JP2012031827A - Reduction gear apparatus of wind power generation equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase the strength of a reduction gear to be mounted between first and second members of wind power generation equipment.SOLUTION: The reduction gear G1(to G4) of the wind power generation equipment is mounted between the lower plate (first member) 70 and the upper plate (second member) 72 of the wind power generation equipment which are arranged with a distance L1 therebetween. The load side of a low-speed side casing body 48 of the reduction gear G1 is supported by the lower plate 70, and the counter-load side is supported by the upper plate 72, respectively. A counter load side bearing 76 out of bearings 74, 76 for supporting the output shaft 66 of the reduction gear G1 is arranged at a position corresponding the upper plate (the second member) 72 (or at the position on the counter load side farther from the position corresponding thereto) in the axial direction X of the output shaft 66.

Description

  The present invention relates to a reduction device for a wind power generation facility, and more particularly, to a reduction device for a wind power generation facility that is mounted between a first member and a second member of a wind power generation facility.

  Patent Document 1 discloses, for example, a reduction gear used for yaw control of a nacelle (power generation chamber) of a wind power generation facility as shown in FIG.

  The reduction gear Go is attached to the floor surface 1 of a nacelle (the whole is not shown). The floor surface 1 is configured as a part of a huge cast member integrally formed with a hollow portion So. In other words, the speed reduction device Go is “a part of a huge casting member” and is attached in a state of straddling both the lower plate 2 and the upper plate 3 facing each other at a distance Lo. become.

  The lower plate 2 has a lower through hole 2A, and the upper plate 3 has an upper through hole 3A. The reduction gear Go has a load side of the casing 4 fitted and supported in the lower through hole 2A of the lower plate 2 and a non-load side fitted in the upper through hole 3A of the upper plate 3. The casing 4 of the reduction gear Go includes a flange portion 4A, and the flange portion 4A is fixed to the upper plate 3 by bolts 5. The thickness Do of the casing 4 is substantially constant at each part of the casing 4.

  The speed reduction device Go includes a speed reduction mechanism 6 disposed substantially at the center between the lower plate 2 and the upper plate 3, and includes an output shaft 7 extending downward. The load side of the output shaft 7 is supported by a load side bearing 8. The non-load side of the output shaft 7 is supported by a non-load side bearing 9 via a flange body 7A integrated with the output shaft 7. The anti-load side bearing 9 is disposed at a substantially central position between the lower plate 2 and the upper plate 3. The bearing span of the load side bearing 8 and the anti-load side bearing 9 is Lb.

Japanese Patent Laying-Open No. 2008-89144 (FIG. 2)

  Wind turbines are not always installed only in mild weather, especially in recent years where turbulent winds occur in complex terrain, and sometimes large wind loads such as typhoons and hurricanes. There are an increasing number of cases in which it is necessary to install in places where it takes. In a wind power generation facility installed in such a place, a very large load may be input from the output side (wind turbine blade side not shown) of the reduction gear, so that the strength of the reduction gear is further increased. There is a request to want. In addition, even if it is a wind power generation facility installed in a place where the weather is mild, there is a need to increase the strength of the wind power generation facility considering that it is a natural speed reducer.

  However, in the speed reducer of the wind power generation facility, there is a specific problem that this “enhancement of strength” is extremely difficult in design. That is, even if there is a request to increase the strength of the speed reduction device Go, the size of the speed reduction device Go is restricted by the size of the lower through hole 2A and the upper through hole 3A for mounting the speed reduction device Go. It must be a designed design.

