JP6489599B2 - Wind power generation equipment - Google Patents

Description

  The present invention relates to a wind power generation facility.

  Patent Document 1 discloses a wind power generation facility as shown in FIGS. 6 and 7.

  The wind power generation facility 912 includes a column 914, a nacelle 916 that is pivotably assembled to the column 914, and a blade 917. The nacelle 916 is rotatably mounted on the support column 914 via a slide bearing 918. The support column 914 is provided with a turning gear 920, and the nacelle 916 is incorporated with a yaw unit 924 having a turning pinion 922 that meshes with the turning gear 920. In the wind power generation facility 912 according to Patent Document 1, four yaw units 924 are provided.

  Each yaw unit 924 includes a motor 930, a speed reducer 932, and a braking mechanism 934, and the turning pinion 922 is provided on the output shaft 933 of the speed reducer 932. When the turning pinion 922 is driven, the turning pinion 922 receives the meshing reaction force from the turning gear 920 and revolves around the axis C920 of the turning gear 920 (= the axis C914 of the support column 914). As a result, the entire yaw unit 924 revolves around the axis C920 of the turning gear 920, so that the nacelle 916 can turn with respect to the support column 914.

  Further, by turning the rotation of the turning pinion 922 by operating the braking mechanism 934 of each yaw unit 924, the turning of the nacelle 916 with respect to the support column 914 can be braked via the turning gear 920.

  On the other hand, Patent Document 1 discloses a configuration using a rolling bearing (not shown) and a configuration using a sliding bearing 918 as a configuration that supports the nacelle 916 to be pivotable with respect to the support column 914. Among these, in the configuration using the sliding bearing 918 (see FIG. 7), the sliding bearing 918 is provided with a braking function for braking the turning of the nacelle 916 at the same time as supporting the nacelle 916. Yes. 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 (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.

JP 2011-127551 A (FIGS. 1 to 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 provide a wind power generation facility that can further reduce the breakage of the 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 the swivel gear, and the swivel gear And a plurality of second braking devices that brake the turning of the nacelle via the turning gear by braking the rotation of the turning pinion. At least a part of the second braking devices of the plurality of second braking devices is a yaw unit with a braking function for turning the nacelle , and the yaw unit includes a motor and a speed reducer. The second braking device has a braking mechanism that is activated when braking the turning of the nacelle that is driven to turn by the yaw unit, and the assumed maximum value of the external force that attempts to turn the nacelle is A, the front When the braking force of the first braking device and is B, the braking force of one of the second brake device of said plurality of second braking device, it is set larger than the (A-B), of the external forces The assumed maximum value A is a total value obtained by adding the products of the rated output torque of the motor and the reduction ratio of the reduction gear for all yaw units, and the first braking device is between the strut and the nacelle. The sliding bearing is provided with an adjusting mechanism that adjusts the braking force, and after the braking force is adjusted by the adjusting mechanism, the adjusted braking force is applied regardless of turning or braking. Thus, the above-described problems are solved.

  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 includes a yaw unit that turns the nacelle as a second braking device that performs braking via the turning gear, and the assumed maximum value of the external force for turning the nacelle is A, When the braking force of the first braking device that brakes the turning of the nacelle without the swirling gear is B, and the sum of the braking forces of some second braking devices (not all) is C, (A− B) <C is satisfied.

  In the present invention, the braking force of at least one second braking device among the plurality of second braking devices may be set larger than that of the other second braking devices.

  Thereby, the breakage of the yaw unit that cannot be handled by the conventional idea can be further reduced.

  ADVANTAGE OF THE INVENTION According to this invention, the wind power generation equipment which can reduce the failure | damage of a yaw unit more can be obtained.

The schematic plan view of the principal part of the wind power generation equipment which concerns on an example of embodiment of this invention. Sectional drawing which shows the structural example of the yaw unit in embodiment of FIG. Sectional drawing which shows the structural example of the brake unit in embodiment of FIG. Sectional view showing a configuration example of a large-capacity yaw unit Schematic plan view of a configuration example of another embodiment of the present invention Side view showing the entire conventional wind power generation facility 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, an example of an embodiment of the present invention will be described in detail based on the drawings.

  As described above, the present invention is based on knowledge newly obtained as a result of examining and verifying the mechanism of breakage of the yaw unit.

  This knowledge is summarized as follows.

  [Knowledge 1] When each yaw unit drives each turning pinion by the driving force of each motor and turns the nacelle, the direction in which the turning pinion of each yaw unit applies torque to the turning gear matches. ing. The variation in the torque of each yaw unit is small, and each yaw unit contributes to the turning of the nacelle jointly.

  [Knowledge 2] However, when the motor stops and the yaw unit enters the braking state, the load balance of each yaw unit (the load borne by each yaw unit) is larger than when the nacelle is turning. There is a tendency to vary. However, as long as it is stationary, no extremely large load is generated.

