JP2017044150A - Wind turbine generator system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To more reduce the breakage of constituent components of a wind turbine generator system, a yaw unit in particular.SOLUTION: A wind turbine generator system (12) comprises: a brace (14); a nacelle (16); a gyration gear (20); a first brake (18) that brakes the gyration of the nacelle without interposing the gyration gear therebetween; and n second brakes YU (n is an integer of 2 or more) that include a gyration pinion RP engaging with the gyration gear and brake the gyration of the nacelle with interposing the gyration gear therebetween by braking the revolution of the gyration pinion, in which the n second brakes include a torque limiter TL which starts sliding when an actuation start torque being the specified value or more is applied; and (A-B)-(n-1)Y<X is established in which A is regarded as an assumption largest value of an external force; B is a brake force of the first brake; X is the actuation start torque; and Y is a torque after actuation.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a wind power generation facility.

  In Patent Document 1, a support column, a nacelle that rotates with respect to the support column, a rotation gear that is provided on the support column, and a rotation pinion that meshes with the rotation gear, and braking the rotation of the rotation pinion, And four yaw units that drive and brake the turning of the nacelle via the wind turbine generator.

  In Patent Literature 1, as shown in FIG. 11, a configuration using a sliding bearing 918 is disclosed as a braking device that brakes the turning of the nacelle 916 without using the turning gear 920. Specifically, the sliding bearing 918 with a braking function is provided with first to third sliding bearing members 921A to 921C so as to surround a bearing plate 919 fixed to the support column 914 side. A predetermined braking force is obtained for the turning of the nacelle 916 (by setting the slip resistance of 918).

  In patent document 1, it is comprised so that the nacelle 916 can turn by weakening the braking force of the yaw unit 924 at the time of a power failure under strong winds.

Japanese Patent Laying-Open No. 2011-127551 (FIG. 4)

  In patent document 1, at the time of a power failure under a strong wind, the braking force is weakened so that the nacelle can turn. However, the actual situation is that damage to the yaw unit cannot be sufficiently prevented, and sometimes the yaw unit may be damaged.

  The present invention has been made to solve such a conventional problem, and an object of the present invention is to further reduce breakage of components of a wind power generation facility, particularly breakage of a yaw unit.

The present invention includes a support column, a nacelle that rotates with respect to the support column, a swivel gear provided on the support column, a first braking device that brakes the swiveling of the nacelle without using the swivel gear, and the swivel gear. And n (n is an integer greater than or equal to 2) second braking devices that brake the turning of the nacelle via the turning gear by braking the rotation of the turning pinion. The n second braking devices include a torque limiter that slides when a torque greater than or equal to a predetermined value is applied, and an estimated maximum value of an external force that attempts to turn the nacelle is A. When the braking force of the first braking device is B, the torque starting torque of the torque limiter corresponding to the predetermined value is X, and the post-operation torque transmitted after the torque limiter is operated is Y,
(AB)-(n-1) Y <X
The above-described problem is solved by adopting a configuration in which is established.

  As a result of examining and verifying the mechanism of breakage of the yaw unit, the present inventors have obtained new knowledge that cannot be handled by the conventional design concept (different from the conventional design concept). The above configuration is based on this finding (detailed later).

  Based on this knowledge, the present invention equips the n second braking devices with a torque limiter that slides when a torque greater than a predetermined value is applied. Then, paying attention to the assumed maximum value A of the external force, the braking force B of the first braking device, the number n of the second braking devices, the operation start torque X of the torque limiter of the second braking device, and the post-operation torque Y, (A− B)-(n-1) Y <X is satisfied.

  As a result, it is possible to further reduce damage to the components of the wind power generation facility, particularly damage to the yaw unit, which cannot be handled by conventional ideas.

The present invention includes a support column, a nacelle that rotates with respect to the support column, a swing gear provided on the support column, a first braking device that brakes the turning of the nacelle without using the swing gear, N (n is an integer of 2 or more) second braking devices that have a turning pinion meshing with the turning gear and brake the turning of the nacelle via the turning gear by braking the rotation of the turning pinion; The n second braking devices include a torque limiter that slides when a torque greater than or equal to a predetermined value is applied, and an assumed maximum value of an external force that attempts to turn the nacelle. A, B, the braking force of the first braking device, B, the operation start torque of each torque limiter corresponding to the predetermined value X1, X2,..., Xn, and the post-operation torque transmitted after each torque limiter is operated. , Y2, ... Yn, when Xmin is the minimum operation start torque among the operation start torques X1, X2,..., Xn, and Ymax is the maximum post-operation torque among the torques Y1, Y2,. ,
(A−B) − [(Y1 + Y2 +... + Yn) −Ymax] <Xmin
It can also be regarded as a wind power generation facility characterized by the fact that

  According to the present invention, it is possible to further reduce breakage of components of the wind power generation facility, particularly breakage of the yaw unit.