  In particular, in the structure disclosed in Patent Document 1, the speed reduction mechanism 6 is disposed at substantially the center between the lower plate 2 and the upper plate 3, and the anti-load side bearing 9 that supports the output shaft 7 is also connected to the lower plate 2 and the upper plate 3. The plate 3 was arranged at approximately the center position. In this configuration, since the reaction force of the speed reduction mechanism 6 and the anti-load side bearing 9 is received depending on “the rigidity of the central portion of the casing 4”, the thickness of the casing 4 is necessarily increased in order to improve the strength. Do must be thickened. However, when the thickness Do of the casing 4 is designed to be thicker, there is a restraining reason that “the outer diameter of the casing 4 cannot be larger than the inner diameter of the upper through-hole 3A”, so that the space in the casing 4 is reduced accordingly. Inevitably, the size of the speed reduction mechanism 6 that can be accommodated is inevitably smaller. Therefore, the actual situation is that a dilemma that the strength of the speed reduction mechanism 6 is rather lowered occurs.

  The present invention has been made to solve such a conventional problem, and further enhances the strength of the reduction gear mounted between the first member and the second member of the wind power generation facility. The challenge is to make it possible.

  The present invention is a reduction device for wind power generation equipment that is mounted across both the first member and the second member of the wind power generation equipment that are arranged at a distance, wherein the load side of the casing of the reduction gear device is the first member, The anti-load side is respectively supported by the second member, and at least a part of the anti-load side bearing among the bearings supporting the output shaft of the speed reducer corresponds to the second member in the axial direction of the output shaft. The above-mentioned problem is solved by adopting a configuration in which the position is arranged at a position on the opposite side of the load or a position opposite to the corresponding position.

  In the present invention, the strength of the speed reducer is not considered at the single level of the speed reducer, but includes the members on the wind power generation equipment side. In particular, the presence of the second member (the upper plate 3 in the above-described conventional example) located on the anti-load side is not regarded as a “restraint factor that inhibits strength enhancement”, but the strength of the second member. Is actively and rationally utilized.

  That is, according to the present invention, the bearing on the anti-load side among the bearings supporting the output shaft of the speed reducer is disposed at or corresponding to the position corresponding to the second member in the axial direction of the output shaft. It is arranged at a position further on the side opposite to the load than the position.

  Here, “at least a part of the bearing on the anti-load side is disposed at a position corresponding to the second member” means “at least a part of the outer ring position (in the axial direction of the output shaft) of the bearing on the anti-load side” Is overlapping the position of the second member (in the axial direction of the output shaft). In other words, when viewed from the radial direction of the bearing, it means that “at least a part of the outer ring of the bearing on the anti-load side overlaps the second member”. In addition, when the bearing on the non-load side does not have an outer ring, “the rolling element and the inner ring (if there is an inner ring), the wider one in the axial direction of the output shaft exists in the axial direction of the output shaft. “Position” is defined as “the position of the outer ring (in the axial direction of the output shaft) of the bearing on the anti-load side”.

  In the present invention, when at least a part of the bearing on the anti-load side is disposed at a position corresponding to the second member, the bearing on the anti-load side generates most of the reaction force against the load applied from the output shaft side ( It can be received directly from the second member located radially outward (via the casing). Therefore, the bearing on the non-load side of the output shaft can be supported with sufficiently high rigidity without increasing the thickness of the casing. Furthermore, since the distance (bearing span) from the bearing on the load side to the bearing on the anti-load side can be made larger than before, the output shaft generated by the radial load acting on the output shaft should be tilted. The bending moment can be received with a smaller reaction force, and in this respect as well, a structure that is more advantageous in terms of strength can be constructed.

  Further, in the present invention, if the bearing on the anti-load side is arranged at a position on the anti-load side further than the position corresponding to the second member, if it is in this position (the size of the through hole of the second member) Since the casing itself of the portion where the bearing is disposed can be formed in a desired size and thickness (without being constrained), sufficient strength can be ensured. In this case, the distance (bearing span) from the bearing on the load side to the bearing on the anti-load side can be further increased as compared with the case where the bearing is disposed at the corresponding position. The bending moment for tilting can be received with a smaller reaction force.