  [Knowledge 3] When the braking mechanism of the yaw unit cannot withstand external forces and starts to slide, a very large load imbalance occurs (the load on each yaw unit varies greatly). Not only that, but even after sliding, the direction of the load received by each yaw unit no longer falls apart.

  This [Knowledge 3] is a concept opposite to the conventional concept of knowledge.

  Conventionally, for example, it has been considered that maintaining the stationary state so that the braking force of the yaw unit is very strong and does not slide out even when a strong external force is applied will lead to damage of the yaw unit. Therefore, as seen in Patent Document 1, for example, the yaw unit may be configured to weaken the braking force during a power failure under strong winds and to darely turn the nacelle (rotate each member of the yaw unit). It was thought to function as a “safety mechanism” to protect the device from damage.

  However, when the present inventors examined and verified the mechanism of breakage of the actual yaw unit, it has been found that this conventional knowledge is not valid, but rather that the yaw unit is easily damaged.

  The reason for this is not necessarily clear, but when a nacelle with a large mass "turns" at the top of the column while being swirled by a strong wind that exceeds the braking force of the braking device, the nacelle support mechanism It is presumed that this is because of the rattling, that is, the shift between the axis of the column and the axis of the nacelle, and the influence of the inclination of both axes. That is, the influence of this rattling is directly received by the turning pinion provided on the nacelle side through the turning gear provided on the support column side, so that an extremely large load is applied to the yaw unit. It is understood that the direction in which the load is applied or the load is applied is dispersed.

  According to the results of examination and verification, in strong winds where the braking mechanism starts to slip, in many cases, momentary extremely large external forces are frequently applied to the yaw unit, causing slippage. It was also confirmed that the time required for each member to rotate at a high speed was extremely short. This means that taking a torque limiter measure against this situation is not in time, and is practically impossible.

  For this reason, the inventors of the present invention are more likely to damage the design philosophy of "the nacelle remains stationary even when the nacelle is subjected to the maximum possible external force during braking." It was the result that it was difficult to reach.

  Therefore, in the wind power generation facility according to an example of the embodiment of the present invention, the following configuration is adopted based on this knowledge.

  First, the schematic configuration of the wind power generation facility 12 will be described. With reference to FIG. 1 and FIG. 2, the wind power generation facility 12 according to this embodiment includes a support column 14 and a nacelle 16 that is pivotably assembled to the support column 14. The nacelle 16 is assembled to the support column 14 through a plain bearing 18 having a braking function so as to be able to turn.

  The sliding bearing 18 corresponds to the “first braking device Br1” of the present embodiment. Here, the first braking device Br1 means a braking device that brakes the turning of the nacelle 16 without using the turning gear 20.

  When the “sliding bearing 18 having a braking function” is employed as the first braking device Br1, specifically, for example, the configuration described in Patent Document 1 already described with reference to FIG. 7 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). As will be described later, for example, a mechanism for adjusting the pressing force of the sliding bearing material against the bearing plate by adjusting the amount of compression 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).

  The support column 14 is provided with a swivel gear 20, and the nacelle 16 incorporates a yaw unit 100 as shown in FIG. 2. The yaw unit 100 has a turning pinion 122 that meshes with the turning gear 20. As shown in FIG. 1, four yaw units 100 are provided in the wind power generation facility 12 according to this embodiment.

  Each yaw unit 100 corresponds to the “second braking device Br2” of this embodiment. Here, the second braking device Br2 means “a braking device that brakes the nacelle 16 via the turning gear 20 by braking the rotation of the turning pinion 122”. In this embodiment, a brake unit 200 dedicated to braking as shown in FIG. 3 is further provided as the second braking device Br2. The turning pinion 222 of the brake unit 200 is also meshed with the turning gear 20.

  In FIG. 1, the upper side of the paper surface corresponds to the side where the blade (see reference numeral 917 in FIG. 6) is present. As shown in FIG. 1, the four yaw units 100 are not equally spaced in the circumferential direction, but have a narrow space on the side with the blade (917) and a wide space on the opposite blade side. The brake unit 200 is disposed at the center of the two yaw units 100 on the opposite blade side. However, the arrangement of the yaw unit 100 and the brake unit 200 is not necessarily limited to the arrangement shown in FIG. For example, the yaw units 100 may be arranged such that the circumferential intervals are the same, or the units 100 and 200 including the brake unit 200 may be arranged so that the circumferential intervals are the same. Good. Furthermore, the number of yaw units 100 and brake units 200 is not limited to the example of FIG. For example, the number of yaw units 100 may be 3 or less, or 5 or more, or the number of brake units 200 may be 2 or more.

  The configuration of the yaw unit 100 in FIG. 2 will be described.

