiment merely engages the joint ring member 79 and the bush 63 in the rotational direction by splines in the second connecting portion 70B, for example, when taking out the connecting shaft 70 The connecting shaft 70 can be easily removed by pulling out the “assembly A1 of the connecting shaft 70 and the bush 63” together with the retaining ring 77 (see FIG. 3).

  As a result of pulling out and inspecting, even when the connecting shaft 70 is not particularly abnormal and reassembled, or when any abnormality is found and replaced with a new one, the inside of the hollow shaft 66 assembled to the front casing 45 In addition, the assembly A1 may be assembled from the one end 66A of the hollow structure of the hollow shaft 66 until it is locked by the retaining ring 77 again (with a clearance fit) using the key 69. Therefore, reassembly and replacement are very easy. Above all, since the connecting shaft 70 can be manufactured in advance “with an appropriate interference fit” in the factory, the management of the first predetermined value S1 (management of the torque that starts to slide) can be realized extremely accurately.

  Note that the configuration in which the assembly A1 is inserted into the hollow shaft 66 with a clearance fit may cause fretting. However, in the unlikely event that fretting occurs between the hollow shaft 66 and the bush 63, the assembly A1 is pulled out. Even if it becomes difficult, in this embodiment, the connecting shaft 70 can be easily pulled out using a jig (not shown) using the tap hole 70T formed at the end of the connecting shaft 70.

  Further, in the above-described embodiment, the connecting shaft 70 is connected to the vicinity of the one end portion 66A of the hollow shaft 66, and the eccentric rocking type planetary gear speed reduction mechanism at the portion protruding from the other end portion 66B of the hollow shaft 66. 44 input shafts (next stage members) 73 are connected. For this reason, the full length L2 of the connecting shaft 70 can be secured longer, and a load distribution effect utilizing "twist deformation" can be obtained.

  Since this effect is not publicly known, it will be described in a little more detail.

  As described above, when a strong wind is blowing, generally, each rotating element of the yaw drive system 14 is made non-rotatable by a brake device (not shown) provided on the non-load side of the motor 22 and the nacelle 12 is strong. This prevents the wind from turning in an uncontrolled state.

  Therefore, in the conventional yaw drive system, the reduction gear (first reduction gear G1 for the sake of convenience) in which the backlash of the drive system is initially packed by moving the nacelle 12 is “only one”. In order to prevent further rotation of the swivel gear 28, the output pinions 24 of the other reduction gears G <b> 2 to G <b> 4 remain in a state where backlash with the swirl gear 28 is not filled, and the swivel gear 28. There was a problem that the wind load from the side could not be received.

  However, according to the present embodiment, first, when a load greater than or equal to the second predetermined value S2 is applied from the swivel gear 28 to the output pinion 24 of the first reduction gear G1 first packed with backlash, the connection is caused by this load. The shaft 70 is twisted and deformed. For this reason, the output pinion 24 rotates as it is due to the torsional deformation of the connecting shaft 70 (although the rotation of the rotating elements of the speed reducers G1 to G4 is basically stopped by the brake device). The swivel gear 28 can also follow the rotation and continue to rotate.

  As a result, a part of the load from the swivel gear 28 side that is conventionally applied only to the first reduction gear G1 is also distributed to the second reduction gear G2. Since the second reduction gear G2 and the third reduction gear G3 can also be twisted, finally the respective connecting shafts 70 of the reduction gears G1 to G4 have substantially the same reaction force. The torsional deformation at the connecting shaft 70 of each of the reduction gears G1 to G4 is balanced so as to be in charge.

  If this is necessary, for example, when the yaw drive system 14 is configured by four reduction gears G1 to G4 as in the present embodiment, the wind load is substantially reduced (compared to the conventional case). This means that it is possible to obtain the same effect as that reduced to ¼. In other words, the wind load that causes the connecting shaft 70 and the hollow shaft 66 to start relative rotation (wind load related to the determination of the first predetermined value S1) can be increased almost four times. .

  However, in the present invention, the configuration of obtaining the “load equidistant effect” by actively utilizing the “twist deformation” of the power transmission member is not necessarily essential. If this configuration is not adopted, the phenomenon that only the wind load applied to the specific speed reducer quickly exceeds the first predetermined value and slipping easily occurs. For example, in the above embodiment, the first connection Since the slippage occurs in the part 70A, the wind load is automatically applied to the reduction gears that have the second largest backlash (after that, the third ...), and as a result, all the reduction gears are obtained. At the time of slipping, a load equalizing effect is obtained.

  In the present embodiment, the connecting shaft 70 has an outer diameter d3 of the intermediate portion 70C between the first connecting portion 70A and the second connecting portion 70B smaller than the outer diameters d1 and d2 at the connecting portions 70A and 70B. It is said that. For this reason, even with the same overall length L2, the above-described twist deformation can be ensured to a greater extent, and as a result, the overall reduction gear G1 can be reduced in size. In the unlikely event that the connecting shaft 70 breaks, the remaining portion of the connecting shaft 70 remaining on the input shaft 73 side (by holding the intermediate portion 70C having a small diameter with an appropriate holding jig) It is also possible to pull it up with a not shown).

