JP5352510B2 - Wind speed booster - Google Patents

Description

  The present invention relates to a step-up gear for wind power generation.

  For example, Patent Document 1 discloses a speed increasing device for wind power generation as shown in FIGS.

  6 and 7, the wind turbine generator 1 is assembled with a support column 2 standing on the foundation 6, a nacelle 3 installed at the upper end of the support column 2, and a rotatable structure with respect to the nacelle 3. And a rotor head 4. A plurality of (three in the illustrated example) wind turbine blades (wind turbine blades) 5 are attached to the rotor head 4. Inside the nacelle 3, a speed increaser 20 and a generator 11 are connected to the rotor head 4.

  When wind hits the windmill blade 5, the rotor head 4 rotates, and the rotation of the rotor head 4 is transmitted to the generator 11 while being accelerated by the gearbox 20. As a result, the rotation of the rotor head 4 (with torque), which is slow, can be amplified to a speed of about 100 times, and the power generation output can be efficiently obtained from the generator 11. In FIG. 7, reference numeral 12 denotes a transformer, 13 denotes a controller, 14 denotes an inverter, 15 denotes an inverter cooler, and 16 denotes a lubricating oil cooler.

  As shown in FIG. 8, the speed increaser 20 includes a planetary gear mechanism 22 in the first stage and parallel shaft gear mechanisms 24 and 26 in the middle stage and the rear stage. The rotation of the main shaft (not shown) of the rotor head 4 input from the input shaft 28 is accelerated by a total of three stages of gear mechanisms 22, 24, 26 and output from the output shaft 30. The generator 11 described above is connected to the output shaft 30.

  The planetary gear mechanism 22 includes a carrier 32 integrated with an input shaft 28, a planetary pin 34 fixed to the carrier 32, a planetary gear 36 rotatably supported by the planetary pin 34, and the planetary gear 36 simultaneously. It is mainly comprised from the internal gear 38 and the sun gear 40 which mesh. In this example, the sun gear 40 is integrated with the output shaft 42 of the planetary gear mechanism 22, and the internal gear 38 is integrated with the casing 44.

  A roller bearing 46 is interposed between the planetary pin 34 and the planetary gear 36 so as to be able to cope with a large torque input from the windmill blade 5 side.

JP 2009-144533 A (FIGS. 6 to 8)

  The wind power generation facility is designed so that its useful life is around 20 years. For this reason, it is required that the speed increaser basically has a life of about 20 years.

  However, wind power generation facilities cannot always be installed in a place where stable winds can be secured at all times. Especially in recent years, places where turbulent winds such as complex terrain parts receive turbulences, sometimes huge typhoons and hurricanes. There are an increasing number of cases where it is unavoidable to install in places where a heavy wind load is applied. Among the wind power generation facilities installed in these areas, the actual situation is that there are many troubles related to the gearbox (even if it is designed according to the guidelines). As troubles of the gearbox once occur, the damage becomes serious, so ensuring reliability is regarded as important.

  In general, an effective measure for ensuring the reliability of the gearbox is to increase the safety factor (safety factor) of each element when designing, if necessary. However, if the safety factor of each element is increased, the speed-up gear as a whole is naturally increased in size and weight, resulting in an increase in manufacturing cost and construction cost.

  The present invention was made to solve such problems, and by overcoming a newly found intermediate problem (described later), it is small, light, and low in cost, and highly reliable. Providing a gearbox for wind power generation with a long service life is the original challenge.

