JP5917070B2 - Wind speed booster with locked train mechanism - Google Patents

Description

  The present invention relates to a step-up gear for wind power generation provided with a locked train mechanism.

  For example, Patent Document 1 refers to a so-called locked train mechanism in which the power of one input shaft is divided and transmitted to two intermediate rotating shafts and is aggregated and integrated as power of one output shaft again. A power transmission system for a marine vessel propulsion turbine having a power transmission mechanism is disclosed.

  Because the locked train mechanism is realized by distributing the intermediate stage that performs deceleration or speed increase to a plurality of intermediate shafts, it can be configured to reduce the speed reducer and speed increaser that handle large torque relatively compactly. Therefore, there are many application examples in the field of large-scale power transmission equipment such as ships and wind power generation equipment.

  Japanese Patent Application Laid-Open No. 2003-228561 discloses a speed increasing device for wind power generation that includes a locked train mechanism that divides the power of one input shaft into eight intermediate rotation shafts.

JP-A-48-91457 (FIG. 1) US2003 / 0015052A1 (FIGS. 1 to 3)

  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, since wind power generation equipment is equipment installed in a natural environment, it sometimes receives turbulent winds and gusts. Such turbulent winds and gusts sometimes generate unexpected torque, which can cause problems with the gearbox. 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. The original problem is to provide a wind power booster equipped with a long-life locked train mechanism.

The present invention relates to a gearbox for wind power generation provided with a locked train mechanism, a gear constituting one element of the locked train mechanism, a shaft integrated with the gear, and the shaft. A support member rotatably supported via the bearing, and a gap is formed between at least one of the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member. A plurality of ring-shaped members provided at least between the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member. There is interposed, in at least one of the inner periphery side and the outer periphery side of the ring-shaped member, by Rukoto the are gap formed, is obtained by solving the original problem above.
The present invention also provides a gearbox for wind power generation provided with a locked train mechanism, a gear constituting one element of the locked train mechanism, a shaft integrated with the gear, and the shaft. A support member rotatably supported via a bearing, and a gap is formed between at least one of the inner ring and the shaft of the bearing and between the outer ring of the bearing and the support member, A liquid is sealed in the gap or a minute space including the gap, and the minute space including the gap or the gap is isolated and sealed from the space in the speed increaser , and between the inner ring of the bearing and the shaft, and A plurality of ring-shaped members are interposed between at least one of the outer ring of the bearing and the support member, and the gap is formed on at least one of the inner peripheral side and the outer peripheral side of the ring-shaped member . By the above original problem Resolve those were.
The present invention also provides a gear for constituting a component of the locked train mechanism, and a shaft that rotatably supports the gear via a bearing in a speed increasing device for wind power generation including the locked train mechanism. A gap is formed between at least one of the gear and the outer ring of the bearing, and between the shaft and the inner ring of the bearing, and the liquid is sealed in the minute space including the gap or the gap. The gap or the minute space including the gap is isolated and sealed from the space in the speed increaser , and at least one of the gap between the gear and the outer ring of the bearing and the axis and the inner ring of the bearing. In addition, a plurality of ring-shaped members are interposed, and the gap is formed on at least one of the inner peripheral side and the outer peripheral side of the ring-shaped member, thereby solving the above-mentioned original problem.

  In the present invention, the locked train mechanism transmits the power of the input shaft to a plurality of intermediate rotating shafts having a larger number than the input shaft, and again transmits the power of the output shaft having a smaller number than the intermediate rotating shaft. It is defined as a power transmission mechanism integrated as

  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 the generator is connected to the tip of the speed increaser as a load, each element of the speed increaser cannot immediately follow the acceleration torque due to inertia and increase the rotation speed. 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.

  When the power applied to the input shaft is power intentionally generated by an engine, a motor, or the like, there is no possibility that the above-described extreme peak torque or the like is applied to the input shaft. However, in the gearbox of wind power generation equipment, the range of torque assumed to be applied to the input shaft (because it uses natural power) is not only very wide, but also changes instantaneously. There is also a problem that the assumption itself is difficult for the torque to be generated.

  Especially, in the case of a gearbox equipped with a locked train mechanism, when peak torque that momentarily rises from the input shaft enters, or when the torque suddenly drops as the backlash reverses , Torque is not necessarily transmitted uniformly to the gears on the plurality of intermediate rotation shafts, and depending on manufacturing errors, assembly errors, etc., a specific intermediate rotation with a small (or no) backlash among the plurality of intermediate shafts Only the power transmission system via the shaft is susceptible to a heavy burden.