  Further, in the present embodiment, since the detection mechanism D1 that can detect from the outside that a specific change (relative slip) has occurred is provided, whether or not the specific change has occurred is disassembled in the front casing 45. It is possible to confirm without doing. Specifically, whether or not relative slip has occurred is determined by straddling the end surface 63A of the bush 63 integrated with the hollow shaft 66 on the upper part of the reduction gear G1 and the end surface 70D of the connecting shaft 70 in the radial direction. It can be confirmed by visually confirming whether or not there is a deviation in the red marking (continuous mark) drawn. If it can be confirmed during maintenance that the connecting shaft 70 has not undergone a specific change by this visual check, the operation of taking out and inspecting the connecting shaft 70 can be omitted. This effect is actually very large in consideration of the situation where the maintenance of the reduction gear G1 must be performed in a very narrow space of the nacelle 12.

  In the present embodiment, the one end portion 66A of the hollow shaft 66 is closed by the lid member 67, so that it is possible to maintain the ease of visual recognition while preventing dust and the like from entering the hollow shaft 66. Can do. In particular, in this embodiment, since the lid member 67 is made of a transparent member, the presence or absence of a specific change can be confirmed without removing the lid member 67, so that the convenience is particularly high.

  Furthermore, in this embodiment, the space P3 of the hollow shaft 66 and the space P4 of the joint ring member 79 are separated from the spaces P1 and P2 in which the lubricant of the reduction gear G1 is sealed by the oil seals 71B, 71B, and 71D. Because of the above configuration, there is no possibility that the lubricant will drip when the connecting shaft 70 is pulled up.

  In the above embodiment, the reduction gear G1 (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 deceleration mechanism of the yaw deceleration system is not particularly limited to the above configuration.

  5 and 6, a configuration example of a reduction gear G1a adopting a worm reduction mechanism 110 instead 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. Indicates. The other three reduction gears (not shown) have the same configuration as the reduction gear G1a.

  In this embodiment, the motor is mounted in a direction perpendicular to the paper surface. However, in FIG. 5, 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 shaft 66 of the second parallel axis reduction mechanism 42 in the previous embodiment. The connection shaft 70 is connected to the inside of the worm output shaft 120 with the same connection configuration as in the previous embodiment. Further, the connecting shaft 70 is connected to the rotating shaft 133 of the sun gear 132 of the first simple planetary gear speed reduction mechanism 130 which is the next stage member with the same configuration as the connecting shaft 70 of the previous embodiment.

  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.

  A second simple planetary gear reduction mechanism 140 is connected to the subsequent stage of the first simple planetary gear reduction mechanism 130. 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.

  In this embodiment, there is no oil seal corresponding to the oil seal 71D of the previous embodiment, and the interior of the hollow shaft 66 is not isolated from the space P5 in which the lubricant is enclosed.

  Also in this embodiment, since the worm output shaft 120 and the connecting shaft 70 have the same configuration as the hollow output shaft 66 and the connecting shaft 70 of the previous embodiment, the same effects as the previous embodiment are obtained. It is done. Accordingly, parts that are substantially the same as those of the previous embodiment are denoted by the same reference numerals as those of the previous embodiment, and redundant description is omitted.

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

  7 and 8 show an example of still another embodiment of the present invention. The basic structure of the reduction gear G1b is the same as that of the reduction gear G1 according to the embodiment shown in FIGS.

  The difference is that the bush 63 is interposed between the hollow shaft 66 and the connecting shaft 70 in the previous embodiment. However, in this embodiment, the connecting shaft 70 is directly connected to the key 169 inside the hollow shaft 66. Are connected. Since the retaining ring (77) is also unnecessary, it is omitted.

  Since the first connecting portion 70A with the hollow shaft 66 is connected with the key 169, the connecting shaft 70 is inserted into and removed from the one end portion 66A of the hollow shaft 66 by “gap fitting” as in the previous embodiment. It is easy. However, since it is connected by the key 169, even if an excessive wind load is applied, relative slip does not occur in this portion. That is, in this embodiment, 70 A of 1st connection parts do not comprise the weak part.

  Instead, in this embodiment, the connecting shaft 70 has the same outer diameter of the first connecting portion 70A with the hollow shaft 66 as that of the previous embodiment d1, and the outer diameter of the second connecting portion 70B with the next stage is also earlier. While d2 is the same as that of the embodiment, the outer diameter of the intermediate portion 70Ca between the first connection portion 70A and the second connection portion 70B is d3a, which is slightly smaller than the outer diameter d3 of the previous embodiment. This portion, that is, the intermediate portion 70Ca itself of the first and second connecting portions 70A and 70B is a “fragile portion”. That is, when an excessive wind load is input, the intermediate portion 70Ca of the connecting shaft 70 itself is configured to be plastically deformed. In other words, in this embodiment, the specific change of the connecting shaft (power transmission member) 70 is plastic deformation of the connecting shaft 70 itself.

