JP5295880B2 - Reducer for pitch drive of wind power generation - Google Patents

Description

  The present invention relates to a pitch drive speed reduction device for wind power generation.

  According to Patent Document 1, a speed reduction device 1 for wind power generation as shown in FIG. 9 is shown. The hollow rotor head 2 of the windmill is rotatably supported by a windmill body (not shown). The pitch wind turbine blade 3 is rotatably connected to the rotor head 2. A pitch driving speed reducer 1 is connected to the radially inner end of the pitch wind turbine blade 3. The speed reduction device 1 is configured such that the rotation of the drive source 4 is reduced by the speed reduction mechanism unit 5 and output from an output pinion 6 connected to an output shaft (not shown) of the speed reduction mechanism unit 5. An internal gear 7 that meshes with the output pinion 6 of the reduction gear 1 is formed on the inner periphery of the inner end portion in the radial direction of the windmill blade 3. The reduction gear 1 is filled with a lubricant in order to prevent wear of its own parts.

Japanese Patent Laying-Open No. 2005-9373 (Claim 1, paragraphs [0013] and [0014], FIG. 1)

  However, in the case of a pitch drive speed reducer for wind power generation, an unexpectedly large load is applied from the output side of the speed reducer due to wind force such as gusts and typhoons, and this large load may reach the speed reducer as a result. . As one of the countermeasures, a float is provided between the output shaft of the drive source and the input shaft of the speed reduction mechanism to absorb the impact caused by the heavy load and flexibly allow the displacement between the two shafts. Concatenation is adopted. Since the speed reducer for pitch drive is oriented in various directions, the speed reducer has been lubricated with grease from the viewpoint of preventing lubricant leakage. However, when the rotational movement of the windmill is performed, the rattle of the float connecting portion may cause a minute slide between both shafts, which may cause fretting wear.

  The present invention has been made in view of such fears, and it is a wind power generation pitch that can prevent fretting wear at the connecting portion of the drive source side shaft and the input shaft of the speed reduction mechanism while suppressing leakage of the lubricant. It is an object of the present invention to provide a drive speed reduction device.

  The present invention relates to a pitch drive speed reduction device for wind power generation, and includes a drive source for the speed reduction device and a speed reduction mechanism portion for reducing the rotation of the drive source, and the speed reduction mechanism portion is lubricated with grease. A portion where the shaft on the drive source side and the input shaft of the speed reduction mechanism portion are fastened by a float connection that is connected to each other while having a radial radial relation, and the float connection is made The above problem is solved by adopting a structure lubricated with oil sealed in a sealed space.

  In the present invention, it is fastened by “a float connection in which the shaft on the drive source side and the input shaft of the speed reduction mechanism portion are connected to each other while having a relative radial play”, Is lubricated with oil sealed in a sealed space. The present invention employs grease lubrication for a reduction mechanism portion that transmits high torque other than the “float connected portion” because of its use (pitch drive of wind power generation), and (need to transmit such a high torque) “Float joint” is “oil lubrication sealed in a sealed space”. As a result, “suppression of lubricant leakage” and “prevention of fretting wear”, which are in a trade-off relationship with the application, are effectively realized at the same time. In other words, “oil” is softer than grease and almost liquid, so it can fully penetrate into the narrow part of the “float connected part” and improve the lubricity between both shafts. As a result, fretting wear occurring between the two shafts can be prevented. Further, since oil is only used in a float-connected part (with a small volume), sealing is easy and the possibility of oil leakage is extremely low. In addition, even if all the oil leaks, it is not a large amount, and in addition, the float-connected part can continue to transmit the power itself to the speed reduction mechanism without any trouble by mechanical connection. Since the speed reduction mechanism is reliably lubricated with grease (which is unlikely to leak), sufficiently safe and smooth continuous operation can be maintained. As a result, it is possible to prevent fretting of the float-connected portion while minimizing the leakage of the lubricant and maintaining safety.