  In addition, each intermediate rotating shaft of the locked train mechanism, its bearings, and the gears on the intermediate rotating shaft have a strength setting that allows for torque to be distributed to multiple transmission systems. Therefore, it is assumed that such a torque that suddenly changes suddenly concentrates only on a specific transmission system among a plurality of transmission systems. Not done. Therefore, it is surmised that the speed-up gear of the locked train mechanism has formed a situation where it is disadvantageous in terms of its configuration.

  The present invention has not only a large torque continuously applied during strong winds, but rather a problem of wind speed gear speed increasers. The starting point of the idea is to pay attention to the fact that a strong load or impact that occurs instantaneously (peak) on the element has a great influence. In particular, in a gearbox equipped with a locked train mechanism, when such a strong momentary load or impact is applied, the inherent torque distribution action of the locked train mechanism does not function well, but it is rather disadvantageous. It was conceived as an “intermediate task” that the situation was formed, and was conceived with the idea of solving the above-mentioned original problem by overcoming this intermediate task.

  In the present invention, at least two of the gear, the bearing, and the support member are slightly displaced relatively in the radial direction at any part other than the part where the gear and the support member rotate relative to each other via the bearing. A gap that allows this is formed.

  According to the present invention, when the input shaft rotation speed changes suddenly due to the presence of this gap, for example, due to a sudden change in wind speed or direction, the speed increaser instantaneously enters the most stable meshing state at that time. Can be configured automatically. That is, each gear is automatically displaced in a direction in which the load that is instantaneously applied becomes more even, and only a specific gear can be prevented from receiving a strong load. Therefore, the original load distribution action of the locked train mechanism can be sufficiently exhibited, and the peak load on each part of the speed increaser can be reduced.

  According to the present invention, it is possible to obtain a step-up gear for wind power generation equipped with a locked train mechanism having high reliability and long life while being small, light, and low cost.

The perspective view which shows typically the principal part of the gearbox for wind power generation provided with the locked train mechanism which shows an example of embodiment of this invention. The perspective view which looked at the principal part of the gearbox of FIG. 1 from another angle Sectional drawing which showed typically the support structure of each axis | shaft of the gearbox of FIG. Similarly, a cross-sectional view schematically showing another support structure of each axis The side view which shows an example of the whole structure of the wind power generation facility to which this invention was applied The perspective view which shows the internal structure of the nacelle of the wind power generation facility of FIG.

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

  First, a schematic configuration around the gearbox of the wind power generator will be described with reference to FIGS. 5 and 6. The wind turbine generator 1 includes a column 2 that is erected on a foundation 6, a nacelle 3 that is installed at the upper end of the column 2, and a rotor head 4 that is rotatably assembled to the nacelle 3. ing. 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 a low speed (although there is torque) can be increased to a faster rotation, and the power generation output can be efficiently obtained from the generator 11. In FIG. 6, reference numeral 12 is a transformer, 13 is a controller, 14 is an inverter, 15 is an inverter cooler, and 16 is a lubricating oil cooler.

  Hereinafter, the structure of the step-up gear 20 for wind power generation provided with the locked train mechanism which concerns on this invention is demonstrated in detail. Here, the locked train mechanism divides and transmits the power of the input shaft to a plurality of intermediate rotating shafts having a larger number than the input shaft, and again as the power of the output shaft having a smaller number of intermediate rotating shafts. It means the power transmission mechanism to be integrated.

  First, the basic configuration of the locked train mechanism employed in the present embodiment will be described based on FIGS. 1 and 2, and then the characteristic part of the present embodiment will be described based on FIG. 3. The basic configuration itself is the same as that in US2003 / 0015052A1.

  FIG. 1 is a perspective view schematically showing a main part of a speed increasing gear 20 for wind power generation provided with a locked train mechanism 21, and FIG. 2 is a schematic view of the main part of the same speed increasing machine 20 from another angle. The perspective views shown respectively are shown. It should be noted that there are some unsharp axes due to the drawing angle.

  The speed increaser 20 uses the eight first gears to transmit the rotation transmitted from the rotor head 4 shown in FIGS. 5 and 6 to the input shaft (not shown) via the input gear 22 incorporated in the input shaft. It is divided and transmitted to the intermediate rotating shafts 31 to 38 and finally integrated into one output shaft (not shown). A specific configuration will be described below.