  Also in this embodiment, whether or not a specific change has occurred can be confirmed by the same configuration as the previous embodiment. However, unlike the previous embodiment, when it is confirmed that a specific change has occurred, the connecting shaft 70 is immediately replaced.

  As described above, the connecting shaft 70 can be taken out, reassembled, or replaced very easily. Moreover, as a practical matter, it is not so often that the wind load is applied so that the connecting shaft 70 is plastically deformed. On the other hand, it is possible to assume that the connecting shaft 70 is the connecting shaft 70 if plastically deformed. Since it is possible to stock in advance, there is not much trouble in practical use, and the embodiment shown in FIGS. 1 to 3 is particularly effective in reducing the initial cost (construction cost of wind power generation equipment). Excellent compared to.

  Since the other points are the same as those of the previous embodiment shown in FIGS. 1 to 3, the same or similar parts in the drawings are designated by the same reference numerals, and redundant description is omitted.

  As described above, in the present invention, there is no particular limitation on which part of the power transmission member is used as the weakened part. For example, it is good also considering a 2nd connection part as a weak part instead of a 1st connection part or in addition to a 1st connection part. Moreover, when connecting the 1st connection part or the 2nd connection part with a key, the method of using the thin key which is easy to carry out plastic deformation is also considered. The specific change in this case is the plastic deformation of the key.

  Thus, the formation of the fragile portion is not necessarily limited to only one place or only one type. If the structure for making the fragile part is different, the specific change that appears also changes, so in order to ensure that a specific change in any power transmission member occurs prior to damage to other parts, etc. It is effective to have a vulnerable part. In this case, the specific change may be set to occur at the same wind load, or may be deviated slightly. For example, in the configuration of FIGS. 1 to 3, in addition to the formation of the first fragile portion by the interference fitting of the first connecting portion, the strength of the intermediate portion of the connecting portion is intentionally set lower to form the second fragile portion. If the relative slip at the first connecting portion does not function properly due to some cause such as adhesion, the connecting shaft itself is plastically deformed at a slightly higher set value than that. A configuration having a stage configuration may be employed.

  Further, as illustrated, the configuration of the speed reduction mechanism of the speed reduction device is not particularly limited. For example, a plurality of eccentric body shafts having eccentric bodies are provided at positions offset from the axis of the internal gear, and each eccentric body shaft is provided. An eccentric oscillating planetary gear reduction mechanism called a so-called sort type that oscillates the external gear by rotating the eccentric members synchronously may be adopted. Further, a bevel reduction mechanism may be adopted instead of the hypoid reduction mechanism. Of course, it is also possible to combine these reduction mechanisms.

  The present invention can be similarly applied to a reduction device for pitch drive in addition to a reduction device for yaw drive.

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 shaft 70 ... Connecting shaft (power transmission member)
70A ... 1st connection part 70B ... 2nd connection part 70C ... Intermediate | middle part 73 ... Input shaft 76 ... External gear 78 ... Internal gear 84 ... Output shaft G1-G4 ... Reduction gear

Claims (10)

A reduction gear used for wind power generation equipment,
As part of the power transmission system, it has a hollow hollow shaft,
A power transmission member to the next stage is connected to the inside of the hollow shaft,
The hollow shaft is capable of exposing one end of the hollow structure from the casing,
The power transmission member is a fragile part that easily undergoes a specific change in power transmission compared to other members constituting the power transmission system, and
The power transmission member is capable of being taken out of the casing from the one end of the hollow shaft while the speed reducer itself is installed in the wind power generation equipment. . In claim 1,
In the power transmission member, a connecting portion with the hollow shaft or a member integrated with the hollow shaft is the fragile portion,
The specific change is a relative slip between the power transmission member and the hollow shaft or a member integrated with the hollow shaft. A reduction gear used for a wind power generation facility. In claim 2,
The speed reducing device used for wind power generation equipment, wherein the connecting portion is connected by an interference fit. In claim 2 or 3,
And a cylindrical member that engages with the inner periphery of the hollow shaft in the rotational direction.
The power transmission member is connected to the tubular member by an interference fit. A reduction gear used for a wind power generation facility. In any one of Claims 1-4,
The speed change device used for wind power generation equipment, wherein the specific change of the power transmission member is plastic deformation of the power transmission member itself. In any one of Claims 1-5,
The power transmission member is connected to the vicinity of the one end portion of the hollow shaft, and is connected to the next stage at a portion protruding from the other end portion of the hollow shaft. To reduce the speed. In claim 6,
The power transmission member is characterized in that the outer diameter between the connecting portion with the hollow shaft and the connecting portion with the next stage is smaller than the outer diameter at each connecting portion. Reducer to use for. In any one of Claims 1-7,
Furthermore, the reduction mechanism used for the wind power generation facility characterized by including the detection mechanism which can detect from the outside that the said specific change occurred. In any one of Claims 1-8,
The speed reducer used for wind power generation equipment, wherein the one end of the hollow shaft is closed by a lid member. In any one of Claims 1-9,
The inside of the hollow shaft is isolated from a space in which the lubricant of the reduction gear is enclosed by a seal member. A reduction gear used for wind power generation equipment.

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