  According to the present invention, it is possible to provide a pitch driving speed reduction device for wind power generation that can prevent fretting wear at the connecting portion between the drive source side shaft and the input shaft of the speed reduction mechanism while suppressing leakage of the lubricant. it can.

The longitudinal cross-sectional view of the speed reduction device for pitch drive of the wind power generation concerning an example of embodiment of this invention Enlarged view of arrow II in Fig. 1 The longitudinal cross-sectional view of the speed reducer for the pitch drive of the wind power generation concerning an example of 2nd Embodiment of this invention The longitudinal cross-sectional view of the speed reduction device for the pitch drive of the wind power generation concerning an example of 3rd Embodiment of this invention The longitudinal cross-sectional view of the speed reduction device for pitch drive of the wind power generation concerning an example of other embodiment of this invention The perspective view which shows the outline of the electric power generation unit in a wind power generation system Longitudinal section of the rotor head of the power generation unit in the wind power generation system Enlarged view of arrow VIII in FIG. Reduction gear used for pitch drive device of conventional wind power generator

  In order to clarify the application of the reduction gear G1, the pitch drive device 401 of the wind power generator will be described for convenience.

  FIG. 6 is a perspective view showing an outline of the power generation unit 402 in the wind power generation system. FIG. 7 shows a schematic side view of a wind power generation system in which the reduction gear G1 according to the above embodiment is incorporated, and FIG. 8 shows an enlarged view of a portion indicated by an arrow VIII in FIG.

  In the present embodiment, the present invention is applied to the reduction gear G1 of the pitch driving device 401. A hollow rotor head 404 used for wind power generation is supported by a power generation unit 402 (nacelle) so as to be rotatable about a substantially horizontal rotation axis. Since this rotor head 404 is connected to a speed increaser and a generator (not shown), (rotary wind) power is generated by the rotation of the rotor head 404.

  The rotor head 404 has a windmill blade 414 in its circumferential direction (see FIG. 7). The radially inner ends of the wind turbine blades 414 are rotatably connected to the rotor head 404 via bearings 408. Further, the wind turbine blade 414 has a large number of internal teeth 410 formed on the inner periphery thereof, constitutes a turning internal gear 412, and is also used as an inner ring of the bearing 408.

  The same number of pitch driving devices 401 as wind turbine blades 414 are attached to the rotor head 404. The pitch driving device 401 is mainly composed of a turning internal gear 412 that meshes with the driving source (motor) 16, the speed reduction mechanism unit 18, and the output pinion 20. The pitch driving device 401 drives the motor 16 to rotate the output pinion 20 while reducing the rotational power by the speed reduction mechanism unit 18. The output pinion 20 meshes with the turning internal gear 412 and can transmit rotational power to the wind turbine blade 414. Thereby, the pitch angle of the windmill blade 414 with respect to the rotor head 404 can be changed, the windmill blade 414 can be directed in a desired direction, and wind pressure can be received efficiently.

  However, since the windmill blade 414 described above is easily subjected to wind pressure, it may be subjected to a large load during a strong wind. Such an excessive load is transmitted to the inside of the reduction gear G1 via the turning internal gear 412 and the output pinion 20, and the rotation shaft (motor-side shaft (drive-source-side shaft) 30 or the input shaft of the speed reduction mechanism unit 18). 32, etc.) may be greatly bent or deformed, and the speed reduction device G1 may be damaged.

  In order to cope with this deformation, the shaft 30 on the motor side and the input shaft 32 of the speed reduction mechanism portion 18 are not firmly connected, and “a relatively small amount of radial movement is allowed between the shafts 30 and 32. Are connected ”(hereinafter referred to as“ float connection ”). Thereby, the misalignment etc. which arise between both the shafts 30 and 32 can be absorbed, and the reduction gear G1 can be used continuously.