  ADVANTAGE OF THE INVENTION According to this invention, the intensity | strength of the speed reducer of the wind power generation equipment attached ranging over between the 1st member and 2nd member of a wind power generation equipment can be raised more.

FIG. 1 is an overall cross-sectional view of a reduction device for wind power generation equipment according to an example of an embodiment of the present invention. Front view of wind power generation equipment to which the speed reducer is applied The perspective view which shows typically a mode that the said speed reducer is integrated in the nacelle of the said wind power generation equipment. Schematic sectional view showing the structure of the yaw drive device of the wind power generation facility Sectional view along the VV line of FIG. Whole sectional drawing of the reduction device of the wind power generation equipment which concerns on an example of other embodiment of this invention. Sectional view along the line VII-VII in FIG. Sectional drawing of the reduction mechanism part of the reduction device of the wind power generation equipment which concerns on an example of other embodiment of this invention. Cross-sectional view of a conventional reduction device for wind power generation equipment

  Hereinafter, a reduction device 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.

  First, the outline of the wind power generation facility in which the speed reducer is incorporated will be described.

  With reference to FIGS. 2 and 3, the wind power generation facility 10 includes a nacelle (power generation chamber) 12 at the uppermost portion of the cylindrical support 11. The nacelle 12 includes a yaw driving device 14 and a pitch driving device 16. The yaw driving device 14 is for controlling the turning angle of the entire nacelle 12 with respect to the cylindrical column 11, and the pitch driving device 16 is for controlling the pitch angle of the three windmill blades 20 attached to the nose cone 18. belongs to.

  In this embodiment, since the present invention is applied to the yaw driving device 14, the yaw driving device 14 will be described here.

  The yaw driving device 14 includes four reduction gears G1 to G4 with a motor 22 and an output pinion 24, and one turning internal gear 28 that meshes with each output pinion 24 (note that the turning gear 14 is used for turning). There is also a type of yaw drive device that includes an external gear (not shown) as a gear and externally meshes the output pinion 24 with the external gear). Each reduction gear G1-G4 is being fixed to the predetermined position by the side of the main body of nacelle 12, respectively. Referring also to FIG. 4, the turning internal gear 28 with which the output pinions 24 of the reduction gears G <b> 1 to G <b> 4 are meshed is fixed to the cylindrical column 11 side, and the inner ring of the yaw bearing 30 is Is configured. The outer ring 30 </ b> A of the yaw bearing 30 is fixed to the floor (main body) 12 </ b> A side of the nacelle 12. In addition, the code | symbol 25 of FIG.

  With this configuration, when the output pinions 24 are simultaneously rotated by the motors 22 of the reduction gears G1 to G4, the output pinions 24 mesh with the internal gears 28 while being centered on the internal gear 28 (see FIG. 3). Revolve against. As a result, the entire nacelle 12 can be swung around the center 36 of the internal gear 28 fixed to the cylindrical column 11. 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 have the same configuration, the speed reducer G1 will be described here.

  Referring to FIGS. 1 and 4, the reduction gear G1 includes a motor Ca, a hypoid orthogonal gear mechanism 40, a parallel shaft gear mechanism 42, and a swinging intermeshing planetary gear mechanism 44 in this order on a power transmission path. Is placed inside. In the present embodiment, the casing Ca is divided into several casing bodies, and among these, the entire reduction gear G1 is attached to the floor surface 12A of the nacelle 12 via a low-speed casing body 48 (described later).

  Hereinafter, the configuration on the power transmission path will be briefly described with the action.

  The rotation of the motor shaft 22 </ b> A of the motor 22 is decelerated by the hypoid orthogonal gear mechanism 40, the rotation direction is changed to a right angle direction, and the rotation is further decelerated by the parallel shaft gear mechanism 42. The output of the parallel shaft gear mechanism 42 is extracted from the hollow shaft 50 and transmitted to the joint shaft 52. The joint shaft 52 is press-fitted into the bush 54.

