JP5074443B2 - Reducer with output pinion for wind power generation system - Google Patents

Description

  The present invention relates to a reduction gear with an output pinion of a wind power generation system.

  Patent Document 1 discloses a “decelerator with an output pinion” used for turning driving of a power generation unit (nacelle) or the like of a wind power generation system. This reduction device with an output pinion includes a reduction mechanism for reducing the rotation of the electric motor, an output shaft connected to or integrated with an output member of the reduction mechanism, and an output pinion provided on the output shaft. Prepare. The speed reducer with an output pinion is attached to the power generation unit side, and the output pinion meshes with a turning internal gear fixed to the column side of the wind power generation system. As a result, the power generation unit is driven to turn (yaw drive), and the wind turbine blades can always be directed in the direction of the wind so that the wind force can efficiently act on the blades.

  The speed reducer with an output pinion used in a wind power generation system is a natural counterpart device called “wind power”, in addition to handling extremely large torque, and sometimes has a reaction force much greater than the torque handled during normal power generation. It may hang. For this reason, the design is such that a large safety factor is applied which is different from that of a normal machine in which the load falls within a certain range. Coupled with these reasons, the yaw control device in the wind power generation system is a “mega device” of the 2 MW class and the diameter of the swivel gear is about 2400 mm (2000 mm to 3000 mm).

Japanese Patent Laying-Open No. 2005-61519 (FIG. 1 etc.)

  The output shaft of the speed reducer with an output pinion of a wind power generation system is also viewed from the viewpoint of maintaining good contact between the output pinion and the swivel gear even when an unexpectedly large load is applied due to a gust of wind or the like. Originally, it is preferable that the casing is supported at both ends. On the other hand, since it is installed at the top of a high tower, naturally the demand for compactness is very strong, and it is also necessary to avoid interference with the swivel gear, so the space for the casing that supports the output shaft is limited. It will be Therefore, in particular, it is very difficult to support the non-drive source side of the output shaft with a high load capacity and high strength.

  The present invention has been made to solve such a conventional problem, and particularly when the output shaft of a reduction gear with an output pinion of a wind power generation system is supported at both ends, in particular, a counter-drive source for the output shaft. The challenge is to be able to improve the support capacity of the side.

  The present invention includes a speed reduction mechanism that reduces the rotation of a drive source, an output shaft that is connected to or integrated with an output member of the speed reduction mechanism, and an output pinion that is provided on the output shaft and can mesh with a gear of a wind power generation system. A reduction device with an output pinion of a wind power generation system, wherein the output shaft is supported at both ends by a pair of bearings on a drive source side and a counter drive source side, and both of the pair of bearings A part of the output pinion is housed in an output-side casing having a meshing window for meshing with the gear, and the rolling element of the bearing on the counter-drive source side of the pair of bearings rotates but does not revolve. The above-mentioned problem is solved by adopting a configuration in which no roller is disposed on the side of the meshing window.

  According to the present invention, the output shaft of the reduction gear is supported at both ends by the pair of bearings on the drive source side and the counter drive source side. Both of the pair of bearings are accommodated in an output side casing having a meshing window for meshing the output pinion with a gear such as a turning gear.

  Here, in order for the output pinion to mesh with the gear without interfering with the output side casing, the outer periphery on the meshing window side of the output side casing must be radially inward from the root circle of the output pinion. I must. Therefore, it is very difficult to secure a sufficient thickness on the meshing window side if a normal bearing is installed normally, and this forms a bearing on the side opposite to the drive source when adopting a structure that supports both ends of the output shaft. It becomes a de facto big obstacle when doing.

  In the present invention, first, the rolling element of the bearing on the counter drive source side among the pair of bearings that support the output shaft is constituted by a plurality of rollers that rotate but do not revolve. With this configuration, the position of each rolling element of the bearing on the counter drive source side in the circumferential direction is determined, and as a result, the rolling elements positioned on the meshing window side are also determined. In addition, in the present invention, no rolling element is disposed on the side of the meshing window.

  This configuration is adopted for the following reason. That is, the load applied to the rolling elements located on the side of the meshing window is a component applied in the tangential direction of the pitch circle of the output pinion (because the output pinion and the turning internal gear mesh with each other at the meshing window). Occupies the majority, and there is almost no component applied in the radial direction. In addition, when a reaction force is applied from the turning internal gear side by wind force, the direction is also reversed, and the component applied to the tangential direction of the pitch circle of the output pinion accounts for the majority. Therefore, even if the arrangement of the rollers at this portion is omitted, no particular problem occurs in terms of strength or rotational smoothness.