Sectional drawing which shows the structural example of the yaw unit of the wind power generation equipment which concerns on an example of embodiment of this invention. Enlarged view of the main part of the yaw unit in FIG. The schematic plan view which shows the arrangement | positioning relationship of the turning gearwheel and turning pinion in embodiment of FIG. The schematic diagram which shows the operating mode of the torque limiter of the yaw unit of FIG. FIG. 4 is a schematic diagram showing an operation mode of the torque limiter after FIG. 4 of the yaw unit of FIG. The schematic diagram which shows the operation | movement aspect of the torque limiter after FIG. 5 of the yaw unit of FIG. The schematic diagram which shows the operation | movement aspect of the torque limiter after FIG. 6 of the yaw unit of FIG. The schematic diagram which shows the operation | movement aspect of the torque limiter after FIG. 7 of the yaw unit of FIG. The schematic diagram which shows the operation | movement aspect of the torque limiter of the yaw unit of the wind power generation equipment which concerns on the other example of embodiment of this invention. Schematic side view showing the entire wind power generation facility of FIG. Schematic cross-sectional view of the main part showing the configuration in the vicinity of the yaw unit and swivel gear of a conventional wind power generation facility

  Hereinafter, a wind power generation facility according to an example of an embodiment of the present invention will be described in detail based on the drawings.

  First, the schematic configuration of the wind power generation facility 12 will be described.

  FIG. 10 is a schematic side view showing the entire wind power generation facility 12. 1 is a cross-sectional view showing a configuration example of a yaw unit YU of a wind power generation facility 12 according to an example of an embodiment of the present invention, FIG. 2 is an enlarged view of a main part thereof, and FIG. It is a schematic plan view which shows the arrangement | positioning relationship between the turning gear 20 (axial center C20) and turning pinion RP (RP1-RP4) in FIG.

  As shown in FIG. 10, the wind power generation facility 12 of the present embodiment includes a support column 14 and a nacelle 16 that is pivotably assembled to the support column 14. The nacelle 16 is rotatably assembled to the support column 14 via a sliding bearing 18 having a braking function.

  The sliding bearing 18 corresponds to the “first braking device” in the present embodiment. Here, the first braking device means “a braking device that brakes the turning of the nacelle without using a turning gear”.

  When the “sliding bearing 18 having a braking function” is employed as the first braking device, specifically, for example, the configuration described in Patent Document 1 already described with reference to FIG. 11 can be employed. The generated braking force can be adjusted by selecting the material of the bearing plate (919) and the first to third sliding bearing materials (921A to 921C). Further, for example, a mechanism for adjusting the pressing force of the sliding bearing material against the bearing plate by adjusting the compression amount of the spring to make the braking force variable may be provided. The braking force generated by the sliding bearing 18 always acts regardless of whether the nacelle 16 is turning or braking (when stationary).

  In addition, the support mechanism of the nacelle 16 does not necessarily need to be comprised with a sliding bearing, for example, you may comprise with a rolling bearing. Even if it is a rolling bearing, since there is always a turning resistance, it can function as a “first braking device that brakes turning of the nacelle without using a turning gear”.

  The support column 14 is provided with a swivel gear 20, and the nacelle 16 incorporates a yaw unit YU as shown in FIGS. 1 and 2. The yaw unit YU corresponds to the “second braking device” in the present embodiment. Here, the second braking device means “a device that has a turning pinion meshing with the turning gear and brakes the turning of the nacelle via the turning gear by braking the rotation of the turning pinion”.

  As shown in FIG. 3, in the wind power generation facility 12, four yaw units YU (YU1 to YU4) are provided for the turning gear 20. That is, n = 4. n is an integer of 2 or more. All four yaw units YU have the same configuration. The yaw unit YU has a turning pinion RP that externally meshes with the revolving gear 20 (may be inscribed meshing).

  As shown in FIG. 3, the four yaw units YU are not equally spaced in the circumferential direction. However, the arrangement of the yaw units YU is not necessarily limited to the arrangement shown in FIG. 3. For example, the yaw units YU may be arranged such that the circumferential intervals between the yaw units YU are the same, or all the yaw units YU1. YU4 may be collected and arranged on the rear side of the nacelle 16 (on the side opposite to the blade 17).

  Hereinafter, a specific configuration of the yaw unit YU will be described with reference to FIGS. 1 and 2.

  Each yaw unit YU includes a motor 2, a speed reduction mechanism 4, and a braking mechanism 6, and a turning pinion RP is provided on an output shaft of the speed reduction mechanism 4 (specifically, a later-stage output shaft 51 described later). Yes. The yaw unit YU can turn the nacelle 16 and can brake the nacelle 16. The yaw unit YU further includes a torque limiter TL that slides when a torque greater than a predetermined value is applied.

  The motor 2 of the yaw unit YU is a three-phase induction motor in the present embodiment. Since the induction motor has essentially “slip”, the torques are automatically distributed by simultaneously driving the motors 2 of the four yaw units YU. The turning pinion RP can be driven with almost the same load. The motor may be a servo motor with a brake.

  The braking mechanism 6 of the yaw unit YU is provided on the non-load side of the motor shaft 12 </ b> A of the motor 2 in the wind power generation facility 12. The braking mechanism 6 includes a coil 24 fixed to the motor casing 22, a movable plate 26 that is fixed to the motor casing 22 in the circumferential direction and is movably incorporated in the axial direction, and the movable plate 26 on the non-coil side. And a brake hub 32 integrated with the motor shaft 12A via a key 66, and a plate 34 fixed to the motor casing 22 side.

  When the motor 2 is not driven (when the coil 24 is not energized), the movable plate 26 is pressed against the brake hub 32 side by the spring 28 and strongly holds the brake hub 32 together with the plate 34 to rotate the motor shaft 12A. Restrained (braking). When the motor 2 is driven, the movable plate 26 is attracted to the coil 24. As a result, braking is released and the motor shaft 12A is allowed to rotate.