The present invention provides a speed increasing device for wind power generation provided with a planetary gear mechanism, comprising: a gear that constitutes one element of the planetary gear mechanism; and a support member that rotatably supports the gear via a bearing. The gear is a planetary gear of the planetary gear mechanism, the planetary gear is rotatably supported with respect to the planetary pin by a planetary pin as the support member, and the bearing includes an outer ring. A lubricant can enter between the planetary gear and the outer ring of the bearing, and at least two of the planetary gear, the bearing, and the support member are relatively small in the radial direction. By adopting a configuration in which a gap that can be displaced is formed , the above-mentioned original problem is solved.
Further, the present invention provides a speed increasing device for wind power generation provided with a planetary gear mechanism, a gear constituting one element of the planetary gear mechanism, and a support member that rotatably supports the gear via a bearing. And the gear is a planetary gear of the planetary gear mechanism, the planetary gear is rotatably supported by the planetary pin as the support member, and the bearing has an inner ring. A lubricant can enter between the planetary pin and the inner ring of the bearing, and at least two of the planetary gear, the bearing, and the support member are relatively radially arranged. The above-described original problem is solved by forming a gap that allows minute displacement.
Further, the present invention provides a speed increasing device for wind power generation provided with a planetary gear mechanism, a gear constituting one element of the planetary gear mechanism, and a support member that rotatably supports the gear via a bearing. And the gear is a planetary gear of the planetary gear mechanism, and the planetary gear includes a planetary pin that rotates integrally with the planetary gear, and the carrier by the carrier of the planetary gear mechanism as the support member. The bearing is provided with an outer ring, a lubricant can enter between the carrier and the outer ring of the bearing, and the planetary gear, the bearing, and the support are supported. The above-mentioned original problem is solved by forming a gap in which at least two of the members are relatively displaceable in the radial direction.
Further, the present invention provides a speed increasing device for wind power generation provided with a planetary gear mechanism, a gear constituting one element of the planetary gear mechanism, and a support member that rotatably supports the gear via a bearing. And the gear is a planetary gear of the planetary gear mechanism, and the planetary gear includes a planetary pin that rotates integrally with the planetary gear, and the carrier by the carrier of the planetary gear mechanism as the support member. The bearing is provided with an inner ring, a lubricant can enter between the carrier and the inner ring of the bearing, and the planetary gear, the bearing, and the support are supported. The above-mentioned original problem is solved by forming a gap in which at least two of the members are relatively displaceable in the radial direction.

  Since the intermediate problem and the solution principle of the present invention are not publicly known, the intermediate problem and the solution principle of the present invention will be described in detail here.

  A wind turbine blade of a wind power generation facility may be momentarily strongly subjected to “wind changing in wind speed or direction”. For example, when a strong gust is applied to the windmill blade, a strong acceleration torque is momentarily applied to each element of the speed increaser. However, since a generator that rotates at high speed is connected as a load at the tip of the speed increaser, each element of the speed increaser can instantaneously follow this acceleration torque due to inertia and increase the rotation speed. Can not. As a result, when the acceleration torque rises steeply, the acceleration torque rising steeply is applied to each element instantaneously (as if applied to each stationary element).

  Further, for example, in the case of bad weather where the wind direction changes drastically, wind may be applied from the opposite side of the windmill blade due to “sudden headwind” or the like. As a result, a phenomenon occurs in which the rotational speed of the wind turbine blade drops momentarily. In this case, a strong deceleration torque is applied to each element of the speed increaser from the input shaft side. However, when a strong deceleration torque is suddenly applied (unlike acceleration torque is applied), even if the rotation direction of the windmill blade is not reversed, the backlash that has been formed between the tooth surfaces of each gear until then is reduced. A phenomenon that the formation direction is reversed occurs. This is because the input shaft changes from “a state in which a driving force is applied” to “a state in which a braking force is applied”. When the backlash is reversed, the tooth surfaces of the gears directly collide with each other, so that it is considered that a strong impact is applied to the tooth surface (in this case, the surface opposite to that during normal driving). From this state, when the “sudden headwind” stops and accelerates again, the backlash of the tooth surface reverses again. For this reason, after all, when the weather is rough and the wind is rolling, every time such a situation occurs, the collision between the tooth surfaces is repeated, and each tooth surface is frequently impacted from both sides. It will be.

  The present invention has not only a large torque continuously applied during strong winds, but rather a problem of wind speed gear speed increasers. It is assumed that a strong load or impact that occurs instantaneously (peak) on the element has a large effect, and mitigating such a strong instantaneous load or impact is regarded as an “intermediate task”. It was conceived with the idea of solving the above-mentioned original problems by overcoming them.

  In the present invention, a “gap” into which the lubricant can enter is formed in any part other than the part where the gear and the support member rotate relative to each other via the bearing. The gap allows at least two of the gear, the bearing, and the support member to be relatively slightly displaced in the radial direction.

  Now, if the input shaft rotation speed suddenly changes due to "abrupt changes in wind speed or direction", the gearbox will inherently instantly attempt to automatically form the most stable meshing state at that moment. . At this time, according to the present invention, due to the presence of the gap, at least two of the gear, the bearing, and the support member can relatively slightly displace in the radial direction. As a result, the formation mode of the gap changes and the lubricant moves (in and out) within the gap. At the same time, the lubricant moves (especially, the movement to go out of the gap). Resistance occurs. With this resistance, it is possible to damp loads and impacts (if there is no resistance, it will rise sharply as it is).

  The step-up gear for wind power generation according to the present invention functions particularly effectively when incorporated in a wind power generation facility installed in an area where strong winds are easily blown or an area where the wind direction is not stable, i.e., an area where wind turbulence is large. To do.