  A plurality of ring-shaped grooves 52 </ b> A are formed at the tip 52 </ b> B of the joint shaft 52. An adhesive is applied to the outer periphery of the tip 52B of the joint shaft 52 including the inside of the groove 52A. With this configuration, when the joint shaft 52 and the bush 54 are fitted by press-fitting (an interference fit), slipping occurs when an excessive torque exceeding a predetermined value is applied, and the excessive torque disappears. In addition, it is possible to realize a configuration in which the torque up to the predetermined value can be transmitted between the joint shaft 52 and the bush 54 again.

  The swinging intermeshing planetary gear mechanism 44 includes an input shaft 56 (of the planetary gear mechanism 44) that rotates integrally with the bush 54, two eccentric bodies 58 provided on the input shaft 56, and the eccentric body. Two external gears (planetary gears) 60 oscillating eccentrically via 58 and an internal gear 62 in which the external gears 60 are internally meshed. The two external gears 60 have an eccentric phase that is exactly 180 degrees, and swing and rotate while maintaining an eccentric state in directions away from each other. The internal gear 62 is integrated with the low-speed casing body 48. The internal teeth of the internal gear 62 are each constituted by a cylindrical outer pin 62A.

  The number of internal teeth of the internal gear 62 (the number of external pins 62A) is one more than the number of external teeth of the external gear 60 (see FIG. 5). An inner pin 64 is loosely fitted to the external gear 60. The inner pin 64 is integrated with the output flange 66A, and the output flange 66A is integrated with the output shaft 66 of the reduction gear G1.

  In this embodiment, since the internal gear 62 is integrated with the low-speed casing body 48, when the input shaft 56 of the planetary gear mechanism 44 rotates, the external gear 60 swings via the eccentric body 58, The relative rotation (spinning) of the external gear 60 with respect to the internal gear 62 is extracted from the output shaft 66 via the internal pin 64 and the output flange 66A. The output pinion 24 is fixedly connected to the output shaft 66 via a spline 67, and the output pinion 24 is meshed with the already-described internal gear 28 for turning (FIGS. 3 and 4). It is said that.

  Here, the arrangement configuration of each member will be described in more detail.

  The reduction gear G1 straddles both the lower plate (first member) 70 and the upper plate (second member) 72 of the wind power generation equipment facing (arranged) at a distance L1 as in the prior art. It can be attached. That is, in the reduction gear G1, the load side of the low-speed casing body 48 is supported by the lower through hole 70A of the lower plate 70, and the anti-load side is supported by the upper through hole 72A of the upper plate 72. More specifically, in this embodiment, the load side of the low-speed casing body 48 is supported by the lower plate 70 by being inserted into the lower through hole 70A of the lower plate 70, and the anti-load side is The bolt 63 that is inserted into the upper through hole 72 </ b> A of the upper plate 72 and penetrates a part of the low-speed casing body 48 is supported by being screwed into the upper plate 72. As described above, the lower plate 70 and the upper plate 72 are part of a huge casting constituting the floor surface 12A of the nacelle 12, and the distance L1 and the lower through hole 70A of the lower plate 70 are the same. The specifications such as the size of the upper through-hole 72A of the upper plate 72 are not of a nature that can be freely changed for reasons on the reduction gear G1 side.

  Therefore, in the present embodiment, the following configuration is adopted in order to further increase the strength of the reduction gear G1 in this mounting environment.

  Of the bearings 74 and 76 that support the output shaft 66, the anti-load side bearing 76 is constituted by a ball bearing having an outer ring 76A, rolling elements 76B, and an inner ring 76C. In the axial direction X of the output shaft 66, the anti-load side bearing 76 has a portion 76A1 of the outer ring 76A of the anti-load side bearing 76 at a position corresponding to the upper plate 72 (a position corresponding to the upper plate 72). overlapping). Hereinafter, the overlapping portion 76A1 is appropriately referred to as an overlapping portion 76A1. Coupled with this configuration, the bearing span of the load-side bearing 74 and the anti-load-side bearing 76 is L2, and the length is almost twice as long as the conventional bearing span Lo. In this embodiment, the pitch circle (the diameter) of the rolling elements 76B of the anti-load side bearing 76 is d5.