  However, with the adoption of this float connection, both shafts 30 and 32 repeat axial reciprocation, vibration, and the like as the windmill rotates. As a result, fretting wear may occur between the shafts 30 and 32.

  Here, from the relationship with the application (rotary motion of the windmill), the specific problems of the lubricant used in the speed reducer G1 for driving the pitch are summarized. When the speed reducer G1 is grease lubricated, there is leakage compared to oil lubrication. Instead of being less likely to occur, fretting wear is likely to occur. On the other hand, when the reduction gear G1 is oil lubricated, fretting wear can be prevented, but oil leakage is likely to occur. That is, in the pitch drive reduction gear G1, the relationship between the suppression of lubricant leakage and the prevention of fretting wear is a trade-off relationship in which if one is pursued, the other must be sacrificed. ing.

  Therefore, in this embodiment, the reduction gear G1 and the lubricant are configured such that the part where the float connection is made is lubricated with oil sealed in a sealed space, and the other part is lubricated with grease. Yes. This will be described in detail below.

  FIG. 1 shows a longitudinal sectional view of a reduction gear G1 according to an embodiment of the present invention. FIG. 2 shows an enlarged view indicated by an arrow II in FIG.

  First, the structure of the reduction gear G1 will be described.

  The rotation of the motor 16 provided in the speed reduction device G1 is decelerated by the speed reduction mechanism portion 18 of the speed reduction device G1 and is output from the output pinion 20 connected to the output shaft 48 of the speed reduction mechanism portion 18.

  As described above, the motor-side shaft 30 and the input shaft 32 of the speed reduction mechanism unit 18 are float-connected. The float connecting portion 36 has a spline structure. A brake 85 is provided on the load side of the motor 16 with respect to a motor shaft (not shown). In this embodiment, since the brake 85 is provided on the load side of the motor 16, the output shaft of the brake 85 corresponds to the shaft on the drive source side. The brake 85 has the same structure as a brake 285 described later (not shown in FIG. 1; details will be described later with reference to FIG. 4).

  The float connecting portion 36 and the speed reduction mechanism portion 18 are disposed inside the cover 46. The cover 46 includes an upper cover 38, a lower cover 44, a first casing 40, and a second casing 42.

  The configuration of the deceleration mechanism unit 18 will be described.

  The reduction mechanism unit 18 includes a so-called distribution type inscribed mesh planetary gear type reduction mechanism.

  As described above, the input shaft 32 of the speed reduction mechanism unit 18 is float-connected to the motor-side shaft 30. A spur pinion 41 is fixed to the input shaft 32 of the speed reduction mechanism unit 18, and three (only one is shown) spur gears 39 are engaged with the spur pinion 41. The three (only one) eccentric body shafts 50 are rotated by the three spur gears 39, respectively. The eccentric bodies 52 and 54 are incorporated in a state of being eccentric with respect to the respective eccentric body shafts 50. The eccentric bodies 52 and 54 have an eccentric phase of 180 degrees. The external gears 56 and 58 are fitted into the eccentric bodies 52 and 54 via the rollers 61 and 62. The external gears 56 and 58 are in mesh with the internal gear 60. The internal teeth of the internal gear 60 are constituted by cylindrical outer pins attached to the first and second casings 40 and 42. The number of internal teeth (the number of external pins) of the internal gear 60 is one more than the number of external teeth of the external gears 56 and 58.

  The eccentric body shaft 50 is rotatably supported by the first and second flange bodies 68 and 70 via roller bearings 64 and 66. The first and second flange bodies 68 and 70 are connected by a bolt 72. The first flange 68 is rotatably supported by a bearing 74 provided between itself and the first casing 40. The input shaft 32 of the speed reduction mechanism 18 is rotatably supported by bearings 95 (95A and 95B), and the output shaft 48 is rotatably supported by a bearing 71.

  Here, a lubricant and a mechanism for preventing leakage of the lubricant will be described.

  The float connecting portion 36 is lubricated with oil.