  On the other hand, if no roller is arranged on the meshing window side, even if the pitch circle of the entire rolling element is increased to increase the load capacity, the gear side of the output casing (the gear side of the swivel gear, etc.) It is possible to prevent the strength of this portion from being reduced due to thinning. As a result, the strength of the entire roller bearing can be increased. Therefore, it is possible to further increase the load capacity as a whole of the bearing on the side opposite to the driving source, and to secure a higher safety factor as a driving device for a natural power generation system called wind power. From the opposite perspective, if the same load capacity is sufficient, the bearing on the counter drive source side can be made more compact, so the entire power generation unit that must be installed at a very high position from the ground Can be reduced in weight.

  Further, since the output pinion is almost entirely covered with the output side casing except for the meshing portion, the teeth of the output pinion can be protected.

  ADVANTAGE OF THE INVENTION According to this invention, when supporting both the output shafts of the reduction gear with an output pinion of a wind power generation system, especially the support capability by the side of the counter drive source of an output shaft can be improved.

Sectional drawing which shows the reduction gear with an output pinion of the wind power generation system which concerns on an example of embodiment of this invention. Sectional view along the line II-II in FIG. Sectional view along the arrow III-III line of FIG. Sectional drawing which shows the reduction gear with an output pinion of the wind power generation system which concerns on an example of other embodiment of this invention. Sectional drawing which shows the reduction gear with an output pinion of the wind power generation system which concerns on an example of other embodiment of this invention. Sectional drawing which shows the reduction gear with an output pinion of the wind power generation system which concerns on an example of other embodiment of this invention. Schematic front view of a wind power generation system in which the power transmission device according to the embodiment is incorporated Side view The perspective view which shows the outline of the electric power generation unit in the wind power generation system

  Hereinafter, a reduction gear with an output pinion of a wind power generation system according to an example of an embodiment of the present invention will be described in detail.

  FIG. 7 is a schematic front view of the wind power generation system 10, and FIG. 8 is a side view thereof.

  The wind power generation system 10 includes a power generation unit (nacelle) 12 at the top of a cylindrical column 11. FIG. 9 is a perspective view showing an outline of the power generation unit 12. The power generation unit 12 incorporates a drive device 14 for yaw drive and a drive device 16 for pitch drive. The drive device 14 for yaw drive is for controlling the turning angle of the entire power generation unit 12, while the drive device 16 for pitch drive is the pitch angle of the three windmill blades 20 attached to the nose cone 18. It is for control.

  In the present embodiment, since the present invention is applied to the drive device 14 for yaw drive, the drive device 14 for yaw drive will be described here. The drive unit 14 for yaw drive includes an electric motor (drive source) Mo, a reduction gear G1 with an output pinion 24, and a turning internal gear (gear of a wind power generation system) 28 that meshes with the output pinion 24. In the example of FIG. 9, four reduction gears G <b> 1 are depicted and are fixed to the main body side of the power generation unit 12. On the other hand, the turning internal gear 28 in which the output pinions of the four reduction gears G1 are meshed with each other is fixed to the cylindrical column 11 and constitutes an inner ring of a yaw bearing (not shown). The outer ring of the yaw bearing is fixed to the main body side of the power generation unit 12. With this configuration, by rotating the output pinion 24 of the speed reducer G1 by the electric motor Mo, the entire power generation unit 12 is engaged with the shaft center 35 of the cylindrical column 11 through the meshing of the output pinion 24 and the turning internal gear 28 ( 9) can be swiveled around. As a result, the nose cone 18 can be directed in a desired direction (for example, the windward direction), and the wind pressure can be efficiently received.

  Next, the reduction gear G1 with the output pinion 24 will be described in detail with reference to FIGS.

  Referring to FIG. 1, the reduction gear G1 includes a reduction mechanism 34 that reduces the rotation of the electric motor Mo, an output shaft 32 that is integrated with an output flange (output member) 36 of the reduction mechanism 34, and the output. And an output pinion 24 provided on the shaft 32 and capable of meshing with the turning internal gear 28 (not shown in FIG. 1).