  The yaw unit 100 includes a motor 130, a speed reducer 132, a turning pinion 122, and a braking mechanism 134. The speed reducer 132 includes an input side eccentric oscillating speed reducer 150 and an output side eccentric oscillating speed reducer 152. The input side eccentric oscillating speed reducer 150 is an eccentric oscillating speed reducer called a center crank type, an input shaft 154 integrated with the motor shaft 151, and an eccentric body 156 that rotates integrally with the input shaft 154. And an external gear 158 incorporated on the outer periphery of the eccentric body 156 so as to be able to swing and rotate, and an internal gear 160 in which the external gear 158 is in meshingly engaged. The number of teeth of the internal gear 160 is slightly larger (only 1 in this example) than that of the external gear 158.

  In the reduction gear 132, when the external gear 158 swings and rotates through the eccentric body 156 by the rotation of the input shaft 154, the external gear 158 rotates slowly with respect to the internal gear 160. This rotation is taken out from the output shaft 165 via the pin member 162 passing through the external gear 158 and the carrier 164.

The output side eccentric oscillating speed reducer 152 is also a center crank type eccentric oscillating speed reducer, and its capacity is larger than that of the input side eccentric oscillating speed reducer 150. It is the same as the reduction gear 150. Accordingly, parts having the same or similar functions as those of the input-side eccentric rocking reduction gear 150 are denoted by the same reference numerals with the suffix A in the figure, and redundant description is omitted. The output shaft 165A of the output-side eccentric oscillating speed reducer 152, the pivot pinion 122 via a spline Contact and bolts 170 are fixed.

  FIG. 3 shows a configuration example of the brake unit 200 that also constitutes the second braking device Br2.

  The brake unit 200 includes a speed reducer 232, a turning pinion 222, and a braking mechanism 234. There is no motor. That is, the brake unit 200 does not have a function of driving the nacelle 16 to turn. The speed reducer 232 of the brake unit 200 includes a center crank type input-side eccentric rocking speed reducer 250 and an output side eccentric rocking speed reducer 252 called a sorting type.

  Since the input-side eccentric oscillating speed reducer 250 has a reduction mechanism similar to that of the input-side eccentric oscillating speed reducer 150 of the yaw unit 100, the function of the input side eccentric oscillating speed reducer 150 in FIG. The same reference numerals are given to the parts that are similar to each other, and redundant description is omitted.

  The output side eccentric oscillating speed reducer 252 includes an input shaft 272 integrated with the output shaft 265 of the input side eccentric oscillating speed reducer 250, an input pinion 274 integrally formed with the input shaft 272, and the input Three sorting gears (only one is shown) 276 that mesh simultaneously with the pinion 274 are provided. Each sorting gear 276 is connected to three crankshafts (only one is shown) 278 arranged at a position offset from the axis C272 of the input shaft 272. Each crankshaft 278 is integrally formed with an eccentric body 280, and an external gear 282 is incorporated in the eccentric body 280 so as to be able to swing and rotate. The external gear 282 is in mesh with the internal gear 284. The number of teeth of the internal gear 284 is slightly larger (by 1 in this example) than the number of teeth of the external gear 282.

  In the output side eccentric oscillating speed reducer 252, when the input shaft 272 rotates, the three crank shafts 278 rotate in the same direction at the same rotational speed via the input pinion 274 and the sorting gear 276, and each crank shaft The eccentric body 280 provided in 278 rotates synchronously. As a result, the external gear 282 rotates slowly with respect to the internal gear 284 while swinging, and this rotation is taken out from the output shaft 288 via the load-side carrier 286 as the revolution of the crankshaft 278. . The output shaft 288 is integrated with the turning pinion 222 via a spline 290 and a bolt 292.

  The rated output torque of the motor 130 of the yaw unit 100 is Rp130, the braking force of the braking mechanism 134 is Bp134, and the reduction ratio of the reduction gear 132 is Sr132. Therefore, the braking force at the turning pinion 122 of the yaw unit 100 is Bp100 (= Bp134 × Sr132) obtained by multiplying the braking force Bp134 of the braking mechanism 134 by the reduction ratio Sr132 of the reduction gear 132.

  The braking force of the braking mechanism 234 of the brake unit 200 is Bp234, and the reduction ratio of the reduction gear 232 is Sr232. Therefore, the braking force at the turning pinion 222 of the brake unit 200 is Bp200 (= Bp234 × Sr232) obtained by multiplying the braking force Bp234 of the braking mechanism 234 by the reduction ratio Sr232 of the reduction gear 232.

  The braking force Bp234 of the braking mechanism 234 of the brake unit 200 is larger than the braking force Bp134 of the braking mechanism 134 of the yaw unit 100 (Bp134 <Bp234). Further, the reduction ratio Sr232 of the reduction device 232 of the brake unit 200 is larger than the reduction ratio Sr132 of the reduction device 132 of the yaw unit 100 (Sr132 <Sr232). Therefore, the braking force Bp200 (= Bp234 × Sr232) at the turning pinion 222 of the brake unit 200 is significantly larger than the braking force Bp100 (= Bp134 × Sr132) at the turning pinion 122 of the yaw unit 100 (Bp100 << Bp200). .