  According to the present invention, it is possible to obtain a speed-up gear for wind power generation that is small in size, light in weight, and low in cost but has high reliability and long life.

Sectional drawing which shows the principal part of the gearbox for wind power generation which shows an example of embodiment of this invention Sectional drawing which shows the whole structure of the gear box of FIG. Sectional drawing which shows the principal part of the gearbox for wind power generation which concerns on other embodiment of this invention. Sectional drawing which shows the principal part of the step-up gear for wind power generation concerning further another embodiment of this invention. The skeleton figure which shows schematic structure of the planetary gear mechanism of the step-up gearbox for wind power generation concerning further another embodiment of this invention. Front view showing an example of the overall configuration of a conventional (and the present invention) wind power generation facility The perspective view which shows the internal structure of the nacelle of the wind power generation facility of FIG. Sectional drawing which shows an example of the conventional gear box for wind power generation installed in the nacelle of the wind power generation equipment of FIG.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  The schematic configuration of the wind power generation facility in which the speed increaser according to the present invention is incorporated is the same as that already described with reference to FIG. 6 and FIG. Details about the configuration.

  FIG. 1 is a cross-sectional view showing a main part of a speed increasing gear 50 for wind power generation showing an example of an embodiment of the present invention, and FIG. 2 is an overall cross-sectional view thereof.

  First, referring to FIG. 2, the speed increaser 50 for wind power generation includes a planetary gear mechanism 52 in the first stage and first and second parallel shaft gear mechanisms 54 and 56 in the middle stage and the rear stage. The rotation of the main shaft (not shown) input from the input shaft 58 is accelerated by a total of three stages of gear mechanisms 52, 54, 56 and output from the output shaft 60. A generator (similar to the conventional generator 11: see FIG. 7) is connected to the output shaft 60, and predetermined power generation is performed.

  The planetary gear mechanism 52 includes a carrier 62 that is integrated with the input shaft 58, planetary pins 64 that are supported at both ends by the carrier 62, and three that are rotatably supported by the planetary pins 64 (one in FIG. 2). Only the planetary gear 68, the internal gear 70 in which the planetary gear 68 is internally meshed simultaneously, and the sun gear 72 in which the planetary gear 68 is externally meshed simultaneously. In this embodiment, the sun gear 72 is directly formed on the output shaft 80 of the planetary gear mechanism 52, and the internal gear 70 is integrated (fixed) with the casing 74.

  The carrier 62 is configured such that a pair of disk-shaped carrier flanges 62A and 62B are connected and confronted via a connecting portion 62C, and the planetary gear 68 and internal teeth are interposed between the pair of carrier flanges 62A and 62B. A gear 70 and a sun gear 72 are incorporated. The carrier flanges 62A and 62B are rotatably supported by the casing 74 of the gearbox 50 (with the input shaft 58) by bearings 75 and 78.

  The planetary pin 64 is press-fitted into the pair of carrier flanges 62A and 62B and is supported at both ends. The planetary gear 68 is rotatably supported by the planetary pin 64 via a roller bearing 76. That is, in this embodiment, the planetary gear 68 corresponds to the “gear” of claim 1, the roller bearing 76 corresponds to the “bearing”, and the planetary pin 64 corresponds to the “support member”.

  Here, the configuration in the vicinity of the planetary gear of the speed increaser in the present embodiment will be described in more detail with reference to FIG.

  As described above, the planetary gear 68 is rotatably supported by the planetary pin 64 (which is a support member) via the roller bearing 76. In this embodiment, two roller bearings 76 are arranged side by side in the axial direction. Each roller bearing 76 includes an inner ring 76A, an outer ring 76B, rollers (rolling elements) 76C, and a retainer 76D. The inner ring 76A of the roller bearing 76 is positioned in the axial direction between the carrier flanges 62A and 62B via the spacer 82 (82A to 82C). Further, the outer ring 76B of the roller bearing 76 is positioned in the axial direction with respect to the inner ring 76A via the roller 76C, the central spacer 82B, and the retainer 76D.

  The planetary gear 68 includes a center hole 68A. A groove 68B is formed in the center hole 68A, and a retaining ring 84 is engaged with the groove 68B. Thereby, the planetary gear 68 is positioned in the axial direction with respect to the end portions 76A1 and 76B1 of the outer ring 76B of the two roller bearings 76, and the movement of the planetary gear 68 in the axial direction is restricted.