  The speed reduction mechanism 34 is configured by connecting an input side speed reduction mechanism 40 and an output side speed reduction mechanism 42 of an intermeshing planetary gear mechanism in series. This is because the reduction gear G1 requires an extremely high reduction ratio of 1/1000 to 1/2000 in function.

  The motor shaft 41 of the motor Mo also serves as the input shaft of the input side reduction mechanism 40, and the rotation of the motor shaft 41 decelerated by the input side reduction mechanism 40 is further reduced by the output side reduction mechanism 42. ing. The input side reduction mechanism 40 and the output reduction mechanism 42 have different sizes because they handle different torques. However, since they have almost the same (known) configuration in terms of mechanism, the output side reduction mechanism 40 and the output reduction mechanism 42 are representatively shown here. The speed reduction mechanism 42 will be described, and redundant description of the input side speed reduction mechanism 40 will be omitted.

  The output-side speed reduction mechanism 42 includes an input shaft 44 that is integral with (combined with) the output shaft of the input-side speed reduction mechanism 40, two eccentric bodies 46, 48 provided on the input shaft 44, and the eccentric bodies 46, 48. Two external gears 50 and 52 that are eccentrically oscillated, and an internal gear 54 that is internally meshed with the external gears 50 and 52 are provided. The external gears 50 and 52 are just 180 degrees out of phase. That is, the two external gears 50 and 52 swing and rotate while maintaining an eccentric state in directions away from each other. The internal gear 54 also serves as the casing 56 of the output side reduction mechanism 42. The internal teeth of the internal gear 54 are each constituted by a cylindrical outer pin 58. The number of internal teeth of the internal gear 54 (the number of external pins 58) is one more than the number of external teeth of the external gears 50 and 52. An inner pin 60 is loosely fitted to the external gears 50 and 52 via an inner roller 62. The inner pin 60 is integrated with an output flange (output member) 36 (of the output side reduction mechanism 42), and further integrated with the output shaft 32 of the reduction gear G1 via the output flange 36. Note that. The inner pin 60 is press-fitted into the output flange (output member) 36 from the counter-electric motor side. The inner pin 60 is provided with a flange 60 </ b> A for positioning the inner pin 60 itself and preventing the inner pin 60 from coming off to the electric motor Mo side. Further, an inner pin support ring 61 in which through holes 61A corresponding to the circumferential position of the inner pin 60 (the number of inner pins 60) are formed is fitted on the electric motor side of the inner pin 60. This is intended to distribute / reduce the load acting on the inner pins 60 by bundling the electric motors of the plurality of inner pins 60.

  In this embodiment, since the internal gear 54 is integrated with the casing 56, the external gears 50 and 52 swing once when the input shaft 44 of the output side reduction mechanism 42 rotates once, and the internal gears. The meshing position with 54 is shifted by one tooth (by the difference in the number of teeth). As a result, the external gears 50 and 52 rotate relative to the internal gear 54 by an angle corresponding to the difference in the number of teeth (rotates in the direction opposite to the rotation of the input shaft 44). The relative rotation (spinning) of the external gears 50 and 52 with respect to the internal gear 54 is taken out from the output flange 36 via the internal pin 60 and further output to the output shaft 32 integrated with the output flange 36. It has become so.

  An output pinion 24 is connected to and fixed to the output shaft 32 via a spline portion 65, and the output pinion 24 is configured to mesh with the turning internal gear 28 (FIG. 9) already described.

  Here, the support structure (built-in structure) of the output shaft 32 will be described in detail with reference to FIGS. 2 is a cross-sectional view taken along the line II-II in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line III-III in FIG.

  The output shaft 32 is supported at both ends by a pair of bearings of a self-aligning roller bearing 70 on the motor side (drive source side) and a roller bearing 72 on the counter motor side (counter drive side). The self-aligning roller bearing 70 and the roller bearing 72 are both housed in an output-side casing 74 that is integrally formed of a single member (including the cover portion 74A on the counter-drive source side of the output shaft 32). .

  Of the pair of bearings 70 and 72, the self-aligning roller bearing 70 on the motor side is separated from the output-side casing 74 and has a bearing housing 76 having an outer diameter d2 larger than the outer diameter d1 of the output pinion 24. The output casing 74 is supported.