  Braking by the braking mechanism 6 is performed on-off in conjunction with driving of the motor shaft 12A. That is, the brake mechanism 6 is a non-excitation operation type brake device that restrains the rotation of the motor shaft 12A except when the motor 2 is actively operated to turn the nacelle 16. Since the motor shaft 12A is linked to the turning pinion RP so that power can be transmitted, the turning pinion RP can be braked by braking the motor shaft 12A.

  The reduction mechanism 4 of the yaw unit YU includes a two-stage front-stage reduction mechanism 44 composed of a hypoid gear set 40 and a parallel shaft gear set 42, and an eccentric oscillating type rear-stage reduction mechanism capable of obtaining a high reduction ratio in one stage. 46 (specific configuration is not shown).

  The torque limiter TL of the yaw unit YU is interposed between the joint shaft 52 integrated with the front output shaft 50 of the front speed reduction mechanism 44 and the rear input shaft 56 of the rear speed reduction mechanism 46.

  The torque limiter TL includes a support member 58 (first member) that rotates integrally with the joint shaft 52 (first shaft), and a friction plate member that rotates integrally with the rear input shaft 56 (second shaft) of the rear speed reduction mechanism 46. 60 (second member), a pressing mechanism 62 that presses the support member 58 and the friction plate member 60, and an adjustment mechanism 64 that adjusts the pressing force of the pressing mechanism 62.

  More specifically, the support member 58 that rotates integrally with the joint shaft 52 is integrally formed radially outward from the cylindrical portion 58A that is externally fitted to the joint shaft 52 and the end of the cylindrical portion 58A on the rear input shaft 56 side. And an extended plate portion 58 </ b> B that is extended.

  The cylindrical portion 58 </ b> A of the support member 58 is integrated with the joint shaft 52 in the circumferential direction via the key 66. The cylindrical portion 58 </ b> A is restricted from moving toward the rear input shaft 56 in the axial direction with respect to the joint shaft 52 by a washer 68 and a bolt 70. In the cylindrical portion 58A, the end portion 58A1 on the axially opposite rear input shaft side is in contact with the end portion 50E on the rear input shaft 56 side on the front output shaft 50, and the axially opposite rear input shaft side with respect to the joint shaft 52 is located. It is restricted to move.

  On the other hand, the rear input shaft 56 of the rear stage reduction mechanism 46 is integrated with the base plate 74 via the spline 72. The base plate 74 includes a disk-shaped plate portion 74A and a rising portion 74B bent from the outer peripheral portion of the plate portion 74A to the joint shaft 52 side.

  The friction plate member 60 is integrated with the base plate 74 and bolts 76 at the rising portion 74B. As a result, the friction plate member 60 rotates integrally with the rear input shaft 56 of the rear speed reduction mechanism 46 via the base plate 74. The friction plate member 60 is positioned on the side opposite to the axial input shaft side of the extending plate portion 58 </ b> B of the support member 58 and faces the support member 58 that rotates integrally with the joint shaft 52.

  The pressing mechanism 62 that presses the support member 58 and the friction plate member 60 is moved along the axial direction of the joint shaft 52 to be able to press the friction plate member 60, and the movable plate 80 is axially anti-frictioned. A disc spring 82 that is pressed from the plate member side and a receiving member 84 that receives a reaction force of the pressing force of the disc spring 82 are provided. The friction plate member 60 is sandwiched between the extending plate portion 58 </ b> B of the support member 58 and the movable plate 80, and is in frictional contact with the support member 58 and the movable plate 80.

  The adjustment mechanism 64 that adjusts the pressing force by the pressing mechanism 62 includes an adjustment bolt 86 that can adjust the axial position of the receiving member 84 and a fixing plate 88 that has a female screw 88A into which the adjustment bolt 86 is screwed. The axial position of the receiving member 84 can be adjusted by adjusting the screwing position of the adjusting bolt 86 with respect to the female screw 88A, and the pressing force of the disc spring 82 of the pressing mechanism 62 can be adjusted. Thereby, the operation start torque X at which the torque limiter TL starts (slides) can be adjusted. Further, the post-operation torque Y transmitted after the torque limiter TL is operated in conjunction with the adjustment of the operation start torque X can be indirectly adjusted.

  The turning pinion RP of the yaw unit YU is provided on the rear output shaft 51 of the rear stage reduction mechanism 46 via the spline 53, the bolt 55, and the plate 57, and meshes with the turning gear 20 fixed to the support column 14 side. (See FIGS. 1 and 3).

  Next, the casing of the yaw unit YU will be described.

  The motor casing 22 of the motor 2 is connected to the front casing 92 of the front speed reduction mechanism 44 via the joint casing 90. An O-ring 93 is disposed between the joint casing 90 and the front casing 92.

  The front casing 92 of the front speed reduction mechanism 44 includes a bottomed cylindrical main body 94 having an opening 94A on a side surface, and a lid body 96 that closes the opening 94A. The main body portion 94 and the lid portion 96 of the front casing 92 are connected by a bolt 98. A space between the main body portion 94 and the lid portion 96 is sealed with an O-ring 100. The main body portion 94 and the lid body portion 96 form a front-stage accommodation space SP1 of the front-stage speed reduction mechanism 44. The main body portion 94 and the lid body portion 96 are penetrated by the front output shaft 50 of the front speed reduction mechanism 44. An oil seal 102 is disposed between the front output shaft 50 and the main body 94, and an oil seal 103 is disposed between the front output shaft 50 and the lid body 96. The front housing space SP <b> 1 is sealed by the main body 94 and the lid body 96, the front output shaft 50, O-rings 93 and 100, and oil seals 102 and 103.