  However, the planetary gear 68 is not particularly restricted by minute movement in the radial direction. The circumferential movement is not restricted at all with respect to at least the roller bearing 76 (the outer ring 76B). That is, in this embodiment, a clearance S1 is formed between the outer ring 76B and the center hole 68A of the planetary gear 68. Specifically, in this embodiment, the clearance S1 is set to be about 0.3% (3/1000) with respect to the outer diameter d1 of the roller bearing 76. This gap S1 enables the planetary gear 68 and the outer ring 76B of the bearing 76 to be relatively displaced in the radial direction relatively. In this embodiment, since the roller bearing 76 is incorporated in a state of being integrated with the planetary pin 64 that is a support member, the planetary gear 68 is configured to be slightly displaced with respect to the roller bearing 76. Yes.

  The planetary gear 68 can be slightly displaced with respect to the roller bearing 76. As a result, the planetary gear 68 can move with respect to the internal gear 70 and the sun gear 72 in addition to a minute displacement in the circumferential direction due to normal backlash. This means that the gap S1 can be further finely displaced in the radial direction.

  The lubricant (lubricating oil) in the gear box 50 can enter the gap S1. The function of the lubricant in the gap S1 will be described in detail later.

  Next, the operation of the speed increasing gear 50 for wind power generation according to this embodiment will be described.

  The rotation of the windmill blade 5 is transmitted to the input shaft 58 of the speed increaser 50 through the main shaft of the rotor head 4. The rotation of the input shaft 58 is input to the planetary gear mechanism 52 as the revolution of the planetary gear 68 through the carrier 62 (carrier flanges 62A and 62B), and the relative rotation of the three of the planetary gear 68, the internal gear 70 and the sun gear 72 is achieved. Thus, the accelerated rotation is output from the sun gear 72 to the output shaft 80 of the planetary gear mechanism 52.

  The rotation of the output shaft 80 of the planetary gear mechanism 52 is amplified by the first parallel shaft gear mechanism 54 via the coupling 79, further amplified by the second parallel shaft gear mechanism 56, and finally the speed increaser. 50 output shafts 60 are taken out. Since the output shaft 60 of the step-up gear 50 is connected to the generator 11, the generator 11 can be rotated after the rotation of the windmill blade 5 is accelerated, and efficient wind power generation is performed. be able to.

  Hereinafter, the operation of the planetary gear mechanism 52 will be described in detail while paying attention to the function of the gap S1.

  When the carrier 62 (carrier flanges 62A, 62B) integrated with the input shaft 58 rotates, the planetary pin 64 revolves around the axis of the planetary gear mechanism 52 as the carrier flanges 62A, 62B rotate. The gear 68 rotates with the sun gear 72 circumscribed and the internal gear 70 inscribed.

  The relative rotation in the circumferential direction between the planetary pin 64 and the planetary gear 68 is realized by the relative rotation of the inner ring 76A and the outer ring 76B of the roller bearing 76 via the roller 76C of the roller bearing 76. This is because the gap S1 is extremely narrow, and therefore, if relative rotation in the circumferential direction is to occur between the outer ring 76B of the roller bearing 76 and the planetary gear 68, the gap S1 exists in the gap S1. This is because shear stress is generated in the lubricant. That is, coupled with the generation of the shear stress, the resistance to the relative rotation of the planetary pin 64 and the planetary gear 68 in the circumferential direction is much larger in the gap S1 than in the roller bearing 76. (Regardless of the presence of the clearance S1), the outer ring 76B of the roller bearing 76 and the planetary gear 68 hardly rotate relative to each other (at least during normal operation).

  On the other hand, during rough weather, especially when strong winds are blowing that frequently change the wind direction, the rotational torque of the windmill blade 5 fluctuates (or suddenly changes), so that it is applied to the planetary gear 68. The revolution propulsion force from the carrier 62 varies in the same manner. As a result, the meshing reaction force received from the internal gear 70 and the sun gear 72 also varies, so that the radial load applied to the gap S1 varies. As a result, a state in which the planetary gear 68 is slightly displaced in the radial direction with respect to the planetary pin 64 (specifically, the outer ring 76B of the roller bearing 76 integrated therewith) is repeated.

  When the gap S1 at a certain portion in the circumferential direction becomes narrow due to this minute displacement, the lubricant present in that portion is pushed out of the gap S1 while being crushed. Conversely, on the opposite side in the diameter direction, the gap S1 increases, and the lubricant enters the gap S1. At this time, in particular, when the gap S1 becomes narrower and the lubricant in the gap S1 is pushed out while being crushed, there is a strong compressive stress on the lubricant and a shear stress caused by being forced to move in a narrow space. Occur.