  Note that the pitch circle diameter Pc222 of the turning pinion 222 of the brake unit 200 is larger than the pitch circle diameter Pc122 of the turning pinion 122 of the yaw unit 100 (Pc122 <Pc222). On the other hand, the swivel pinion 222 of the brake unit 200 and the swivel pinion 122 of the yaw unit 100 need to be engaged with the same swivel gear 20 and are therefore set to be the same. However, in this embodiment, the backlash of the turning pinion 222 of the brake unit 200 with respect to the turning gear 20 is set smaller than the backlash of the turning pinion 122 of the yaw unit 100 with respect to the turning gear 20. In order to reduce the backlash, specifically, for example, the tooth thickness on the pitch circle of the turning pinion 222 of the brake unit 200 is set larger than the tooth thickness on the pitch circle of the turning pinion 122 of the yaw unit 100. Good. Alternatively, when the brake unit 200 is assembled to the nacelle 16, the backlash can be set small by a method of incorporating the brake pin 200 so that the axis of the turning pinion 222 is closer to the turning gear 20 side.

  Here, the reduction ratio is a value of the denominator of the speed ratio. The speed reduction ratio is the speed increase ratio when viewed from the turning pinions 122 and 222 side.

  As described above, in this embodiment, in this embodiment, the braking of the turning of the nacelle 16 of the wind power generation facility 12 is not simply regarded as the role of the yaw unit 100 but is captured by the entire wind power generation facility 12. That is, in the present embodiment, the rotation of the sliding bearing 18 (first braking device Br1) with a braking function and the rotation pinions 122 and 222 that perform the braking of the turning of the nacelle 16 without using the turning gear 20 is braked. This is realized by a combination of four yaw units 100 and brake units 200 (a plurality of second braking devices Br2) performed through the swivel gear 20.

  When the assumed maximum value of the external force to turn the nacelle 16 is A, the braking force of the first braking device Br1 is B, and the total braking force value of some second braking devices Br2 is C. , (A−B) <C. The “braking force of the second braking device Br2” here refers to the braking forces Bp100 and Bp200 at the turning pinions 122 and 222.

  Specifically, the braking force B of the first braking device Br1 indicates the sliding resistance of the sliding bearing 18 in this embodiment. In other words, the braking force B corresponds to a force necessary for turning the nacelle 16 from a stationary state. In addition, in the present embodiment, the total braking force C of some second braking devices Br2 is greater than (A−B) because the braking force Bp200 of only the brake unit 200 is greater than (A−B). The power Bp200 is indicated.

  Hereinafter, the technical significance of the mathematical formula (A−B) <C will be described in detail.

  Based on the findings 1 to 3, the present embodiment is based on the design philosophy that “the nacelle remains stationary even when the nacelle is subjected to the maximum external force that can be assumed during braking”. I have already said that. In order to realize this design concept, the assumed maximum value A of the external force must be determined in some form. However, although the assumed maximum value A of the external force is a finite value, it is due to the wind force in the natural environment, and is not originally determined to be a specific value.

  Therefore, in the present embodiment, the assumed maximum value A of the external force is defined as “the sum of the rated output torque Rp130 of the motor 130 of each yaw unit 100 incorporated × the reduction ratio Sr132 of the reduction gear 132”.

  In this embodiment, since all the yaw units 100 have the same configuration, the assumed maximum value A is (Rp130 × Sr132 × 4). However, if the motor has a different rated output torque or is different. When yaw units having reduction gears with a reduction ratio are mixed, the total value of the yaw units is obtained.

  That is, the motor 130 of the yaw unit 100 is selected so as to have the ability to make the nacelle 16 go around several tens of seconds against the wind even in a situation where a strong wind blows. That is, the driving force is sufficient to turn the nacelle 16 against the wind with the continuous rated output torque Rp130 (not the startup output torque of about 1 second).

  On the basis of this, considering the above knowledge 1 that “when nacelle is driven, the yaw units generally drive the nacelle jointly”, “the wind power generation facility 12 determines the estimated maximum value A of the external force as the yaw. The yaw unit 100 having the motor 130 of the rated output torque Rp130 and the speed reduction device 132 of the speed reduction ratio Sr132 is selected because it is regarded as the sum of the rated output torque Rp130 of the motor 130 of the unit 100 × the speed reduction ratio Sr132 of the speed reduction device 132. It can also be said. By following this definition, the assumed maximum value A of the external force in the present embodiment is a concept that can be uniquely specified.

  Next, the technical significance of the mathematical formula (A−B), that is, the braking force of the first braking device Br1 that directly brakes the turning of the nacelle 16 (without the turning gear 20) from the assumed maximum value A of the external force. Explain the technical significance of subtracting B.

  When the nacelle 16 is stationary with respect to the support column 14, the support mechanism (sliding bearing 18) of the nacelle 16 always has a turning resistance (that is, braking force B), so that braking is performed via the turning gear 20. The second braking device Br2 only needs to provide a braking force (A−B) obtained by subtracting the braking force B corresponding to the turning resistance of the support mechanism from the assumed maximum value A. This is the first significance of the mathematical formula (A−B).