  The upper cover 38, the first casing 40, and the oil seals 96 </ b> A, 96 </ b> B, and 99 form a sealed space that becomes the oil reservoir 97, and the oil is enclosed in the oil reservoir 97.

  More specifically, the pair of oil seals 96 </ b> A and 96 </ b> B are provided in the oil seal placement portion 96 provided on the load side (the speed reduction mechanism portion 18 side) of the oil reservoir 97 and on the anti-load side of the bearing 95. It is disposed between the casing 40 and a bush 33 provided on the input shaft 32 of the speed reduction mechanism section 18. On the other hand, the oil seal 99 is disposed between the motor-side shaft 30 and the upper cover 38 on the anti-load side (motor 16 side) of the oil reservoir 97. Accordingly, the upper cover 38, the first casing 40, and the oil seals 96A, 96B, and 99 can form a space for sealing the oil in the oil reservoir 97.

  The volume of the oil reservoir 97 is preferably larger than the volume of the float coupling part 36 of the input shaft 32 and less than 3 times.

In the present embodiment, when the diameter of the input shaft 32 (pitch circle diameter in the case of a spline) is D and the length with which both the shafts 30 and 32 are fastened is Y, the float coupling portion 36 is used. Is πD ² Y / 4 (see FIG. 2).

  In the present embodiment, the volume of the oil reservoir 97 is about 1.3 times the volume of the float connecting portion 36.

  Oil is supplied from an oil supply port 93 attached to the side surface of the first casing 40. The oil supply port 93 is a through hole with a cap.

  On the other hand, the bearings 92 (92A, 92B) that support the inside of the speed reduction mechanism 18 and the shaft 30 on the motor side are lubricated with grease. As grease for lubricating the bearing 92, grease having a consistency number of 2 (concentration: 265 to 295) is used. This grease is filled in the speed reduction mechanism 18 and the bearings 92 (92A, 92B).

  The first casing 40, the second casing 42, and the oil seals 96 and 94 (94 </ b> A and 94 </ b> B) form a sealed space that becomes the grease reservoir 98, and the grease is sealed in the grease reservoir 98.

  The oil seal 94 and the grease reservoir 98 are provided on the load side of the speed reduction mechanism 18.

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

  In the speed reduction mechanism 18, the eccentric gears 52, 54 incorporated in the three eccentric shafts 50 in the same phase rotate at the same rotational speed at the same time, so that the external gears 56, 58 swing and rotate.

  In this embodiment, since the internal gear 60 is fixed to the first and second casings 40 and 42, the rotation of the input shaft 32 of the speed reduction mechanism unit 18 is transmitted to the eccentric body shaft 50 via the spur pinion 41 and the spur gear 39. When the eccentric body shaft 50 is transmitted once and rotated, the external gears 56 and 58 swing once and the meshing position with the internal gear 60 is shifted by one tooth (by the difference in the number of teeth). As a result, the external gears 56 and 58 rotate relative to the internal gear 60 by an angle corresponding to the difference in the number of teeth. The relative rotation between the external gears 56 and 58 and the internal gear 60 is extracted from the second flange 70 as a revolution component around the axis of the three eccentric body shafts 50. Since the second flange 70 is integrated with the output shaft 48 in the rotation direction, the output pinion 20 can be rotated via the output shaft 48 to output power from the reduction gear G1. Thereby, the pitch angle of the windmill blade 414 can be changed by this rotational power, and the windmill blade 414 can be directed in a desired direction (angle).

  Even if an excessive load is applied, the float coupling portion 36 can absorb the deviation between the shaft centers of the motor-side shaft 30 and the input shaft 32 of the speed reduction mechanism portion 18 satisfactorily.

  Next, the operation of the mechanism for preventing the lubricant and the lubricant from leaking will be described.