  Generation of this compressive stress and shear stress prevents the peak load from being transmitted directly (as it is) from one side to the other side between the two members sandwiching the gap S1. That is, if there is no gap S1 between the planetary gear 68 and the outer ring 76B of the roller bearing 76 integrated with the planetary pin 64 which is a support member, it will rise sharply and rise sharply as it is. Transmission of shocking torque is suppressed.

  Further, if the planetary gear 68 that has been rotating integrally within the range of the shearing stress in the circumferential direction of the lubricant in the clearance S1 is between the outer ring 76B of the bearing 76, the circumference exceeding the shearing stress is assumed. When a load in the direction is applied, a “slip” occurs between the planetary gear 68 and the outer ring 76B of the bearing 76. Therefore, it is considered that an impact absorbing effect is exhibited even by this newly generated slip.

  Furthermore, by suppressing the transmission of steep torque fluctuations, the frequency at which the backlash is reversed can be reduced, and even if it is reversed, the impact on the tooth surface during the reversal can be further reduced. This effect is not considered to be small in the case of wind power generation equipment installed in an area where the wind direction is not stable.

  In addition, in the case of the step-up gearbox 50 for wind power generation according to this embodiment, there are three planetary gears 68 and there are a total of six meshing points where power is transmitted. The revolution trajectory (the position of the planetary pin 64 with respect to the carrier 62) always varies due to manufacturing errors. Further, the coaxiality of the internal gear 70 and the sun gear 72 is not necessarily ensured accurately.

  For this reason, in the case of a conventional speed increaser for wind power generation (having a planetary gear mechanism), there is a tendency that a load of transmission torque is easily applied only at a certain “specific meshing point”. Needless to say, if the transmission torque load is strongly received only at a specific meshing point, the damage at the specific meshing point is further enhanced, but this effect is a shocking effect that rises sharply and decreases sharply. This becomes more noticeable when a large torque is applied.

  According to the speed increaser 50 according to this embodiment, the three planetary gears 68 can be slightly displaced in the radial direction with respect to the internal gear 70 and the sun gear 72 by the presence of the gap S1, respectively, There is also an effect that the most stable meshing state can be formed automatically and more easily at that moment. The function that can automatically form this stable meshing state is always maintained not only when shocking torque is applied, but also when the wind direction does not change so rapidly, so fluctuation components in the lower frequency range It is thought that it contributes to absorption of water.

  As a result, the total amount of energy from the windmill blade 5 to the generator 11 is substantially the same due to the presence of the gap S1 and the lubricant in the gap S1, but in particular, the peak value of the load applied to each element is reduced, Instantaneous overload and impact generation can be reduced. As a result, the torque input from the wind turbine blade 5 can be transmitted more stably, and the life of the gearbox can be greatly extended.

  In the above embodiment, the gap S1 is formed between the roller bearing 76 (the outer ring 76B) and the planetary gear 68. However, the position where the gap according to the present invention is formed is limited to this position. It is not done. For example, instead of forming the clearance S1 or in addition to forming the clearance S1, the clearance S2 (illustrated by imaginary lines in FIG. 1) is provided between the inner ring 76A of the roller bearing 76 and the planetary pin (support member) 64. ), The same effect can be obtained.

  The size of the gap is not limited to 3/1000 of the inner diameter of the gap (in the above embodiment, the outer diameter of the outer ring 76B of the roller bearing 76). Changing the formation position, number, or size (interval) of the gap changes the inertial mass of the member that can be finely displaced and the manner of displacement, so the frequency component of the region that can absorb fluctuation (load fluctuation) well Can be adjusted. For this reason, it is good to set suitably considering the property of the wind actually blown in the area where the wind power generation facility is installed.

  FIG. 3 shows an example of another embodiment of the present invention.

  In this embodiment, the planetary gear 83 includes a planetary gear portion 83A and a planetary pin portion 83C that supports the planetary gear portion 83A. As is apparent from this configuration example, the “gear” in the present invention can be defined as a member or member group that is rotatably supported by a support member via a bearing and has a tooth portion. Then, the planetary gear 83 (including the planetary pin portion 83C) is rotated with respect to the carrier 84 via a roller bearing 86 by a carrier 84 (a pair of carrier flanges 84A and 84B) which is a support member disposed on both sides. Both ends are supported as possible. The planetary gear 83 is rotatable relative to the carrier flanges 84A and 84B via the roller bearing 86. The roller bearing 86 includes an inner ring 86A, an outer ring 86B, and a roller 86C.