  The main body portion 94 and the lid body portion 96 of the front stage reduction mechanism 44 are connected to the first joint plate 106 by through bolts 104. The first joint plate 106 is connected to the limiter casing 110 of the torque limiter TL via the joint bolt 108.

  The limiter casing 110 forms a limiter accommodating space SP3 for the torque limiter TL. The limiter casing 110 is connected to the second joint plate 114 by a connecting bolt 112. The second joint plate 114 is connected to the rear casing 118 of the rear reduction mechanism 46 via the rear bolt 116. A rear housing space (SP 2) is formed in the rear casing 118 in the rear deceleration mechanism 46.

  In the rear casing 118, the rear input shaft 56 of the rear speed reduction mechanism 46 penetrates. A bush 120 and an oil seal 122 are interposed between the rear casing 118 and the rear input shaft 56. The rear housing space SP2 of the rear speed reduction mechanism 46 is sealed by a rear casing 118, a rear input shaft 56, a bush 120, an oil seal 122, and the like.

  The front housing space SP1 of the front speed reduction mechanism 44 and the limiter housing space SP3 of the torque limiter TL are partitioned by an oil seal 102 disposed between the main body portion 94 of the front speed reduction mechanism 44 and the front output shaft 50. The limiter housing space SP3 of the torque limiter TL and the rear housing space SP2 of the rear speed reduction mechanism 46 are partitioned by a rear casing 118, a rear input shaft 56, a bush 120, and an oil seal 122.

  Lubricant is sealed in the front housing space SP1 and the rear housing space SP2, but no lubricant is sealed in the limiter housing space SP3. That is, the torque limiter TL is a dry torque limiter.

  The wind power generation facility 12 according to the present embodiment is designed on the basis of newly obtained knowledge as a result of examining and verifying the mechanism of breakage of the yaw unit YU.

  This knowledge is summarized as follows.

  [Knowledge 1] When each yaw unit YU drives the turning pinion RP by the driving force of the motor 2 to turn the nacelle 16, the turning pinion RP of each yaw unit YU transmits torque to the turning gear 20. Are consistent. The variation in the torque of each yaw unit YU is small, and each yaw unit YU contributes to the turning of the nacelle 16 together.

  [Knowledge 2] However, when the motor 2 stops and the yaw unit YU enters a braking state, an external force (wind force) is input to each yaw unit YU from the nacelle 16 side by wind force. At this time, the load borne by each yaw unit YU tends to vary greatly compared to when the nacelle 16 is turned by the motor 2.

  [Knowledge 3] When the torque limiters TL of all the yaw units YU are operated (slid) and the nacelle 16 starts continuous turning, the load received by each yaw unit YU varies greatly. In addition, immediately after all the torque limiters TL have started to slide (immediately after the nacelle 16 starts continuous turning), the direction of the load received by each yaw unit YU becomes uneven, or in a specific yaw unit YU. In some cases, a larger load may be applied than when stationary.

  [Knowledge 4] The total load of the external force (wind force) input to each yaw unit YU from the swivel gear 20 side of the nacelle 16 can withstand if all the yaw units YU receive the load equally. Level (almost never large enough that all yaw units YU cannot withstand even loads).

  The above [Knowledge 3] is a completely different concept from the concept of the conventional knowledge.

  Conventionally, as seen in the above-mentioned Patent Document 1, for example, if it is configured to allow the nacelle 16 to stop turning at the time of a power failure under strong winds, the load on the yaw unit YU was considered to decrease. .

  However, when the present inventors examined and verified the mechanism of damage of the actual yaw unit YU, this conventional knowledge is not valid. When the nacelle 16 starts continuous turning, the load is overturned. The phenomenon of [Knowledge 3] that a yaw unit YU that increases may occur may be confirmed.

  The reason why the event of [Knowledge 3] occurs is not necessarily clear, but when the turning of the nacelle 16 is restrained by braking, the nacelle 16 and the column 14 are almost integrated, When the nacelle 16 that has been stopped by the braking operation tries to “start turning” while being blown by the wind, the positional relationship between the turning gear 20 and the turning pinion RP is shocked by the backlash of the support mechanism of the nacelle 16. It is inferred that this is due to a shift.

  Since the mass of the nacelle 16 is enormous, it is considered that the rattling of the support mechanism of the nacelle 16 has a great influence on the meshing between the turning gear 20 and the turning pinion RP. Therefore, it is understood that when the nacelle 16 starts rotating, the load received in each yaw unit YU may vary, or an extremely large load may be generated in a specific yaw unit YU.

  From such knowledge, the present inventors came to have the following views.

  As a measure in consideration of [Knowledge 3], it is necessary that the braking mechanism 6 of all yaw units YU be able to evenly handle external force during braking. If so, it is effective to slide the torque limiter TL of the yaw unit YU in order to equalize the meshing state of the turning pinion RP with respect to the turning gear 20 (to eliminate the difference in backlash).

  However, even in this case, at least one torque limiter TL should remain inactive without slipping. That is, a state in which all the torque limiters TL start to slide simultaneously (a state in which the nacelle 16 starts continuous turning) should not be caused. For this purpose, each torque limiter TL needs to maintain a high transmission torque (post-operation torque Y) even after the operation.

  Considering [Knowledge 4], if the setting of the operation start torque X and the post-operation torque Y of each torque limiter TL is appropriate, the torque limiter TL of at least one yaw unit YU does not need to be operated. It is possible to maintain the nacelle 16 in a state in which it does not enter continuous turning while the yaw unit YU is equally loaded. Thereby, most damage of the yaw unit YU can be prevented.