  In addition, the mathematical formula (A−B) has another technical significance. When the second braking device Br2 starts to slide in a state where the braking force is applied, the load received by each second braking device Br2 increases rapidly from the knowledge 3. This can be inferred from the fact that “the influence of the support mechanism of the nacelle having a huge mass (the misalignment between the axis of the column and the nacelle and the inclination of both axes) becomes obvious”. As already mentioned.

  In order to cope with this situation, the turning of the nacelle 16 is not only braked via the turning gear 20, but a structure that directly brakes the nacelle 16 with respect to the column 14 without using the turning gear 20 is actively used. It is preferable to use them together (to increase the braking force B more positively). Thereby, it becomes possible to further reduce the influence of the rattling of the support mechanism of the nacelle 16 under a strong wind. In the present embodiment, the braking force B is constantly generated when the nacelle 16 is stationary with respect to the support column 14, so that the influence of rattling during braking and stationary can be further reduced. This is the second significance of the mathematical formula (A-B).

  From this point of view, the braking force B of the first braking device Br1 is not that in which the turning resistance is intentionally reduced as in the case of, for example, a rolling bearing, but is at least equal to or more than the turning resistance of the sliding bearing, that is, “braking force” The value is preferably large enough to function. Of course, as will be described later, the first braking device Br <b> 1 may be configured to more actively brake the nacelle 16.

  Next, the total value C in the formula (A−B) <C is not the total braking force value of “all” second braking devices, but the total braking force value of “some” second braking devices. Explain the technical significance of being.

  According to the knowledge 2, when the nacelle 16 enters the braking / resting state, the load balance of each yaw unit 100 tends to vary more than (when the nacelle 16 is turned). For example, when a backlash occurs between the turning pinion 122 of the specific yaw unit 100 and the turning gear 20 during braking at a certain point in time, the braking mechanism 134 of the specific yaw unit 100 causes the turning pinion 122 to rotate. This means that the rotation of the swivel gear 20 cannot be braked even though it can be braked. In this case, it is necessary to be able to brake the turning gear 20 with the braking force of the second braking device Br2 excluding this specific yaw unit 100. In other words, the braking force that can be applied to the nacelle 16 is not necessarily a simple sum of the braking forces of “all” yaw units 100 when the nacelle 16 is braked and stationary. It is. That is, in the calculation, even if the sum of the braking forces of all yaw units 100 exceeds (AB), the braking force that can actually be generated may be less than (AB). . However, this increases the possibility that the nacelle 16 will move.

  For example, when an excessive external force is applied to a specific yaw unit 100, the yaw unit 100 may be damaged. In this case, if the remaining yaw unit 100 cannot share the braking force that can stop the nacelle 16, chain damage may occur one after another, and as a result, the nacelle 16 may not be kept stationary. However, even in this respect, if only a part of the second braking devices Br2 has a braking force exceeding (A-B), all the second braking devices Br2 are chain damaged and the nacelle 16 starts to turn. It is possible to further reduce the risk of being lost.

  This is why the sum of the braking forces of all the second braking devices Br2 is used as the sum C of the formula (A−B) <C, not the sum of the braking forces of all the second braking devices Br2. It is.

  In view of this point, more specifically, “a part of the second braking devices Br2” refers to a second braking device Br2 (for example, the second braking device Br2 of less than half of the total number of all the second braking devices Br2). If the total number is 5, 2 or less second braking devices Br2) are preferable. Furthermore, it is more preferable that the braking force of one of the plurality of second braking devices Br2 is set larger than (AB). It is also preferable that the braking force of all the second braking devices Br2 is set to be larger than (A−B).

  In the present embodiment, the braking force Bp200 is configured to exceed (AB) with only one brake unit 200, that is, only one second braking device Br2. Therefore, even if the other yaw unit 100 cannot be involved in the braking of the swivel gear 20 due to the presence of backlash, for example, or if it is in a braking situation in which it does not slide to provide the original braking force, the 1 Only the second braking device Br2 (brake unit 200) of the stand can provide a braking force exceeding (A-B). Therefore, it is possible to prevent the nacelle 16 from slipping out with a very high probability.

Hereinafter, if specific numerical values are exemplified, in the present embodiment, four yaw units 100 having a rated output torque Rp130 of the motor 130 of 2.145 kgm are used, and the speed reduction device 132 of each yaw unit 100 is used. reduction ratio Sr132 is 1, is a 075 (reduction ratio 25 of the reduction ratio 43 × output side eccentric oscillating speed reducer 152 of the input-side eccentric oscillating speed reducer 150). Therefore, the assumed maximum value A of the external force is 2.145 × 1,075 × 4 = 9,223 kgm.