  The clearance S3 according to the present invention is formed between the carrier 84 (the pair of carrier flanges 84A and 84B) and the bearing 86 (the outer ring 86B). That is, in this embodiment, the planetary gear 83 (including the planetary pin portion 83C) corresponds to the “gear” of the present invention, and the carrier 84 (the pair of carrier flanges 84A and 84B) This corresponds to a “support member” that is rotatably supported via the bearing 86.

  Also with the configuration according to this embodiment, the planetary gear 83 can be slightly displaced in the radial direction with respect to the carrier 84 as a support member, as in the above-described embodiment. However, since the planetary gear 83 according to this embodiment includes the planetary pin portion 83C integrally, the inertial mass of the member that is slightly displaced is larger than that of the previous embodiment. For this reason, depending on the design, there is a possibility that fluctuation absorption in a lower frequency region can be satisfactorily performed.

  Also in this embodiment, a gap S4 (illustrated by an imaginary line in FIG. 3) is formed between the inner ring 86A of the roller bearing 86 and the planetary gear 83 instead of or in addition to the gap S3. You may do it. Further, instead of or in addition to the formation of the gap S3 (or S4) in the carrier 84, a gap S7 is provided between the planetary gear portion 83A and the planetary pin portion 83C of the planetary gear 83 (FIG. 3). ), A ring-shaped member (not shown) as described later may be disposed between the planetary gear portion 83A and the planetary pin portion 83C. As a result, in addition to the fluctuation absorbing effect due to the gap S3 (or S4) in the carrier 84, an effective fluctuation absorbing effect can be obtained between the planetary gear portion 83A and the planetary pin portion 83C (depending on the frequency component to be absorbed). It will be obtained. Note that the planetary gear portion 83A and the planetary pin portion 83C are not separated and may be formed integrally.

  Since other configurations are the same as those of the previous embodiment, the same reference numerals are given to the same or functionally similar parts in FIG.

  FIG. 4 shows an example of still another embodiment of the present invention.

  In the speed increasing device 91 for wind power generation according to this embodiment, the ring-shaped member 88 is formed between the planetary gear 68 and the bearing 76 (the outer ring 76B) based on the configuration of the embodiment of FIGS. Is interposed. A small gap S5 is formed on the inner peripheral side of the ring-shaped member 88, and a larger gap S6 is formed on the outer peripheral side. Accordingly, the presence of the two gaps S5 and S6 allows the planetary gear 68 to be slightly displaced in the radial direction with respect to the planetary pin 64 that is a support member. One of the gaps S5 and S6 may not be provided.

  In this embodiment, the ring-shaped member 88 itself can be slightly displaced in the radial direction with respect to the planetary pin 64 (and the outer ring 76B of the roller bearing 76 integrated therewith), and this ring-shaped member. Since the planetary gear 68 is configured to be slightly displaceable in the radial direction with respect to 88, the frequency region in which the fluctuation component can be satisfactorily absorbed can be further expanded.

  Also in this embodiment, depending on the frequency region intended to absorb fluctuation, between the planetary pin 64 and the bearing 76 (the inner ring 76A) as a support member, as in the embodiment of FIGS. It is effective to form the gap S2 (illustrated by an imaginary line in FIG. 4).

  Further, such a ring-shaped member 88 is replaced with the planetary gear 68 and the outer ring 76B of the bearing 76, or in addition to the planetary gear 68 and the outer ring 76B of the bearing 76, the roller bearing 76 is provided. It may be arranged between the inner ring 76A and the planetary pin 64.

  The other configurations are the same as those of the embodiment of FIGS. 1 and 2, and therefore, the same or similar parts in FIG. 4 as those of the embodiment of FIGS. Omitted.

  Such an arrangement of ring-shaped members is also applicable to the embodiment shown in FIG. In the case of attaching a ring-shaped member in the embodiment shown in FIG. 3, a pair of carrier flanges 84A, 84B, between the outer ring 86B of the bearing 86, or in the planetary gear 83 in which the planetary pin portion 83C is integrated. The ring-shaped member may be disposed either or both of the planetary pin portion 83C and the inner ring 86A of the bearing 86.

  If necessary, in the present invention, the ring-shaped member may be disposed between the gear and the bearing, or between the bearing and the support member, and further, only one member may be disposed in any case. It does not have to be arranged. When arranging a ring-shaped member, the gap may be provided only on the outer peripheral side of the ring-shaped member, only on the inner peripheral side, or on both the outer peripheral side and the inner peripheral side. Also good.