  Further, the thickness D1 of the low-speed casing body 48 in the vicinity of the overlapping portion 76A1 of the anti-load side bearing 76 can be borrowed from the strength (rigidity) on the upper plate 72 side, so that it is thinner than the conventional thickness Do (Do > D1). Further, the thickness D2 of the low-speed casing body 48 between the lower plate 70 and the upper plate 72 is substantially stress free in terms of strength, and therefore may be made thinner than the thickness D1 in the vicinity of the overlapping portion 76A1. Is possible. Thereby, weight and cost can be reduced accordingly.

  Furthermore, in this embodiment, in the axial direction X of the output shaft 66, the meshing position E <b> 1 between the internal gear 62 and the external gear 60 of the swinging intermeshing planetary gear mechanism 44 corresponds to the upper plate 72. It is arranged further on the side opposite to the load than the position. In other words, it can be said that the planetary gear mechanism (reduction mechanism) 44 is located on the side opposite to the load from the upper plate 72. Therefore, in this embodiment, the outer diameter d1 of the meshing position corresponding portion 48A1 (corresponding to the meshing position E1 of the planetary gear mechanism 44) of the low speed side casing body 48 is made smaller than the inner diameter D3 of the upper through hole 72A of the upper plate 72. There is no need (there is no restriction reason d1 <D3). For this reason, in this embodiment, the outer diameter d1 of the meshing position corresponding portion 48A1 of the low speed side casing body 48 is made larger than the inner diameter D3 of the upper through-hole 72A and a sufficient thickness D4 is secured. And, in the radially inner side (engagement position E1) of the portion having the sufficiently large outer diameter d1 and the sufficiently thick thickness D4 of the low speed side casing body 48, it has a larger diameter than the conventional one (high strength). ) The internal gear 62 and the external gear 60 mesh with each other.

  Next, the operation of the speed reducing device G1 for wind power generation equipment according to this embodiment will be described.

  The operation of the power transmission system of the reduction gear G1 is as already outlined with the description of the configuration. The rotation of the motor shaft 22A of the motor 22 is decelerated via the hypoid orthogonal gear mechanism 40, the parallel shaft gear mechanism 42, and the swinging intermeshing planetary gear mechanism 44 and is taken out from the output shaft 66, and the spline 67 is Via the output pinion 24. Since the output pinion 24 meshes with the internal gear 28 for turning, and the internal gear 28 is fixed to the cylindrical column 11 side, the nacelle 12 is eventually opposed to the cylindrical column 11 by reaction. Rotates itself horizontally.

Here in this embodiment:
A) Of the bearings 74 and 76 that support the output shaft 66 of the reduction gear G1, a part (overlapping portion) 76A1 of the non-load-side bearing 76 (outer ring 76A thereof) is an upper plate (in the axial direction X of the output shaft 66). It overlaps the position corresponding to the second member 72. For this reason, the anti-load side bearing 76 can directly receive the reaction force generated in the anti-load side bearing 76 from the highly rigid upper plate 72 itself having a large mass;
B) Since the bearing span L2 of the load-side bearing 74 and the anti-load-side bearing 76 is longer (than the conventional bearing span Lb), the bending moment applied when the output shaft 66 is tilted is reduced (less than the conventional force). Can be received at;
C) The thickness D1 of the low speed side casing body 48 corresponding to the overlapping portion 76A1 of the anti-load side bearing 76 is viewed from the viewpoint of securing the necessary strength, and the conventional thickness Do is determined from the above circumstances A) and B). Can be designed to be thinner;
D) An intermediate portion (a portion where strength is almost unnecessary) of the low-speed casing body 48 that is substantially stress-free can be made thinner than the thickness D1;
E) The meshing position E1 between the internal gear 62 and the external gear 60 of the planetary gear mechanism 44 is further arranged on the non-load side than the position corresponding to the upper plate 72 in the axial direction X of the output shaft 66. . For this reason, the outer diameter d1 of the meshing position corresponding portion 48A1 of the low-speed casing body 48 is very large (because the size of the upper through hole 72A of the upper plate 72 is not restricted). Therefore, a large accommodation space for the planetary gear mechanism 44 can be secured, and each member (the internal gear 62, the external gear 60, etc.) constituting the planetary gear mechanism 44 is designed to be larger;
F) The mesh position corresponding portion 48A1 of the low-speed casing body 48 has a sufficiently thick thickness D4 (since there is no circumstance that the planetary gear mechanism 44 is passed inside). Therefore, the rotation of the planetary gear mechanism 44 accommodated inside the radial direction is stable and can be smoothly rotated;
For example, many effective effects can be obtained with respect to strength enhancement.