Therefore, in the present embodiment, the assumed maximum value A of the external force for turning the nacelle 16, the braking force B of the first braking device that brakes the turning of the nacelle 16 without using the turning gear 20, and the second braking force. The number n of yaw units YU as devices, the operation start torque X at which the torque limiter TL starts to operate, and the post-operation torque Y to be transmitted after the torque limiter TL operates, are regarded as parameters to be managed.
(AB)-(n-1) Y <X (1)
Is configured to hold.

  This equation (1) assumes that the structures (characteristics) of all yaw units YU are the same. In the wind power generation facility 12 according to this embodiment, since the number of yaw units YU is 4 (n = 4), specifically, the above equation (1) is (A−B) −3Y <X.

  In the formula (1), A, B, X, and Y are converted values at the position of the turning pinion RP. That is, each value is converted into a magnitude at the position of the turning pinion RP in consideration of a reduction ratio between the position of the torque limiter TL and the braking mechanism 6 in the power transmission system and the position of the turning pinion RP. It is the value.

  (A-B) in the equation (1) is a value obtained by subtracting the braking force B of the first braking device that is constantly applied from the assumed maximum value A of the external force (wind force) that is to turn the nacelle 16, that is, This corresponds to the braking force that must be handled by the second braking device.

  (N-1) Y in the equation (1) is a total of the post-operation torque Y obtained when all of the second braking devices except the last one of the n units slide.

  The above formula (1) is calculated from the braking force (AB) that must be handled by the second braking device, and the sum (n-1) Y of the post-operation torque Y for the (n-1) slipping units. If the subtracted value is smaller than the operation start torque X of the last one second braking device that is not slipping, the last one is based on the idea that it can maintain a non-sliding state. Thereby, it is possible to hold the nacelle 16 in a stationary state without (continuously) turning.

  From [Knowledge 4], the assumed maximum value A can be assumed to be a realistic value smaller than n · X. Further, the braking force B in the first braking device that is always applied is a value that can be set to be almost arbitrarily large. Therefore, (A−B) is a value that can be set almost arbitrarily small. Therefore, the expression (1) can be surely realized depending on the design.

  Here, the above formula (1) is slightly supplemented.

  Although the assumed maximum value A of the external force is a finite value, it is a value related to the wind force in the natural environment and is not originally uniquely determined to be a specific value. Therefore, in the present embodiment, the estimated maximum value A of the external force is defined as “the sum of the rated output torque of the motor 2 of all the built-in yaw units YU × the reduction ratio of the speed reduction mechanism 4 to the turning pinion RP position”. The value is adopted.

  Since all four yaw units YU have the same configuration in this embodiment, the assumed maximum value A is the rated output torque of the motor 2 of the built-in yaw unit YU × the reduction ratio of the reduction mechanism 4. X4. If a yaw unit having a motor with different rated output torque or a speed reduction mechanism with a different reduction ratio coexists, the combined value of each yaw unit is adopted.

  The rated output torque of the motor 2 of the yaw unit YU is selected so as to have the ability to make the nacelle 16 go around several minutes to several tens of minutes against the wind even in a situation where a strong wind blows. In this sense, it is reasonable to determine the estimated maximum value A of the external force for turning the nacelle 16 in association with the rated output torque of the motor 2. According to this definition, the assumed maximum value A of the external force is uniquely determined.

  On the other hand, the operation start torque X at which the torque limiter TL starts operating is the maximum transmission torque immediately before the torque limiter TL starts to slide. The torque limiter TL operates (slid out) when the transmission torque input from the upstream side exceeds the operation start torque X, and does not transmit any more torque to the downstream side. Specifically, the friction plate member 60 sandwiched by frictional contact between the extension plate portion 58B of the support member 58 of the torque limiter TL and the movable plate 80 starts to slide, and no further torque is transmitted to the downstream side. It becomes a state.

  On the other hand, the post-operation torque Y transmitted after the torque limiter TL is operated is a torque that can be transmitted when the torque limiter TL is actually operating (sliding). This post-operation torque Y is generally much lower than the operation start torque X in the case of a torque limiter not specifically designed. However, in the present invention, it is preferable to employ a torque limiter having a characteristic as close to the operation start torque X as possible in order that the post-operation torque Y also positively contributes to braking.

  More specifically, the post-operation torque Y is preferably 80% or more of the operation start torque X, and more preferably 90% or more of the operation start torque X can be secured. In the dry torque limiter TL according to the embodiment already described, 85% or more of the operation start torque X can be secured as the post-operation torque Y.

  Note that, when the number n of the mounted yaw units YU is large, the variation is more leveled, so that even if the post-operation torque Y is somewhat low, the tendency tends to be acceptable. Specifically, the torque limiter TL can realize the present invention more effectively when the post-operation torque Y is [100-5 (n-1)]% or more of the operation start torque X.

  Next, the operation of the wind power generation facility 12 will be explained.

  When the motor 2 of each yaw unit YU is operated, the turning pinion RP rotates via the front stage reduction mechanism 44, the torque limiter TL, and the rear stage reduction mechanism 46. As a result, the turning pinion RP revolves around the axis of the turning gear 20 (the axis of the support column 14) in response to the meshing reaction force from the turning gear 20. Thereby, the whole yaw unit YU revolves around the axis of the turning gear 20, and the nacelle 16 can turn with respect to the column 14.