  The float connecting portion 36 is lubricated with oil. Since oil has a lower viscosity than grease, it can enter a finer gap, and can evenly cover the meshing portion (the surface on which the motor-side shaft 30 and the input shaft 32 of the speed reduction mechanism 18 mesh). . Specifically, the oil enters the gap between the female spline portion of the motor-side shaft 30 and the male spline portion of the input shaft 32 of the speed reduction mechanism 18, and forms an oil film between the shafts 30 and 32. , Fretting wear can be prevented (details above).

  The oil is enclosed in an oil reservoir 97 formed by the upper cover 38, the first casing 40, and oil seals 96 </ b> A, 96 </ b> B, 99.

  On the load side of the oil reservoir 97 (the speed reduction mechanism 18 side of the oil reservoir 97), a pair of oil seals 96A and 96B are disposed facing each other (each lip portion facing in the opposite direction). As a result, oil leakage that occurs from the oil reservoir 97 to the inside of the speed reduction mechanism portion 18 and grease leakage that occurs from the inside of the speed reduction mechanism portion 18 to the oil reservoir portion 97 can be prevented.

  Further, since the oil seal 99 is disposed on the anti-load side (motor 16 side) of the oil reservoir 97 and the bearing 92 is lubricated with grease, the space inside the oil reservoir 97 and the brake 85 is provided. Can be partitioned. Therefore, it is possible to prevent oil from leaking from the oil reservoir 97 to the brake 85 side.

  Since the bearing 92 is lubricated with grease, combined with the effect of the oil seal 99, the risk of oil leaking from the oil reservoir 97 to the brake 85 side can be further reduced.

  The volume of the oil reservoir 97 is not less than three times the volume of the float coupling portion 36 and less than three times, and is not too large and not too small to form a highly reliable sealed space. Not only can the portion 36 be sufficiently lubricated to keep deterioration to a minimum, but also early deterioration of the oil can be prevented.

  Even if all the oil flows out of the float connecting part 36, the amount is less than three times the volume of the float connecting part 36 and is not an amount that affects the safety of the continuous operation of the reduction gear G1. In addition, since power transmission in the spline connection structure is not immediately disabled (only fretting is likely to occur), the operation of the reduction gear G1 can be continued without any problem.

  In general, oil is more likely to leak from the sealed space to the outside than grease, so that the cost of sealing the oil is higher than when sealing the grease. For this reason, if the lubrication part by oil increases, the seal cost cost of the whole apparatus will rise correspondingly. In this respect, since the reduction gear G1 uses only the float coupling portion 36 as oil lubrication, the cost of the seal can be suppressed and oil leakage can be prevented at a low cost.

  On the other hand, the parts other than the float coupling part 36 are lubricated with grease having higher viscosity than oil including the speed reduction mechanism part 18 and the grease whose viscosity has been lowered due to deterioration due to long-term use is a grease reservoir part. It is stored in 98. For this reason, even if the speed reducer G1 turns in various directions as the rotor head 404 rotates, the grease is less likely to leak from the speed reduction mechanism 18 to the oil reservoir 97 or the external space.

  That is, the lubricant (oil, grease) inside the reduction gear G1 is difficult to leak from the reduction gear G1 to the external space as a whole.

  In this embodiment, since the brake 85 is provided on the load side of the motor 16, the shaft 30 on the motor side does not have to bear the brake torque, which is preferable in terms of torque transmission.

  From the above, it is possible to provide a safe wind-powered pitch driving speed reduction device G1 that can prevent fretting wear of the motor-side shaft 30 and the input shaft 32 of the speed reduction mechanism 18 while suppressing oil leakage at low cost. .

  Next, another embodiment will be described.

  FIG. 3 shows a cross-sectional view of a reduction gear G2 according to another embodiment.

  The speed reduction device G2 according to the present embodiment is also substantially the same as the speed reduction device G1 (FIG. 1) described above, and therefore, the members having the same or similar functions are given the same reference numerals in the lower two digits as the speed reduction device G1. The duplicated explanation is omitted.