  As described above, in the present invention, there is no particular limitation on the position and size at which the gap is specifically formed. In short, as a result, the lubricant can enter any part of the bearing other than the part that rotates relative to the bearing (with or without a ring-shaped member), and the gear, the bearing, and the support member. It is sufficient that at least two of the members are formed so as to be relatively minutely displaceable in the radial direction. In this respect, there may be no ring-shaped member, and a plurality of members may be arranged.

  If the position, size, or phase at which the gap is formed differs, the frequency range in which fluctuations can be absorbed varies, and therefore more effective fluctuation absorption is possible taking into account the characteristics of the area where the wind power generation equipment is installed. Will be able to do.

  In the above embodiment, a planetary gear mechanism having a simple planetary gear structure is employed as the planetary gear mechanism. However, the planetary gear mechanism in the present invention is not limited to a planetary gear mechanism having a simple planetary gear structure. Absent. For example, JP-A-2003-278849 discloses a planetary gear mechanism as shown in FIG.

  This planetary gear mechanism 93 has two sun gears 94A and 94B of the same number of teeth integrated with the planetary pin portion 94C, and has a sun gear and is engaged with the planetary gear portions 94A and 94B and is different. Two internal gears 95A and 95B having the number of teeth are provided. When this planetary gear mechanism 93 is applied to a wind power speed increaser (not shown), one of the two types of internal gears 95A and 95B is connected to the input shaft 92, The carrier 97 (which may be a pair with the planetary gear 94 interposed therebetween if necessary) is used in such a manner that it is connected to the output shaft 96.

  Although this planetary gear mechanism 93 has a slightly complicated structure, there is an advantage that the speed increaser can be designed in various ways. For this reason, it can be effectively used mainly in terms of dimensions and shapes as a speed increaser for wind power generation with large installation space restrictions.

  For example, since the planetary gear mechanism 93 does not have the sun gear as described above, it is easy to form a large hollow portion (not shown) in the central portion. For this reason, when it becomes necessary to arrange some control devices, sensors, pipes and the like around (or inside) the input shaft 92, the hollow portion can be used effectively. Further, the planetary gear mechanism 93 can be easily designed to increase the speed by about 5 to 30 times, so if necessary, it is possible to use a single stage of the rear stage parallel shaft gear mechanism (not shown). In this case, the weight and the axial dimension can be reduced.

  In the case of a speed increasing device for wind power generation having the planetary gear mechanism 93 having such a structure, specifically, a “planetary gear 94” in which two planetary gear portions 94A and 94B and a planetary pin portion 94C are integrated is provided. The structure is such that the carrier 97, which is a support member on both sides thereof, is supported at both ends via a bearing (not shown). Therefore, the present invention can be applied with a configuration similar to the configuration shown in FIG.

  The planetary gear mechanism 93 has a structure in which one of the two internal gears 95A and 95B is rotatably supported by the casing 99 via the bearing 98, depending on the design. It is also possible to form a clearance according to the present invention between the internal gear 95A, the bearing 98, and the casing 99 supporting the internal gear 95A.

  In other words, the “gear” according to the present invention is not limited to the planetary gear, and can be applied to an internal gear or a sun gear depending on the configuration of the planetary gear mechanism.

  As described above, various configurations are known for the planetary gear mechanism. Even when the planetary gear mechanism having any configuration is adopted, the lubricant is applied to any portion of the bearing other than the relatively rotating portion. The scope of the present invention is not limited as long as it is capable of entering, and is formed with a gap that allows at least two of the specific gear, bearing, and support member to be relatively finely displaced in the radial direction. Therefore, the effects of the present invention can be obtained accordingly. However, it is preferable to apply the present invention to the support portion of the “planetary gear” of the “simple planetary gear mechanism”. It has a simple structure and is inexpensive, and the planetary gear has a revolution component and a rotation component and rotates while being sandwiched between an internal gear and a sun gear. This is because the effect of being able to make a minute displacement in the radial direction is very prominent. The number of planetary gears is three in the above embodiment, but may be two or four or more, and is not particularly limited.