  If the situation peculiar to the present embodiment will be further described with respect to the effect F) that the rotation of the accommodated planetary gear mechanism 44 is stabilized, generally, a swinging intermeshing planetary gear mechanism will be described. Since the meshing position of the external gear and the internal gear rotates while moving, the direction of the load changes depending on the meshing position. In particular, as in this embodiment (the conventional example in FIG. 9 is also the same), the two external gears 60 are oscillated and rotated while maintaining an eccentric state in a direction away from each other with an eccentric phase shifted by 180 degrees. In the case of such a swinging internal meshing planetary gear mechanism, each external gear 60 swings at a different phase, so that a moment for tilting the internal gear 62 (the outer pin 62A thereof) is generated. Inevitable. For this reason, higher rigidity is required for the internal gear 62 side (that is, the meshing position corresponding portion 48A1 of the low speed side casing body 48). In the present embodiment, as a result, the internal gear 62 and the (two) external gears 60 can mesh with each other on the radially inner side of the sufficiently thick thickness D4, and under high strength and high rigidity, An extremely smooth and stable deceleration action can be obtained.

  6 and 7 show an example of another embodiment of the present invention.

  In the reduction gear G101 according to this embodiment, the anti-load side bearing 176 that supports the output shaft 166 is disposed coaxially with the outer pin 162A of the internal gear 162. In this anti-load side bearing 176, the low-speed casing body 148 integrated with the internal gear 162 functions as an outer ring, the flange portion 166A of the output shaft 166 functions as an inner ring, and only the rolling element 176B is an internal tooth. The outer pin 162A of the gear 162 is arranged side by side in the axial direction. The rolling element 176B is rotatably supported in a pin groove 162C formed by extending an outer pin groove 162B for the outer pin 162A long in the axial direction. The outer diameter d103 of the rolling element 176B is set slightly larger than the outer diameter d104 of the outer pin 162A of the internal gear 162. This is because the output shaft 166 is supported without any difficulty and the internal gear 162 and the external gear 160 are smoothly meshed.

  In this embodiment, in the axial direction of the output shaft 166, in addition to the planetary gear mechanism 144, the anti-load side bearing 176 is further provided on the anti-load side than the corresponding position of the upper plate 172 (see the position of the rolling element 176B). ). Therefore, the bearing span L102 can be made larger (than the bearing span L2 of the previous embodiment), and the pitch circle diameter d105 of the rolling elements 176B of the anti-load side bearing 176 is set to the anti-load side bearing of the previous embodiment. It can be secured larger than the pitch circle diameter d5 of 176. Therefore, the output shaft 166 can be supported more stably.