  The braking force B of the first braking device Br1 (sliding bearing 18) is 5,000 kgm. Therefore, (A−B) = 9,223-5,000 = 4,223 kgm. And the brake unit 200 which can provide braking force Bp200 (Bp234 * Sr232 = 4,500Kgm = C) exceeding 4,223 kgm with one (a part of second braking devices Br2) is provided. Therefore, the wind power generation facility according to the present embodiment satisfies the formula of (A−B) <C.

  Next, the operation of the wind power generation facility according to this embodiment will be described.

When the motor 130 of each yaw unit 100 is rotated and the turning pinion 122 is driven, the turning pinion 122 receives the meshing reaction force from the turning gear 20 and rotates around the axis C20 of the turning gear 20 (the axis C14 of the support column 14). (Refer to FIG. 1). Thereby, since the whole yaw unit 100 revolves around the axis C20 of the turning gear 20, the nacelle 16 can turn with respect to the support column 14.

  At this time, the brake unit 200 is rotated with no load. Since the brake unit 200 does not have a motor, no matter how the reduction ratio Sr232 and the pitch circle diameter Pc222 (number of teeth) of the turning pinion 222 are set, it does not interfere with other yaw units 100. The degree of freedom is extremely high.

  When braking the turning of the nacelle 16, the braking mechanism 134 of each yaw unit 100 is operated to brake the rotation of the turning pinion 122, thereby braking the turning of the nacelle 16 with respect to the column 14 via the turning gear 20. At the same time, the turning of the nacelle 16 with respect to the column 14 can be braked via the turning gear 20 by operating the braking mechanism 234 of the brake unit 200 to brake the rotation of the turning pinion 222 of the brake unit 200. .

  In the present embodiment, the first braking device Br1 (specifically, the sliding bearing 18) for directly braking the turning of the nacelle 16 without using the turning gear 20 is provided. 2 The braking force of the braking device Br2 can be reduced (if the braking force of the second braking device Br2 is made the same, the braking force of the nacelle 16 having a sufficient margin can be secured).

  In addition, it is possible to further suppress the nacelle 16 from rattling against the support column 14 when braking or when the nacelle 16 starts to turn during braking, and accordingly, an excessive load applied to the yaw unit 100 is reduced. it can.

  In this embodiment, the assumed maximum value of the external force for turning the nacelle 16 is A, the braking force of the first braking device Br1 is B, the total braking force value of some second braking devices is C, Since (A−B) <C is established, the nacelle 16 is stationary and does not slide out in a braked state as long as the external force due to the wind is within the assumption. Therefore, a situation in which a strong load such as that obtained in Knowledge 3 is generated randomly is prevented, and the yaw unit 100 can be further prevented from being damaged.

  In particular, in this embodiment, the first braking device Br1 is constituted by a sliding bearing 18 disposed between the support column 14 and the nacelle 16. For this reason, a braking torque can always be generated between the support column 14 and the nacelle 16. That is, the braking force of the first braking device Br1 can be applied also when the nacelle 16 is actively turned by the motor 130. For this reason, the effect of reducing unnecessary fluctuation of the nacelle including not only during braking but also during normal power generation can be obtained. It is cheaper than anything and is less likely to break down. Then, the braking force of the second braking device Br2 can be reduced by the amount of the braking force B of the first braking device Br1.

  In the present embodiment, the braking force of at least one second braking device Br2 (brake unit 200) among the plurality of second braking devices Br2 is greater than that of the other second braking devices (yaw unit 100). Is set. Therefore, even if the other second braking device Br2 (not having a large braking force) cannot support the swivel gear 20 due to insufficient capacity (or due to the presence of backlash, etc.), the second braking device Br2 having a large braking force is set. (2) The possibility that the second braking device Br2 can support the swivel gear 20 is increased (if the second braking device Br2 is configured only with a braking force having the same magnitude, a specific second If the braking device Br2 cannot support the swivel gear 20 for some reason, it cannot supplement the swivel gear 20 by supplementing it, and there is a high possibility that it will not be possible to maintain the stationary state of the swivel gear 20 after all).

  Further, in the present embodiment, the second braking device Br2 (brake unit 200) in which the braking force Bp200 is increased is a speed increasing ratio Sr232 that is larger than the speed increasing ratio Sr132 of the yaw unit 100 when viewed from the turning pinion 222 side. It has a speed increasing mechanism. For this reason, coupled with the fact that the braking force Bp234 itself of the braking mechanism 234 of the brake unit 200 is stronger than the braking force Bp134 of the braking mechanism 134 of the yaw unit 100 (by multiplication), the braking force at the turning pinion 122 of the yaw unit 100 A braking force Bp200 (= Bp234 × Sr232) that is much stronger than Bp100 (= Bp134 × Sr132) can be applied to the turning gear 20 via the turning pinion 222.

  In the present embodiment, the braking force Bp200 of one unit (brake unit 200) of the plurality of second braking devices Br2 is set to be larger than (AB). Therefore, unless the assumed maximum value A of the external force is unexpectedly high, the brake unit 200 prevents the turning gear 20 from starting to turn independently regardless of the braking situation of the other second braking device Br2. can do.