  The output casing 74 has an opening 74 </ b> C formed on the axial motor side so as to be larger than the outer diameter d <b> 1 of the output pinion 24 so that the bearing housing 76 can be inserted therethrough. Further, as shown in FIG. 2, the output casing 74 has a mesh window 74 </ b> D for meshing the output pinion 24 with the above-described turning internal gear 28 at a part of the outer periphery thereof. A width dimension (opening width dimension) L1 perpendicular to the axis of the opening 74D1 of the meshing window 74D is smaller than the outer diameter d1 of the output pinion 24. 1 and 2 is a bolt hole used when G1 is fixed to the power generation unit (nacelle) 12 in the reduction gear with an output pinion.

  A bush 82 that rotates integrally with the output shaft 32 is disposed at a portion corresponding to the inner periphery 76 </ b> A of the bearing housing 76 in the axial direction of the output shaft 32. Further, the speed reduction mechanism 34 (the input side speed reduction mechanism 40 and the output speed reduction mechanism 42) is provided between the inner periphery 76A of the bearing housing 76 and the bush 82 (which is a member that rotates integrally with the output shaft 32). An oil seal 84 for sealing is disposed. In this embodiment, the oil seal 84 is disposed on the side opposite to the driving source in the axial direction of the self-aligning roller bearing 70 that is a driving source side bearing, and the self-aligning roller bearing 70 is a lubricant on the speed reduction mechanism 34 side. Lubricated by. That is, the speed reduction mechanism 34 and the self-aligning roller bearing 70 side and the output pinion 24 and the roller bearing 72 side are blocked by the oil seal 84.

  The reason for this configuration is as follows. Since the turning internal gear 28 of the wind power generation system 10 has a very large diameter (usually φ2000 mm to φ3000 mm), lubrication of the turning internal gear 28 is not achieved by “closed type” in which oil is enclosed in a closed space. Without using grease in an open space). Accordingly, the grease is likely to become dirty due to contamination of dust. Further, since the rotation of the turning internal gear 28 is about 2 rpm at the maximum and is very low speed, the grease enters the self-aligning roller bearing 70 side from the turning internal gear 28 side and the self-aligning roller bearing 70. The action of replenishing the internal grease cannot be expected from the beginning. Rather, even if it enters, the grease in the self-aligning roller bearing 70 is undesirably contaminated. Conversely, when viewed from the self-aligning roller bearing 70 side, good quality grease lubrication is indispensable for preventing fretting. Therefore, in order to keep good quality grease in the self-aligning roller bearing 70 (without leaking to the turning internal gear 28 side), on the other hand, the dirty grease on the turning internal gear 28 side does not rise. The oil seal 84 is arranged on the lower side (counter drive source side) of the self-aligning roller bearing 70. The presence of the oil seal 84 can prevent (dirty) grease, foreign matter, and the like from entering the speed reduction mechanism 34 from the output pinion 24 side. A method for incorporating the oil seal 84 will be described later.

  A convex portion 74B is formed on the output side casing 74 toward the inside in the radial direction. On the other hand, the flange 76B is formed in the bearing housing 76 toward the outer side in the radial direction. The flange portion 76B and the convex portion 74B of the output side casing 74 can abut against each other in the axial direction. The contact between the flange portion 76B and the convex portion 74B causes the bearing housing 76 to pivot relative to the output side casing 74. It is configured to be positioned in the direction.

  The bearing housing 76 is fixed to the output casing 74 by a fixing bolt 86 that fixes the flange portion 76B and the convex portion 74B in the axial direction.

  In this embodiment, the output shaft 32 is integrally formed with the output flange (flange-shaped output member) 36. Therefore, when fixing the flange portion 76B and the convex portion 74B by the fixing bolt 86, that is, fixing the bearing housing 76 to the output side casing 74, a through hole (for inserting a tool for tightening the fixing bolt 86) ( (Not shown) is formed on the output flange 36 in parallel with the inner pin 60. When considering the ease of assembly, it is preferable to form the through holes in the output flange 36 by the number of the fixing bolts 86 corresponding to the positions of all the fixing bolts 86. However, the through holes do not necessarily have to be formed corresponding to all the fixing bolts 86 as many as the fixing bolts 86 (one may be used), for example, corresponding to every other fixing bolt 86. You may make it form the through-hole only for half. Thus, if a number corresponding to the “divisor” of the number of the fixing bolts 86 is formed at a predetermined interval, the workability of fixing the bearing housing 76 is not significantly reduced, and the output by forming the through-holes is reduced. A decrease in strength of the flange 36 can be minimized.