  Further, the actual situation is that the pitch circle d5 of the anti-load side bearing 176 of the output shaft 166 of the speed reducer G101 of the wind power generation facility must be very large in size, resulting in high costs. In this embodiment, the groove 162B of the outer pin 162A of the internal gear 162 is extended to form a pin groove 162C so that the internal gear 162 has the function of an outer ring, and the rolling element 167B is placed in the pin groove 162C. Since the anti-load-side bearing 176 is configured only by direct assembly (see FIG. 7), the cost is extremely low compared to a configuration incorporating an independent bearing despite having a large pitch circle d105. Is able to.

  Further, the position of the anti-load side bearing 176 (the position of the rolling element 176B) is further shifted to the anti-load side as compared with the previous embodiment. As a result, in the axial direction X of the output shaft 166, the anti-load side bearing 176 and the bearing 180 supporting the eccentric body shaft (in this embodiment, the input shaft 156) having the eccentric body 158 for swinging the external gear 160 are on the same plane (a plane perpendicular to the output shaft). It arrange | positions above (it arrange | positions so that at least one part may overlap in the axial direction X of the output shaft 166). With this configuration, the input shaft 156 that is an eccentric body shaft is supported on the radially inner side (of the flange portion 166A) of the output shaft 166 that is supported with high support rigidity. Can be performed very smoothly and stably.

  Since the other configuration is basically the same as that of the previous embodiment, members having the same or functional similarity as those of the previous embodiment are denoted by the same reference numerals in the last two digits on the drawing. The duplicated explanation is omitted.

  In the present invention, the configuration of the speed reduction mechanism incorporated in the speed reduction device is not limited to the speed reduction device as described above. FIG. 8 shows an example of still another embodiment of the present invention (only the speed reduction mechanism is shown).

  The reduction gear G201 according to this embodiment has two-stage swinging inscribed planetary gear mechanisms 241 and 244 as a reduction mechanism. Although the two swinging inscribed planetary gear mechanisms 241 and 244 are different in size, the mechanical configuration is basically the same as the planetary gear mechanisms 44 and 144 of the previous two embodiments. In this embodiment, both a part of the anti-load side bearing 276 and a part of the meshing position E201 of the swinging intermeshing planetary gear structure 244 overlap with the corresponding position of the upper plate 272.

  Therefore, both the counter load side bearing 276 and the meshing position E201 of the swinging intermeshing planetary gear structure 244 can receive the reaction force directly from the upper plate 272. Therefore, even if the thickness D201 of the low-speed casing body 248 in this portion is made thinner than the conventional thickness Do, the support rigidity is much higher than that of the structure in which the reaction force is provided from the center of the conventional casing 4. Can be secured. In addition, since almost half of the meshing position E201 is located on the side opposite to the load side than the corresponding position of the upper plate 272, the thickness D204 of the low-speed casing 248 can be made very thick in this part. The strength can be significantly increased as compared with the conventional reduction gear Go.

  A specific configuration of the anti-load side bearing 276 and a bearing 280 supporting an eccentric body shaft (an input shaft 256 in this embodiment) having an eccentric body 258 for swinging the external gear 260 are on the same plane. Other configurations, including the configuration arranged above, are the same as those in the embodiment shown in FIGS. For this reason, the same or functionally similar parts as those of the embodiment are designated by the same reference numerals in the last two digits in FIG.

  In the above embodiment, an example in which the present invention is applied to a reduction device for yaw driving is shown. However, the present invention relates to a wind power generation facility facing (disposed) at a distance. If the speed reducer is mounted across both the first member and the second member, for example, a speed reducer for pitch driving can be applied in the same manner, and similar effects can be obtained.

  As described above, in the present invention, a great merit can be obtained when the speed reducing mechanism of the swinging intermeshing planetary gear mechanism is adopted as the speed reducing mechanism. The speed reduction mechanism is not limited to the inscribed planetary gear mechanism. For example, a reduction mechanism of a simple planetary gear mechanism or a parallel axis reduction mechanism may be used. Combination is also free. Like the above-mentioned embodiment, the deceleration mechanism of an orthogonal axis system may be combined. Of course, a plurality of eccentric body shafts are provided in a state of being offset from the shaft center of the speed reducer and penetrating the external gear, and the plurality of eccentric body shafts rotate in the same phase so that the external gear is eccentrically swung. It may be a swinging intermeshing type reduction mechanism of the type to be made.