  When the nacelle 16 is stationary, the braking mechanism 6 of each yaw unit YU is operated to brake the rotation of the turning pinion RP. Thereby, the yaw unit that brakes the turning of the nacelle 16 via the turning gear 20 by braking the braking force of the sliding bearing 18 that brakes the turning of the nacelle 16 without using the turning gear 20 and the rotation of the turning pinion RP. The turning of the nacelle 16 with respect to the support column 14 can be braked by the sum total with the braking force of YU.

  In the wind power generation facility 12, a structure in which the nacelle 16 is supported by the slide bearing 18 as a first braking device that directly brakes the turning of the nacelle 16 without using the swivel gear 20 is employed. The capacity of the braking mechanism 6 of the yaw unit YU as the second braking device can be reduced by the amount of the braking force (if the braking capability of the braking mechanism 6 is kept the same, the nacelle 16 can be braked with a sufficient margin).

  The braking action of the nacelle 16 by the four yaw units YU of the wind power generation facility 12 will be described in detail with reference to FIGS. 4 to 8 schematically show an example of a braking mode of the nacelle 16 by the yaw unit YU of the wind power generation facility 12.

  4 to 8, white triangular marks indicate the operation start torque Xn (X1 to X4) at which the torque limiters TLn (TL1 to TL4) of the respective yaw units YUn (YU1 to YU4) start to operate. The black triangle marks indicate the transmission torque T (T1 to T4) that is actually transmitted by the yaw unit at that time. Note that the lowercase letters a to e next to the letter “T” are given to distinguish values that change over time.

  Normally, immediately after the nacelle 16 is turned by the motor 2 and stopped, all the yaw units YU are in substantially the same contact state (backlash 0 state) with respect to the turning gear 20 ([knowledge 1]). However, when time elapses from this state, the nacelle 16 is blown by the wind and slightly moves or tilts with respect to the column 14 due to the backlash of the turning gear 20 and the turning pinion RP or the backlash of the supporting system of the nacelle 16. Or For this reason, the backlash with respect to the turning gear 20 of each yaw unit YU will be in a different state.

  FIG. 4 shows that in this state, a gust or the like is generated, the nacelle 16 is blown by the gust, and an external force that attempts to turn the nacelle 16 is reversed from the turning pinion RP side to the yaw unit YU via the turning gear 20. It shows the input status.

  In the state of FIG. 4, the yaw unit YU2 that happens to be in strong contact with the swivel gear 20 with the backlash 0 at that time is applied with a transmission torque that exceeds the operation start torque X2 of the torque limiter TL2. Yes. Since the torque limiter TL2 starts to operate (being slid out), the transmission torque Ta2 does not increase beyond the operation start torque X2.

  Incidentally, at this time, the yaw unit YU1 receives only the transmission torque Ta1 less than the operation start torque X1 of the torque limiter TL1 (Ta1 <X1), and the yaw unit YU4 has only a smaller transmission torque Ta4 (Ta4 <X4). I have not received it. The yaw unit Y3 happens to have a large backlash with the swivel gear 20 and is not in contact with the swivel gear 20 at all, and therefore receives no transmission torque from the swivel gear 20 side (Ta3 = 0 <X3).

  That is, in the state of FIG. 4, only the torque limiter TL2 of the yaw unit YU2 operates (slides out), and the other torque limiters TL1, TL3, TL4 do not operate (does not slide out). Therefore, the turning pinions RP1, RP3, and RP4 of the yaw units YU1, YU3, and YU4 remain stationary, and the nacelle 16 does not pivot (maintains a stationary state).

  As the torque limiter TL2 of the yaw unit YU2 is activated, the wind power generation facility 12 transitions to the state shown in FIG.

  In the state of FIG. 5, the transmission torque Tb2 of the torque limiter TL2 decreases from the operation start torque X2 to the post-operation torque Y2 (Ta2 = X2 → Tb2 = Y2). In the stage of FIG. 5, since the yaw unit YU4 is not yet operated, the nacelle 16 has not started to turn. Therefore, a backlash (gap) is still formed between the turning pinion RP3 of the yaw unit YU3 and the turning gear 20, and the transmission torque Tb3 of the torque limiter TL3 of the yaw unit YU3 remains zero.

  On the other hand, as a result of the transmission torque Tb2 of the torque limiter TL2 being reduced to the post-operation torque Y2, the torque limiters TL1 and TL4 of the yaw units YU1 and YU4 are increased. As a result, for example, when Tb1 ≧ X1, the torque limiter TL1 is activated, and the process proceeds to FIG.

  In FIG. 6, as a result of the transmission torque Tc1 of the yaw unit YU1 being reduced to the post-operation torque Y1, the transmission torque Tc4 of the yaw unit YU4 is increased. As a result, when Tc4 ≧ X4, the torque limiter TL4 is also activated, and the process proceeds to FIG.

  In FIG. 7, the torque limiters TL2, TL1, and TL4 are in an activated state, and the transmission torques Td2, Td1, and Td4 corresponding to the post-operation torques Y2, Y1, and Y4 are transmitted. That is, since the torque limiters TL2, TL1, and TL4 of the other yaw units YU2, YU1, and YU4 all slip while leaving the torque limiter TL3 of one yaw unit YU3, the swivel gear 20 turns the yaw unit YU3. Only a small amount of backlash between the pinion RP3 and the swivel gear 20 turns (the nacelle 16 also turns slightly). As a result, the transmission torque Td3 corresponding to the overflow of the yaw unit YU3 that has not been loaded until now is applied.