  In the above embodiment, a roller bearing is employed as the bearing. However, in the present invention, the type of bearing is not necessarily limited to the roller bearing. Depending on the power generation capacity or the configuration of the planetary gear mechanism, for example, a ball bearing or a sliding bearing may be employed. Further, in the above embodiment, all the bearings have both the inner ring and the outer ring. However, in the present invention, the bearing in which the inner ring or the outer ring is omitted may be provided on the side where no gap is formed. . Even when a bearing having any structure is employed, there is a gap according to the present invention in addition to the original relative rotation (between the gear and the support member) as the bearing. For example, when a sliding bearing is employed as the bearing, relative rotation during normal operation between the gear and the support member is performed only at the sliding bearing portion. Accordingly, a gap according to the present invention is separately present in addition to the portion where the relative rotation is performed in the slide bearing. In other words, a gap is unavoidably present in the “part of relative rotation in the bearing”, but the gap of the part of relative rotation in the bearing is not included in the gap of the present invention. The “gap between the relative rotating parts of the bearing” is a gap between the inner ring, the rolling element, and the outer ring, for example, if the bearing has inner and outer rings. That is, the rolling element—the gap between the members constituting the rolling surface of the rolling element.

DESCRIPTION OF SYMBOLS 1 ... Wind power generation equipment 3 ... Nacelle 4 ... Rotor head 5 ... Windmill blade 11 ... Generator 50 ... Speed up gear 52 ... Planetary gear mechanism 58 ... Input shaft 60 ... Output shaft 62 ... Carrier 64 ... Planetary pin 68 ... Planetary gear 70 ... Internal gear 72 ... Sun gear 74 ... Casing 76 ... Roller bearing 88 ... Ring-shaped members S1 to S7 ... Clearance

Claims (8)

In the gearbox for wind power generation equipped with a planetary gear mechanism,
A gear constituting one element of the planetary gear mechanism;
A support member that rotatably supports the gear via a bearing,
The gear is a planetary gear of the planetary gear mechanism;
The planetary gear is rotatably supported with respect to the planetary pin by a planetary pin as the support member;
The bearing includes an outer ring;
Between the outer ring before Symbol planetary gear and the bearing, the lubricant is a possible approach, and the planetary gears, bearings, and at least two parties to each other of the support member, minute displacement relative radial A speed increaser for wind power generation, characterized in that a gap is made possible. In the gearbox for wind power generation equipped with a planetary gear mechanism,
A gear constituting one element of the planetary gear mechanism;
A support member that rotatably supports the gear via a bearing,
The gear is a planetary gear of the planetary gear mechanism;
The planetary gear is rotatably supported with respect to the planetary pin by a planetary pin as the support member;
The bearing has an inner ring;
Between the inner ring before Symbol planetary pin and the bearing, and lubricant was possible approach, and the planetary gears, bearings, and at least two parties to each other of the support member, can minute displacement relative radial A speed increaser for wind power generation, characterized in that a gap is formed . In the gearbox for wind power generation equipped with a planetary gear mechanism,
A gear constituting one element of the planetary gear mechanism;
A support member that rotatably supports the gear via a bearing,
The gear is a planetary gear of the planetary gear mechanism;
Planetary gear, each planetary pin to rotate said planetary gears and integrally, together is rotatably supported by the carrier by the carrier of the planetary gear mechanism as the supporting member,
The bearing includes an outer ring;
A lubricant can enter between the carrier and the outer ring of the bearing, and at least two of the planetary gear, the bearing, and the support member can be relatively minutely displaced in the radial direction. A speed increaser for wind power generation, characterized in that a gap is formed . In the gearbox for wind power generation equipped with a planetary gear mechanism,
A gear constituting one element of the planetary gear mechanism;
A support member that rotatably supports the gear via a bearing,
The gear is a planetary gear of the planetary gear mechanism;
Planetary gear, each planetary pin to rotate said planetary gears and integrally, together is rotatably supported by the carrier by the carrier of the planetary gear mechanism as the supporting member,
The bearing has an inner ring;
A lubricant can enter between the carrier and the inner ring of the bearing, and at least two of the planetary gear, the bearing, and the support member can be relatively displaced in the radial direction relatively. A speed increaser for wind power generation, characterized in that a gap is formed . In any one of Claims 1-4 ,
The speed increasing device for wind power generation, wherein the planetary gear mechanism is a simple planetary gear mechanism. In any one of Claims 1-5 ,
A ring-shaped member is interposed between the planetary gear and the bearing,
The speed increaser for wind power generation, wherein the gap is formed in at least one of an inner peripheral side and an outer peripheral side of the ring-shaped member. In any one of Claims 1-6 ,
A ring-shaped member is interposed between the bearing and the support member,
The speed increaser for wind power generation, wherein the gap is formed in at least one of an inner peripheral side and an outer peripheral side of the ring-shaped member. In claim 6 or 7 ,
A speed increaser for wind power generation, comprising a plurality of the ring-shaped members.

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