  Here, the configuration of the roller bearing 72 which is the bearing on the counter driving source side will be described in detail.

  In this embodiment, the roller bearing 72 which is the bearing on the counter driving source side is directly supported by the output side casing 74 (without the bearing housing 76).

  The rolling element of the roller bearing 72 includes a plurality of “rollers” 73 that rotate but do not revolve. Here, “does not revolve” includes the case where there is some play in the circumferential direction. The point is that the roller 73 does not move toward the side (meshing position) facing the turning internal gear 28.

  By the way, in this reduction gear G1, as will be described later, an assembly method is adopted in which the output shaft (for each output pinion 24) is assembled from the upper side of the turning internal gear 28 and the output pinion 24 is engaged with the turning internal gear 28. is doing. Here, in particular, in order to mesh the swivel internal gear 28 and the output pinion 24 without interference between the swivel internal gear 28 and the output side casing 74, the meshing window 74 </ b> D side of the output side casing 74 is arranged. The outer periphery 74F must be radially inward (left side in FIG. 1) with respect to the root circle 24A of the output pinion 24. Therefore, if a normal bearing is normally incorporated, it is very difficult to secure a sufficient thickness T1 on the side of the meshing window 74D, which is a major obstacle when adopting a configuration in which the output shaft 32 is supported at both ends. It has become.

  Therefore, in this embodiment, as shown in FIG. 3, the rollers (73) are not arranged on the side of the meshing window 74D (in this embodiment, two rollers (73) are not arranged. ). This is because the load vector applied to the output pinion 24 is taken into consideration, and the roller (73) in this portion is omitted to achieve compactness, and a high-strength bearing having a larger load capacity as a whole is configured. .

  That is, the load applied to the roller (73) located on the meshing window 74D side is determined by the pitch of the output pinion 24 (because the output pinion 24 and the turning internal gear 28 mesh with each other in the meshing window 74D). Most of the components are applied in the tangential direction of the circle, and almost no components are applied in the radial direction. In addition, when a reaction force is applied from the turning internal gear 28 side by wind force, the direction is also reversed, and the component applied to the tangential direction of the pitch circle of the output pinion 24 occupies the majority. Therefore, even if the arrangement of the roller (73) at this portion is omitted, there is no particular problem in terms of strength or rotational smoothness. On the other hand, if the rollers (73) are not arranged on the meshing window 74D side, even if the pitch circle of the rollers 73 is increased to increase the load capacity, the turning internal gear of the output side casing 74 is increased. It can be prevented that the 28 side becomes thin and the strength of this portion is reduced. As a result, it is possible to configure a high-strength bearing having a larger load capacity as a whole than a configuration in which rollers are simply arranged all around.

  The outer ring of the roller bearing 72 is constituted by the output casing 74. That is, the output side casing 74 also serves as the outer ring of the roller bearing 72. A holding hole 74 </ b> E for holding the roller 73 is integrally formed in the output side casing 74. This is because the holding hole 74E of the roller 73 is directly formed in the output side casing 74 itself so that the thickness of the output side casing 74 in the radial direction is as thick as possible. In addition, the inner periphery of the output side casing 74 may be formed by a simple circle that circumscribes the roller 73, for example, and the roller 73 may be held using a separate retainer or the like (not shown).

  In this embodiment, the output casing 74 also serves as an outer ring of the roller bearing 72. However, the outer ring of the roller bearing 72 is a member independent of the output casing 74 (for example, FIG. 3). And the portion of the outer ring (77) on the circumferential meshing window side is made thick (to the extent that the rollers are omitted). Also good. Furthermore, in this embodiment, the roller bearing 72 is provided with an independent inner ring 79 in consideration of ease of assembly, but the inner ring 79 of the roller bearing (counter-drive source side bearing) 72 is not necessarily required. In FIG. 1, reference numeral 88 denotes a collar, and reference numeral 90 denotes an oil seal that seals the lubricant of the roller 72.