  In the present embodiment, the pitch circle diameter Pc222 of the turning pinion 222 of the second braking device Br2 (brake unit 200) in which the braking force Bp200 is greater than (AB) is the other second braking device Br2. It is larger than the pitch circle diameter Pc122 of the turning pinion 122 of the (yaw unit 100). Therefore, even if the braking force is large, the surface pressure of the turning pinion 222 can be further reduced, and the strength (or durability) of the turning pinion 222 can be further increased.

  Further, in this embodiment, the backlash of the turning pinion 222 of the brake unit 200 with respect to the turning gear 20 is set smaller than the backlash of the turning pinion 122 of the yaw unit 100 with respect to the turning gear 20. Accordingly, the probability that the turning pinion 222 of the brake unit 200 can contribute to the braking of the turning gear 20 first (loading the load first) is higher than that of the turning pinion 122 of the yaw unit 100 during braking. Can be increased. Therefore, the stationary state of the nacelle 16 can be stabilized earlier in an environment where the nacelle 16 is likely to be turned by an external force. If the specific yaw unit 100 is clogged with the backlash earlier than the brake unit 200, and the specific yaw unit 100 alone cannot brake the turning of the turning gear, the turning gear 20 has the backlash of the brake unit 200. Until the braking force Bp200 of the brake unit 200 is applied to the swivel gear 20. However, unless the swivel gear 20 starts to move continuously, the braking force B does not change to dynamic friction. Therefore, the relationship of (A−B) <C is not broken, and the turning gear 20 can be reliably maintained stationary by the braking force Bp200 of the brake unit 200 that can work with backlash. . Note that when the nacelle 16 is driven to turn by the motor 130 of the yaw unit 100, the brake unit 200 only rotates with no load, so even if the backlash of the brake unit 200 is set to be small, There is almost no adverse effect.

  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 with respect to the support column. 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 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 with a biasing force such as a spring It is also possible to adopt a configuration in which the nacelle is braked by pressing 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, it is possible to more reliably reduce the influence of rattling of the nacelle support mechanism.

  Furthermore, as the first braking device, for example, a braking device using a hydraulic control mechanism can be employed to obtain the pressing force of the brake shoe member. Although the braking device using the hydraulic control mechanism is expensive, the braking force of the first braking device can be turned “off” when the nacelle is actively turned, thereby reducing loss during turning driving. it can. In addition, there is an advantage that the braking torque by the first braking device can be set higher than that of the constant braking type.

  In the above embodiment, the second braking device is configured to add one large-capacity braking unit to four yaw units. However, the present invention does not necessarily have this configuration. It is not limited.

  For example, a configuration in which the braking force of at least one second braking device among the plurality of second braking devices is larger than the braking force of other second braking devices may be employed. That is, for example, the braking force of two or more second braking devices may be set larger than that of other second braking devices. Conversely, there may be no second braking device with a large braking force set (that is, all the second braking devices have the same braking force). Even in this case, for example, in addition to the yaw unit, if there is a second braking device dedicated to braking, the assumed maximum value of external force is A, the braking force of the first braking device is B, and some second braking devices When the total value of the braking force of the device is C, it is possible to establish (A−B) <C, and the effect of the present invention can be obtained. Moreover, even if it does not have the 2nd braking device only for braking, that is, all the 2nd braking devices may be a yaw unit of the same composition. For example, all yaw units may have a braking force C greater than (A-B).

  Further, in the above embodiment, the second braking device with the increased braking force Bp200 includes a speed increasing mechanism (decelerator 232) having a speed increasing ratio larger than the speed increasing ratio of the yaw unit as seen from the turning pinion side. However, the second braking device having a large braking force does not necessarily have a speed increasing mechanism with a large speed increasing ratio. For example, the second braking device is different between a yaw unit and a brake unit that differ only in the presence or absence of a motor. An apparatus may be configured.

  Of course, for example, the braking force of the braking mechanism of the second braking device is all the same, and by having a speed increasing mechanism with a speed increasing ratio larger than the speed increasing ratio of the yaw unit as seen from the turning pinion side, the turning pinion A second braking device with different braking force may be configured.

  Further, in the above-described embodiment, in order to maintain the braking of the nacelle more reliably regardless of the braking state of each second braking device at the time of nacelle braking, one of the second braking devices is controlled. The power is set so that a braking force larger than (A-B) can be secured. However, as long as the braking force of some of the second braking devices is used, the effects of the present invention can be obtained accordingly. it can. Therefore, the structure that the total value of the braking force of two or more 2nd braking devices is larger than said (AB) may be sufficient.