  However, since the wind power generation facility 12 is designed to satisfy the formula (1), that is, [(AB) -3Y <X], the transmission torque Td3 applied to the yaw unit YU3 at this time is It does not exceed the operation start torque X3 of the unit YU3. This is because [(A−B) −3Y] = Td3 and Td3 <X3. Therefore, since the torque limiter TL3 of the yaw unit YU3 does not operate (slide out), the nacelle 16 also turns more than the minute backlash between the turning pinion RP3 and the turning gear 20 of the yaw unit YU3 is packed. No (does not start turning). Therefore, it is possible to prevent a phenomenon in which a very large load is applied to the specific yaw unit YU when the nacelle 16 starts to turn.

  Note that the operation (slip) of the torque limiters TL1, TL2, and TL4 is settled soon (becomes inactive) because the torque limiter TL3 can receive the transmission torque Td3 satisfactorily. Therefore, eventually, as shown in FIG. 8, all torque limiters TL receive the transmission torques Te1 to Te4 almost equally and receive the transmission torques Te1 to Te4 up to the respective operation start torques X1 to X4. Switch to getting state.

  As a result, all four yaw units YU function effectively, and very effective braking can be performed.

  In the present embodiment, the braking function of the sliding bearing itself is used as the first braking device. However, the configuration of the first braking device according to the present invention is not limited to this configuration as long as the configuration can brake the turning of the nacelle without using the turning gear.

  For example, as described above, it is more effective as the first braking device according to the present invention that the resistance (that is, the braking force) of the sliding bearing can be positively adjusted by a fastening means such as a bolt.

  Naturally, the first braking device may be provided as a dedicated braking device instead of using a sliding bearing. For example, a cylindrical part (or a disk part) that rotates coaxially with the axis of the support column is formed on a part of the pedestal of the nacelle, and a brake shoe member provided on the support column side is attached to this cylindrical part such as a spring or hydraulic pressure. You may employ | adopt the structure which presses with an urging | biasing force and brakes the turning of a nacelle with a frictional force. Since rotation and braking are in a relative relationship, it is possible to provide a configuration in which a cylindrical portion (or a disc portion) is provided on the support column side and a brake shoe member is provided on the nacelle side.

  By providing such a dedicated first braking device, the value of (A-B) in the equation (1) can be further reduced, and the burden on the second braking device side can be further reduced.

  Moreover, in the said embodiment, all the yaw units were comprised with the same yaw unit. However, the present invention does not necessarily require that all yaw units be the same. The number is not limited to four (n = 4).

  FIG. 9 shows an example of the configuration.

  9 includes a first yaw unit YU101 having a first torque limiter TL101 and four second yaw units YU102 to YU102 having second torque limiters TL102 to TL105. YU105 is provided. The second yaw units YU102 to YU105 are all the same yaw unit.

  The first operation start torque X101 of the first torque limiter TL101 is larger than the second operation start torques X102 to X105 of the second torque limiters TL102 to TL105. Differences D102 to D105 between the second operation start torques X102 to X105 and the second post-operation torques Y102 to Y105 of the second torque limiters TL102 to TL105 are the first operation start torque X101 and the first post-operation torque of the first torque limiter TL101. It is smaller than the difference D101 from Y101.

  FIG. 9 shows a state in which the second torque limiters TL102 to TL105 of all the second yaw units YU102 to YU105 are operating, leaving only one first yaw unit YU101 (a state similar to FIG. 7 of the previous embodiment). ).

  The purpose of the configuration of the wind power generation facility 212 of FIG. 9 is as follows.

  First, by increasing the number of yaw units YU (n = 4 → n = 5), it is possible to perform braking with more uniform variations.

  Next, the second operation start torques X102 to X105 of the second torque limiters TL102 to TL105 of the four second yaw units YU102 to YU105 are used as the first operation of the first torque limiter TL101 of the one first yaw unit YU101. It is suppressed to be lower than the starting torque X101 (X102 to X105 <X101). Therefore, a situation is formed in which the second torque limiters TL102 to TL105 are easy to operate before the first torque limiter TL101.

  When a slip occurs in a torque limiter, the swing pinion of the yaw unit in which this slip has occurred is packed with backlash with the swivel gear, and thereafter, the yaw unit in which the slip has occurred surely performs the original braking. Is possible.

  The second torque limiters TL102 to TL105 have the second operation start torque X102 to X105 and the second operation post-operation torque Y102 to Y105, since the difference D102 to D105 is set small. The second post-operation torques Y102 to Y105 that are close to the start torques X102 to X105 can be maintained.

  Of course, the first yaw unit YU101 does not always remain without slipping to the end in relation to the initial backlash state, the magnitude of the applied external force, and the like. However, since the first operation start torque X101 of the first torque limiter TL101 is larger than the second operation start torques X102 to X105 of the second torque limiters TL102 to TL105, the first yaw unit YU101 remains without slipping to the end. The probability is high.

  Therefore, it is possible to equalize the braking force of each yaw unit more easily and to maintain the nacelle 16 so as not to start turning more reliably.

  In addition, including such a configuration, when the characteristics of the (torque limiter) of the yaw units are different from each other, it is preferable that the following equation (2) is satisfied.