  Also in this embodiment, the oil is filled in the oil reservoir 197 formed by the upper cover 138, the first casing 140, and the oil seals 196 (196A, 196B), 199, and the float connecting portion 136 is lubricated by the oil. Has been. On the other hand, the speed reduction mechanism 118 and the like other than the float connecting portion 136 are lubricated with grease. As a result, as in the above-described embodiment, it is possible to prevent the fretting wear of the motor-side shaft 130 and the input shaft 132 of the speed reduction mechanism 118 while suppressing the lubricant leakage at a low cost and safely. A reduction gear G2 can be provided.

  In the present embodiment, not only the oil seal 196 but also the bearing 195 is disposed between the inner periphery of the hole into which the input shaft 132 of the first casing 140 is inserted and the input shaft 132. The thickness T of the one casing 140 on the motor 116 side is increased, and a deep oil reservoir 197 is formed. Thereby, the amount of oil to be filled can be increased more than the oil reservoir (97) of the reduction gear G1, and the float connecting portion 136 is sufficiently lubricated by the oil.

  In this embodiment, since the output shaft 148 of the speed reduction mechanism 118 that is longer than the output shaft (48) of the speed reduction device G1 is supported at both ends by the two bearings 171 and 173, the distance between the bearings 171 and 173 is long. Thus, the grease reservoir 198B can be provided between the bearing 171 and the bearing 173. As a result, the amount of grease that can be accommodated on the load side of the speed reduction mechanism 118 can be greatly increased.

  In addition, the shape of the first flange 168 is made simpler and the bearing (74) of the reduction gear G1 is eliminated to provide a grease reservoir 198A on the motor 116 side of the reduction mechanism 118.

  Thereby, since the whole capacity | capacitance of the grease storage part 198 (198A, 198B) becomes large compared with the reduction gear G1, the leakage of grease can be reduced more.

  Moreover, the following secondary effects can be acquired by employ | adopting said structure. In the float coupling part 136, in combination with the fact that the shaft center of the motor side shaft 130 and the input shaft 132 of the speed reduction mechanism part 118 are allowed to deviate, the distance between the bearings 171 and 173 is increased. Impact resistance against a radial load that may be input from the output shaft 148 can be further increased. Moreover, since the bearing 74 in the previous embodiment can be eliminated, the structure on the load side of the speed reduction mechanism 118 can be further simplified.

  FIG. 4 shows a cross-sectional view of a reduction gear G3 according to still another embodiment.

  Also in this embodiment, the float connecting part 236 is lubricated with oil sealed in the oil reservoir 297 (sealed space formed by the oil seals 296A, 296B, and 299), and the speed reduction mechanism part 218 is lubricated with grease. As a result, the same effects as in the above embodiment can be obtained.

  The float connecting portion 236 is configured using a coupler (dedicated shaft coupling) 265. By the fastening method of the motor-side shaft 230 and the input shaft 232 of the speed reduction mechanism 218 using the coupler 265, the space between the speed reduction mechanism portion 218 and the motor 216 can be expanded, and the volume of the oil sump portion 297 is increased. can do. In this embodiment, the amount of oil that can be filled is increased by expanding the volume of the oil reservoir 297 to three times or more than the volume of the float connecting portion 236.

  This is because in the present embodiment, the brake 285 is provided on the opposite side of the motor 216, so that even if oil leakage occurs, the degree of adverse effects is low. With this configuration, it is possible to provide a reduction gear G3 that can more easily prevent fretting wear.

  About another form, it is the same as the reduction gear G1 shown in FIG.

  The present invention can also be applied to a simple planetary gear type reduction gear G4 other than the so-called sort type reduction gears G1 to G3 described above.

  FIG. 5 shows an embodiment in which the present invention is applied to a simple planetary gear type reduction gear G4.

  The reduction gear G4 decelerates the rotation of the motor 316 by a total of four stages of simple planetary gear reduction mechanisms 318 (318A to 318D), and the rotation of the final stage flange 370 is integrated with the flange 370. It is configured to transmit to the shaft 348.