  In the above embodiment, the pitch circle diameter Pc222 of the turning pinion 222 of the second braking device (brake unit 200) whose braking force is greater than (A-B) is different from that of the other second braking device (yaw). It was set larger than the pitch circle diameter Pc122 of the turning pinion 122 of the unit 100), and in particular, the higher strength of the tooth portion of the turning pinion 222 was secured. However, the present invention does not necessarily have such a configuration, and for example, the pitch circle diameters of the turning pinions may all be the same.

  In the above embodiment, a brake unit dedicated to braking that does not contribute to the driving of the swivel gear is provided as the second braking device. However, in the present invention, the second braking device is configured only by the yaw unit. May be. For example, as shown in FIG. 5, three small-capacity yaw units 100 and one large-capacity yaw unit 300 are provided, resulting in a total of four second braking devices Br2. It is good also as a structure. Specifically, the yaw unit 100 shown in FIG. 2 and the yaw unit 300 as shown in FIG. 4 may be used. The yaw unit 300 is obtained by adding a motor 330 to the brake unit 200. For this reason, the same reference numerals are assigned to the same parts as the brake unit 200, and redundant description is omitted.

  This configuration is excellent in that the large-capacity yaw unit 300 can also function as the brake unit 200, and the total number of the second braking devices Br2 does not have to be increased in the narrow nacelle 16. However, unlike the brake unit 200 dedicated to braking, the yaw unit 300 needs to drive the swivel gear 20 in synchronization with the small capacity yaw unit 100, and therefore the pitch circle of the swivel pinion 122 of the small capacity yaw unit 100. It is necessary to set the pitch circle diameter Pc322 of the swivel pinion 322, the reduction ratio Sr332 of the speed reducer 332, etc. so that the tangential speed at the pitch and the tangential speed at the pitch circle of the swivel pinion 322 of the large-capacity yaw unit 300 are the same. There is.

  In addition, the above-described configuration in which “the braking force of at least one second braking device among the plurality of second braking devices is larger than the braking force of other second braking devices”, “the braking force is increased The second braking device has a speed increasing mechanism having a higher speed increasing ratio when viewed from the turning pinion side than the other second braking devices, or “the turning pinion of the second braking device having a larger braking force”. The configuration that “the pitch circle diameter is larger than the pitch circle diameter of the turning pinion of the other second braking device” is a configuration that has technical significance even when separated from the concept of the maximum assumed value A of the external force. This is because these configurations can be regarded as a configuration that can avoid the turning of the turning gear at the time of braking, in view of the above knowledge 2 and knowledge 3.

  Further, the method of determining the maximum estimated value A of the external force in the above embodiment is an example, and other determination methods are not excluded. For example, based on data such as wind speed measured over a certain period of time (for example, one year), actual measurement data such as the state of damage or deformation of nacelles, struts, and yaw units, for example, actually measured at the wind power generation facility. It is reasonable to determine an external force that slightly exceeds the determined maximum external force as the “maximum estimated value A of the external force”. This method is superior in that it can take into account the geographical circumstances peculiar to the land where the wind power generation facility is actually installed.

12 ... Wind power generation equipment 14 ... Prop 16 ... Nacelle 18 ... Sliding bearing (first braking device)
20 ... Swivel gear
122 ... turning pinion 100 ... yaw unit (second braking device)
200 ... Brake unit (second braking device)
A ... Assumed maximum value of external force B ... Braking force of first braking device C ... Sum of braking forces of some second braking devices

Claims (4)

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 plurality of 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,
Wherein at least a portion of said second braking device of the plurality of second braking device is a yaw unit with braking function for turning drive the nacelle,
The yaw unit has a motor and a reduction gear,
The second braking device has a braking mechanism that is operated when braking the turning of the nacelle that is driven to turn by the yaw unit,
When the assumed maximum value of the external force for turning the nacelle is A and the braking force of the first braking device is B , the control of one second braking device of the plurality of second braking devices is performed. The power is set larger than (A-B),
The assumed maximum value A of the external force is a total value obtained by adding the products of the rated output torque of the motor and the reduction ratio of the reduction gear for all yaw units,
The first braking device is a sliding bearing disposed between the support column and the nacelle, and has an adjusting mechanism for adjusting a braking force. After the braking force is adjusted by the adjusting mechanism, A wind power generation facility in which the adjusted braking force acts regardless of braking. In claim 1,
The wind power generation facility, wherein a braking force of at least one second braking device among the plurality of second braking devices is larger than that of the other second braking devices. In claim 2,
The second braking device has a speed increasing mechanism between the braking mechanism of the second braking device and the turning pinion, which makes the rotation of the braking mechanism faster than the rotation of the turning pinion,
The second braking device in which the braking force is increased is a braking device other than the yaw unit,
The wind power generation facility characterized in that the speed increasing ratio of the speed increasing mechanism of the second braking device in which the braking force is increased is larger than the speed increasing ratio of the speed increasing mechanism of the yaw unit. In any one of Claims 1-3 ,
The wind turbine generator according to claim 2, wherein the second braking device in which the braking force is greater than (A-B) has a larger pitch circle diameter of the turning pinion than other second braking devices.

Images