  Since the reduction gear G1 with output pinion has the above-described configuration, the output shaft 32 is supported at both ends, thereby making the entire device compact and covering and protecting most of the output pinion 24. The assembly can be easily performed while adopting a configuration that can be performed.

  In order to incorporate the output shaft 32, first, the self-aligning roller bearing 70 is shrink-fitted onto the output shaft 32 from the non-output flange side of the output shaft 32. Next, along with the self-aligning roller bearing 70, the bush 82 is shrink-fitted onto the output shaft 32. Thereafter, the self-aligning roller bearing 70 and the bush 82 (which are hot due to shrink fitting) are cooled, and the bearing housing 76 is heated and press-fitted or shrink-fitted onto the outer periphery of the outer ring 70A of the self-aligning roller bearing 70. . In the case of shrink fitting, after the bearing housing 76 is cooled, an oil seal 84 is mounted between the inner periphery 76 </ b> A of the bearing housing 76 and the bush 82. With this procedure, the heat-sensitive oil seal 84 can be mounted in a state where both the bearing housing 76 and the bushing 82 are cooled.

  After the oil seal 84 is attached, the output pinion 24 is shrink-fitted on the spline portion 65 and the collar 88 is shrink-fitted on the output shaft 32. This completes the subassembly around the output shaft 32.

  On the other hand, the roller 73 of the roller bearing 72 is directly assembled in the holding hole 74E (FIG. 3) formed in the bottom of the output side casing 74. When there is an inner ring 79 as in this example, the inner ring 79 is also incorporated. Then, a lubricant is put in the bottom portion of the output side casing 74, and the oil seal 90 is incorporated in the bottom portion of the output side casing 74 in advance.

  In this state, the above-described output shaft 32 (in the sub-assembly state) is assembled so as to drop into the inner ring 79 of the roller bearing 72 from above (from the drive source side). In this embodiment, the outer diameter of the bearing housing 76 is larger than the outer diameter of the output pinion 24, and the output side casing 74 is formed so that the bearing housing 76 can be inserted (the outer diameter of the output pinion 24 is formed larger). An opening 74C is provided. For this reason, it is possible to drop the output shaft 32 into the output side casing 74 with the bearing housing 76 being sub-assembled.

  When the output shaft 32 is dropped into the output-side casing 74, the flange portion 76B formed on the bearing housing 76 and the convex portion 74B formed on the output-side casing 74 abut on each other in the axial direction. Therefore, the bearing housing 76 is positioned in the axial direction with respect to the output side casing 74 by this contact. The bearing housing 76 is fixed to the output side casing 74 by inserting a tool through the through hole (not shown) formed in the output flange 36 in a positioned state and tightening the fixing bolt 86. In addition, when the through-hole formed in the output flange 36 is not formed in the position corresponding to all the fixing bolts 86, the fixing bolts 86 should be fixed sequentially while rotating the output flange 36 slightly.

  Thus, in this embodiment, all members around the output shaft 32 can be provided in the output-side casing 74 in advance, or can be assembled in a sub-assembled state around the output shaft 32. Does not require large-scale equipment. In addition, since the output shaft 32 is supported at both ends by the output side casing 74, the support rigidity can be maintained extremely high while being compact, and the rigidity capable of withstanding the reaction force caused by a strong wind is provided. Can be provided. Further, since the output side casing 74 is integrated by a single member including the cover portion 74A on the side opposite to the driving source of the output shaft 32, it is possible to ensure a strong rigidity with a minimum thickness. Is done.

  In addition, in this embodiment, the width dimension L1 of the opening 74D1 of the meshing window 74D is set to the output pinion (for example, because the output pinion 24 does not need to be assembled from the side of the meshing window 74D, that is, from the direction perpendicular to the axis). It is smaller than the outer diameter d1 of 24, and is the minimum size necessary for meshing with the swivel internal gear 28. As a result, the strength of the output side casing 74 can be increased as much as possible, and the output pinion 24 can be covered and protected as widely as possible. Further, the rolling element of the roller bearing 72 is constituted by a plurality of rollers 73 that rotate but do not revolve, and the rollers 73 are not disposed on the side of the meshing window 74D. Even when the load capacity is increased by enlarging the circle, it is possible to prevent the strength of this portion from being reduced because the turning internal gear 28 side of the output side casing 74 becomes thin. Depending on the design, more rollers can be arranged as much as the pitch circle can be increased. For example, even if “two” rollers on the meshing window 74D side are omitted, the total number of rollers is “ In some cases, it may be possible to simply reduce “only one”. Further, instead of increasing the pitch circle (or increasing the pitch circle), the diameter of the roller 73 itself is made larger, or the wall thickness of the output side casing 74 is made thicker. It is also possible to do. In any case, the output shaft 32 can be supported in a higher-strength manner with a larger load capacity than the configuration in which the rollers are simply arranged all around the circumference, and the meshing window 74D of the output-side casing 74 can be supported. Together with the fact that it is formed small, it is possible to realize further rigidity enhancement.