That is, the assumed maximum value of the external force for turning the nacelle is A, the braking force of the first braking device is B, the operation starting torque at which each torque limiter starts operating is X1, X2, ..., Xn, each torque limiter , Yn are the post-operation torques to be transmitted after the operation is performed, and the minimum operation start torque among the respective operation start torques X1, X2,..., Xn is Xmin, and the post-operation torques Y1, Y2 When the maximum post-operation torque among Yn is Ymax,
(A−B) − [(Y1 + Y2 +... + Yn) −Ymax] <Xmin (2)
It is good to comprise so that.

  This equation (2) is based on the following points. That is, in the torque limiter, the post-operation torque does not become larger than the operation start torque. Therefore, the most severe condition for preventing the nacelle from turning is that all yaw units are left with only one. The torque limiter is slipping.

  Among the plurality of second braking devices (yaw units in the above example), there is a second braking device having such characteristics that the torque starter operating torque X is the smallest and the post-operation torque Y is the largest. The most severe situation for wind power generation equipment is when it exists and when the second braking device remains without slipping.

  However, even in this situation, a transmission torque of [(Y1 + Y2 +... + Yn) −Ymax] is obtained at least by only the slipping torque limiter. Therefore, even if the second braking device remaining without slipping to the end is a second braking device including a torque limiter that can hold only the minimum operation starting torque Xmin among the plurality of second braking devices, If the operation start torque Xmin is larger than (A−B) − [(Y1 + Y2 +... + Yn) −Ymax], the slip does not occur. Thereby, similarly to the said embodiment, the failure | damage of the structural member of a wind power generation facility can be reduced more, without turning a nacelle.

  The equation (2) corresponds to the general equation (1). In other words, the equation (2) is the equation (1) when all the second braking devices are the same. 9 is Y102 (= Y103 to Y105) and Xmin is X102 (= X103 to X105), the equation (2) can be expressed as [(A−B) − (Y101 + Y102 + Y103 + Y104 + Y105). ) -Y102] <X102. Thereby, even when the first yaw unit YU101 does not remain last, the nacelle does not turn more than the backlash between the turning pinion and the turning gear.

  In the above-described embodiment, the second braking device includes a motor, a speed reduction mechanism, and a braking mechanism, and a turning pinion is provided on the output shaft of the speed reduction mechanism, and the nacelle is driven to turn and can be braked. A yaw unit was used. However, the second braking device is not necessarily a yaw unit. For example, a unit dedicated to braking in which the motor is omitted from the yaw unit may be employed. Only a part of the brake unit may be used.

12 ... Wind power generation equipment 14 ... Prop 16 ... Nacelle 18 ... Sliding bearing (first braking device)
20 ... turning gear RP ... turning pinion TL ... torque limiter YU ... yaw unit (second braking device)
A ... Assumed maximum value of external force B ... Braking force of first braking device X ... Torque after starting operation Y ... Torque after actuation n ... Number of units (integer of 2 or more)

Claims (6)

A strut, a nacelle that swivels with respect to the strut, a swivel gear provided on the strut, a first braking device that brakes swiveling of the nacelle without the swivel gear, and a swivel that meshes with the swivel gear A wind power generation facility comprising: n (n is an integer of 2 or more) second braking devices that have a pinion and brake the turning of the nacelle via the turning gear by braking the rotation of the turning pinion Because
The n second braking devices include a torque limiter that slides when a torque of a predetermined value or more is applied,
An assumed maximum value of external force for turning the nacelle is A,
The braking force of the first braking device is B,
The torque starting torque of the torque limiter corresponding to the predetermined value is X,
When the post-operation torque transmitted after the torque limiter is operated is Y,
(AB)-(n-1) Y <X
A wind power generation facility characterized by the fact that In claim 1,
The second braking device is a yaw unit that includes a motor, a speed reduction mechanism, and a braking mechanism, and is provided with a turning pinion on an output shaft of the speed reduction mechanism to drive the nacelle to turn and perform braking. Wind power generation facility characterized by that. In claim 2,
The wind power generation facility characterized in that the accommodation space of the speed reduction mechanism and the accommodation space of the torque limiter are partitioned, and no lubricant is sealed in the accommodation space of the torque limiter. In any one of Claims 1-3,
The wind power generation facility, wherein the torque limiter has an after-operation torque Y of [100-5 (n-1)]% or more of the operation start torque X. In any one of Claims 1-4,
The second braking device has a first shaft and a second shaft connected to the first shaft via the torque limiter,
The torque limiter includes: a first member that rotates integrally with the first shaft; a second member that rotates integrally with the second shaft; a pressing member that presses the first member and the second member; An adjustment mechanism for adjusting a pressing force by the member. A strut, a nacelle that swivels with respect to the strut, a swivel gear provided on the strut, a first braking device that brakes swiveling of the nacelle without the swivel gear, and a swivel that meshes with the swivel gear A wind power generation facility comprising: n (n is an integer of 2 or more) second braking devices that have a pinion and brake the turning of the nacelle via the turning gear by braking the rotation of the turning pinion Because
The n second braking devices include a torque limiter that slides when a torque of a predetermined value or more is applied,
An assumed maximum value of external force for turning the nacelle is A,
The braking force of the first braking device is B,
The operation start torque of each torque limiter corresponding to the predetermined value is set to X1, X2,.
Y1, Y2,..., Yn, post-operation torque to be transmitted after each torque limiter is activated.
The minimum operation start torque among the operation start torques X1, X2,..., Xn is Xmin,
When the maximum post-operation torque among the post-operation torques Y1, Y2,..., Yn is Ymax,
(A−B) − [(Y1 + Y2 +... + Yn) −Ymax] <Xmin
A wind power generation facility characterized by the fact that

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