  Also in this embodiment, the float connecting portion 336 is lubricated by the oil enclosed in the oil reservoir 397 (sealed space formed by the oil seals 396A, 396B, and 399), and the speed reduction mechanism portion 318 is lubricated with grease. As a result, the same effects as in the above embodiment can be obtained.

  Further, a grease reservoir 398 (398A to 398F) is provided on the load side of the speed reduction mechanism 318 of each stage. Thereby, the function which prevents the leak of grease can be improved more.

  In addition, the kind of speed reducer which can apply this invention is not limited.

  In addition, grease having another consistency number may be used as the grease for the bearing that supports the output shaft of the brake disposed on the load side of the drive source. The consistency number is not particularly limited as long as it has a function as a speed reduction mechanism and a function of preventing leakage.

  Even if the shape of the oil reservoir is other than the shape shown in this embodiment, the shape is not particularly limited as long as it has the same effect. Further, the number of oil seals is not limited to the number in the present embodiment.

  As a fastening method of the float connecting part, spline fastening in the above embodiment, and fastening using a coupler which is a part other than the speed reducer is shown, but the float connecting part may be configured using other members, For example, it is good also as a key connection using a key.

  Further, in the above embodiment, oil lubrication is used only for the float connecting portion considered to be the best from the viewpoint of preventing leakage of the lubricant, and grease lubrication is used for all other portions. As long as grease lubrication is used for the speed reduction mechanism portion that is filled with a large amount of lubricant, the portion other than the float connecting portion may be oil lubricated.

  Note that, among the components and elements described in the embodiment, even if not particularly described, the dimensions, materials, shapes, and other relative arrangements of the components are not particularly specified, unless otherwise specified. The scope of the present invention is not intended to be limited to that.

G1 ... Deceleration device 16 ... Motor (drive source)
DESCRIPTION OF SYMBOLS 18 ... Deceleration mechanism part 30 ... Drive source side shaft 32 ... Input shaft 36 ... Float connection part (part in which float connection is made)

Claims (7)

In the speed reducer for pitch drive of wind power generation,
A drive source of the speed reducer, and a speed reduction mechanism that decelerates the rotation of the drive source,
The speed reduction mechanism is lubricated with grease;
The shaft on the drive source side and the input shaft of the speed reduction mechanism section are fastened by a float connection that is connected to each other while having a relative radial direction, and
A speed reduction device for pitch driving of wind power generation, characterized in that the portion where the float connection is made is lubricated with oil sealed in a sealed space. In claim 1,
A bearing for supporting the shaft on the drive source side is lubricated with grease. A speed reducer for pitch driving of wind power generation. In claim 1 or 2,
An input shaft of the speed reduction mechanism unit has a pinion, and the pinion is disposed in a space on the speed reduction mechanism unit side . In claim 1, further comprising:
An oil reservoir portion is provided that communicates with the portion where the float connection is made and fills oil for lubricating the portion where the float connection is made. Reducer. In claim 4,
The volume reduction of the oil pool part is larger than the volume of the part where the float connection of the input shaft is made, and is less than 3 times. In claim 4 or 5, further
It has a cover that covers the outer periphery of the speed reduction mechanism,
A bearing for supporting the input shaft of the speed reduction mechanism portion on the cover, an oil seal arrangement portion for providing an oil seal on the anti-load side of the bearing, and the oil provided on the anti-load side of the oil seal arrangement portion A speed reducer for pitch driving of wind power generation, characterized in that a reservoir is provided. In claim 6, further:
In order to prevent the leakage of the lubricant from both directions inside the oil reservoir and the speed reduction mechanism, a pair of oil seals are provided in the oil seal arrangement part,
In order to prevent oil leakage from the oil reservoir to the drive source side, an oil seal is provided on the drive source side of the oil reservoir. .

Images