  Next, another embodiment of the present invention will be described.

  In the above-described embodiment, the output pinion 24 is connected and fixed to the output shaft 32 via the spline portion 65, but may be integrally formed from the beginning. In this case, for example, the output flange 136 of the speed reduction mechanism 134 is configured separately from the output shaft 132 as in the speed reduction device G2 with an output pinion shown in FIG. The flange 136 and the output shaft 132 may be connected. The self-aligning roller bearing 170, the bearing housing 176, the bush 182 and the oil seal 184 are incorporated into the output shaft 132 from the motor side of the output pinion 124 (after the self-aligning roller bearing 170 is fitted into the housing 176). In this structure, in order to prevent the oil seal 184 from being damaged by heat at the time of assembling, there is a possibility that some shrinkage fitting is changed to press-fitting, but the output flange 136 is necessary. Thus, there is an advantage that it is not necessary to form a through hole for inserting a tool for tightening the fixing bolt 186. Further, since the output flange (output member) 136 is separated from the output shaft 132, for example, the inner pin 160 of the output-side reduction mechanism 142 can be incorporated into the output flange 136 by press-fitting or shrink fitting. As a result, the configuration of the output side reduction mechanism 142 can be further simplified. Since the other configuration is the same as that of the previous embodiment, the same reference numerals are given to the portions having the same or the same function in the drawing, and the duplicate description is omitted.

  FIG. 5 shows an example of another embodiment.

  In the embodiment of FIG. 5, the input side reduction mechanism 240 is the same as that of the previous embodiment, but the configuration of the output side reduction mechanism 242 is a so-called distribution type inscribed mesh planetary gear reduction mechanism. . That is, the output side reduction mechanism 242 includes three (only one shown) spur gears 293 connected to the output shaft (input shaft of the output side reduction mechanism) 244 of the input side reduction mechanism 240, and the three spur gears. Three eccentric body shafts 294 respectively rotated by 293, and eccentric bodies 246, 248 incorporated in the respective eccentric body shafts 294 and eccentric in phase with the eccentric body shafts 294, The external gears 250 and 252 engaged with the eccentric bodies 246 and 248 and the internal gear 254 with which the external gears 250 and 250 are internally meshed are mainly configured.

  In the output side reduction mechanism 242, the external gears 250 and 252 are in phase with the three eccentric body shafts 294 (instead of being oscillated and rotated by the eccentric body arranged in the center as in the above embodiment). The incorporated eccentric bodies 246 and 248 rotate at the same rotational speed to rotate and rotate. The internal gear 254 is integrally fixed with the casing 256, and the relative rotation between the external gears 250 and 252 and the internal gear 254 is a revolution component around the axis O of the three eccentric body shafts 294. It is taken out from the output flange (output member) 236. The output flange 236 is integrated with the output shaft 232 in the circumferential direction via the spline portion 292, and is integrated with the output shaft 232 in the axial direction via a pressing plate 297 and a pressing bolt 298. In this example, as in the embodiment of FIG. 4, the output pinion 224 is formed integrally with the output shaft 232. Therefore, the spherical roller bearing 270, the bearing housing 276, the bushing 282, and the oil seal 284 are incorporated into the output shaft 232 from the motor side of the output pinion 224.

  Since the other configuration is basically the same as that of the embodiment already described, the same reference numerals are given to the same two or more parts having the same or the same function in the drawing, and the redundant description is omitted.

  Thus, in the present invention, the configuration of the speed reduction mechanism is not particularly limited. For example, the present invention can also be applied to a reduction gear G3 with an output pinion having a reduction mechanism as shown in FIG.