  In each of the previous embodiments, the meshing position of the speed reduction mechanism is further on the anti-load side than the anti-load side bearing. For example, as shown in FIG. The configuration may be such that the meshing position of the speed reduction mechanism is present on the load side of the load side bearing. Even in this case, at least a part of the bearing on the anti-load side among the bearings supporting the output shaft of the speed reducer is the second member (the upper plate in the previous embodiment) in the axial direction of the output shaft. As long as it is arranged at a position corresponding to the above, or at a position on the further anti-load side than the corresponding position, a corresponding effect can be obtained.

  Moreover, in the previous embodiment, the floor surface of the nacelle formed of a casting as an integral body has been exemplified as the first and second members. However, the present invention is the kind of the first and second members of the wind power generation facility. The material, the formation method, etc. are not asked. For example, as a substitute for the reduction gear that has already been installed at the installation location of the specific first and second members of the wind power generation facility, it is also suitable for situations where a high-strength reduction gear is re-installed at the same installation location Applicable to.

10 ... wind power generation equipment 11 ... cylindrical support 12 ... nacelle (power generation room)
DESCRIPTION OF SYMBOLS 14 ... Yaw drive device 18 ... Nose cone 20 ... Windmill blade 22 ... Motor 24 ... Output pinion 44 ... Final stage reduction mechanism (oscillating intermeshing planetary gear mechanism)
60 ... External gear 62 ... Internal gear 66 ... Output shaft 70 ... Lower plate (first member)
72 ... Upper plate (second member)
74 ... Load side bearing 76 ... Anti-load side bearing 76A1 ... Part (corresponding part)
E1 ... meshing position L1 ... distance

Claims (5)

In a reduction device for a wind power generation facility installed across both the first member and the second member of the wind power generation facility arranged at a distance,
While the load side of the casing of the speed reducer is supported by the first member and the anti-load side is supported by the second member,
Of the bearings that support the output shaft of the speed reducer, at least a part of the bearing on the anti-load side is in a position corresponding to the second member in the axial direction of the output shaft, or further counter to the corresponding position. A speed reducer for wind power generation equipment, characterized by being arranged at a load side position. In claim 1,
The speed reduction mechanism of the speed reduction device is constituted by a planetary gear mechanism in which a planetary gear meshes with an internal gear, and
The meshing position of the internal gear and the planetary gear is arranged at a position corresponding to the second member in the axial direction of the output shaft, or at a position on the more anti-load side than the corresponding position. A reduction device for wind power generation equipment characterized by the above. In claim 2,
The planetary gear mechanism has a swinging internal meshing planetary planetary gear in which the planetary gear has external teeth with a slight difference in the number of teeth from the internal teeth of the internal gear and is in meshing with the internal gear while swinging. A speed reducer for wind power generation equipment, characterized by being a gear mechanism. In claim 3,
The planetary gears are arranged in a plurality of rows in the axial direction,
The wind power is characterized in that the meshing position of the internal gear and the plurality of planetary gears is disposed at a position corresponding to the second member or at a position on the more anti-load side than the corresponding position. Reducer for power generation equipment. In any one of Claims 1-4,
The reduction mechanism of the reduction gear includes a swinging internal meshing type in which the planetary gear has external teeth with a slight difference in the number of teeth from the internal teeth of the internal gear and is in meshing with the internal gear while swinging. An eccentric having a planetary gear mechanism and an anti-load side bearing among the bearings supporting the output shaft of the speed reducer in the axial direction of the output shaft, and an eccentric body for swinging the planetary gear A speed reducer for wind power generation equipment, characterized in that the bearings supporting the body axis are arranged on the same plane.

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