  The reduction gear G3 with an output pinion decelerates the rotation of the electric motor Mo by a total of four simple planetary gear reduction mechanisms 340 to 343, and rotates the rotation of the output member 336 at the final stage via the spline part 392. It is configured to transmit to 332. The configuration of the sub-assembly around the output shaft 332 and the method of assembling the output shaft 332 are basically the same as those in the previous embodiments, although there are some differences in shape and the number of oil seals 384. . Therefore, the same reference numerals are given to the same two or more parts having the same function in the drawing, and the duplicated explanation is omitted.

  In the above embodiment, a swivel internal gear having “internal teeth” is exemplified as a gear of the wind power generation system. However, in the present invention, the gear has “external teeth” and an output pinion is It can be similarly applied to a power transmission device circumscribing the gear. Moreover, in the said embodiment, although the output side casing was comprised by the integral object, in this invention, the output side casing does not necessarily need to be an integral object. Furthermore, in the above-described embodiment, an example in which the present invention is applied to a power transmission device for yaw drive of a wind power generation system is shown. However, application of the present invention is applicable to a power transmission device for yaw drive of a wind power generation system. However, the present invention is not limited thereto, and can be applied to, for example, a power transmission device for pitch driving of a wind turbine blade of a wind turbine system.

  The present invention is an output for yaw drive used as a speed reducer with a pinion for pitch drive for changing the angle of a windmill blade in a wind power generation system, or for directing a power generation unit, for example, in an optimum recovery direction at that time. It can be suitably applied as a reduction device with a pinion.

DESCRIPTION OF SYMBOLS 10 ... Wind power generation system 12 ... Power generation unit 14 ... Drive device for yaw drive 16 ... Drive device for pitch drive 18 ... Nose cone 20 ... Windmill blade 24 ... Output pinion 28 ... Turning internal gear 32 ... Output shaft 34 ... Deceleration Mechanism 40 ... Input-side reduction mechanism 42 ... Output-side reduction mechanism 44 ... Input shaft of output-side reduction mechanism 70 ... Self-aligning roller bearing (drive source side bearing)
72 ... Roller bearing (anti-drive source side bearing)
74 ... Output side casing 74A ... Cover part 74D ... Mating window 74D1 ... Opening 74E ... Holding hole 76 ... Bearing housing 79 ... Inner ring d1 ... Outer diameter of output pinion d2 ... Outer diameter of bearing housing G1-G4 ... Reduction gear with output pinion L1: Axial dimension of opening of meshing window Mo: Electric motor

Claims (7)

A speed reduction mechanism for reducing the rotation of the drive source, an output shaft connected to or integrated with an output member of the speed reduction mechanism, and an output pinion provided on the output shaft and meshable with a gear of a wind power generation system A reduction device with a pinion of a wind power generation system,
The output shaft is supported at both ends by a pair of bearings on the drive source side and the counter drive source side,
Both of the pair of bearings are accommodated in an output casing having a meshing window for meshing the output pinion with the gear on a part of the outer periphery,
Of the pair of bearings, the rolling element of the bearing on the counter drive source side is constituted by a plurality of rollers that rotate but do not revolve,
A speed reducer with an output pinion for a wind power generation system, wherein no roller is disposed on the side of the meshing window. In claim 1,
A speed reducer with an output pinion for a wind power generation system, wherein a width dimension in a direction perpendicular to an axis of the opening of the meshing window is smaller than an outer diameter of the output pinion. In claim 1 or 2,
The output-side casing is integrally formed of a single member including a cover portion on the side opposite to the driving source of the output shaft. A speed reducer with an output pinion for a wind power generation system. In any one of Claims 1-3,
A reduction gear with an output pinion for a wind power generation system, wherein an outer ring of the bearing on the counter driving source side is constituted by the output casing. In claim 4,
A speed reducing device with an output pinion for a wind power generation system, wherein a holding hole for holding the roller is formed integrally with the output side casing. In any one of Claims 1-3,
The outer ring of the bearing on the side opposite to the driving source is constituted by a member independent of the output side casing, and the portion on the circumferential meshing window side of the outer ring is made thicker as the roller is omitted. A speed reducer with an output pinion for a wind power generation system. In any one of Claims 1-6,
The speed reducing device with an output pinion for a wind power generation system, wherein the bearing on the counter driving source side includes an inner ring.

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