  The input gear 22 meshes with the eight first intermediate gears 41 to 48 provided on the eight first intermediate rotation shafts 31 to 38 at a position where the outer periphery is equally divided into eight. Thus, the power transmitted from the rotor head 4 side to the single (one) input shaft is transmitted via the input gear 22 in a state of being divided into the eight first intermediate rotating shafts 31 to 38. The

  Of the eight first intermediate rotation shafts 31 to 38, half (four) first intermediate rotation shafts 31, 33, 35, and 37 are on the axial rotor head side (front side) of each input gear 22. The front stage side second intermediate gears 51, 53, 55, and 57 are provided at the ends of the front side. Further, the remaining first intermediate rotation shafts 32, 34, 36, and 38 are provided with rear-stage second intermediate gears 52, 54, 56, and 58 at the respective end portions on the counter-rotor head side (rear-stage side). ing. That is, four first intermediate gears 41 to 48 on the first intermediate rotation shafts 31 to 38 are alternately arranged on the front side and the rear side in the axial direction with respect to the input gear 22.

  The four front-stage second intermediate gears 51, 53, 55, 57 provided on the front-stage side are front-stage-side third intermediate gears provided on the four second intermediate rotating shafts 61-64 on the axial front-stage side. The gears 71, 73, 75, and 77 are engaged. The four second-stage second intermediate gears 52, 54, 56, 58 provided on the rear-stage side are rear-stage-side third gears provided on the same four second intermediate rotation shafts 61 to 64 on the rear-stage side in the axial direction. The intermediate gears 72, 74, 76, and 78 mesh with each other.

  As a result, the power divided and transmitted to the eight first intermediate rotating shafts 31 to 38 is collected and integrated into the four second intermediate rotating shafts 61 to 64.

  Fourth intermediate gears 81 to 84 are provided at rear end portions of the four second intermediate rotating shafts 61 to 64, respectively. The four fourth intermediate gears 81 to 84 mesh with the fifth intermediate gears 101 to 104 provided on the four third intermediate rotation shafts 91 to 94, respectively.

  Of the four third intermediate rotation shafts 91 to 94, the two third intermediate rotation shafts 91 and 93 are provided with rear-stage sixth intermediate gears 111 and 113 on the rear-stage side of the fifth intermediate gears 101 and 103, respectively. Yes. In the remaining two third intermediate rotation shafts 92 and 94, front-stage sixth intermediate gears 112 and 114 are provided on the front-stage side of the fifth intermediate gears 102 and 104.

  The rear-stage sixth intermediate gears 111 and 113 mesh with the rear-stage seventh intermediate gears 131 and 133 of the fourth intermediate rotation shaft 121 (which is one of the two fourth intermediate rotation shafts 121 and 122). ing. The front-stage sixth intermediate gears 112 and 114 mesh with the front-stage seventh intermediate gears 132 and 134 of the other fourth intermediate rotation shaft 122.

  As a result, the power divided and transmitted to the four third intermediate rotating shafts 91 to 94 is aggregated and integrated as the power of the two fourth intermediate rotating shafts 121 and 122.

  In this embodiment, the rotation of the two fourth intermediate rotating shafts 121 and 122 is the same as the method transmitted from the four third intermediate rotating shafts 91 to 94 to the two fourth intermediate rotating shafts 121 and 122. (This method) is further integrated into a single output shaft (not shown) and is configured to drive the one generator 11 described above. In addition, it is good also as a structure which drives two generators directly in parallel by making the two 4th intermediate rotating shafts 121 and 122 into the output shaft of the gearbox 20. FIG.

  In the step-up gear 20 according to this embodiment, one input shaft (not shown), eight first intermediate rotation shafts 31 to 38, four second intermediate rotation shafts 61 to 64, and four Third intermediate rotation shafts 91 to 94, two fourth intermediate rotation shafts 121 and 122, and one output shaft (not shown) are provided.

  Here, when these “shafts” are schematically represented by the symbol Sa1, the support configuration of these “shafts” is any (the number of gears G1, G2 incorporated in the shaft Sa1 Basically, for example, it can be represented by the support structure shown in FIG. 3 or FIG.

  First, the support structure as shown in FIG. 3 will be described.

  In the support structure shown in FIG. 3, the gears G1, G2 and the shaft Sa1 are integrated, and the shaft Sa1 is supported by the casings Ca1, Ca2 as support members via the bearings B1, B2. All the “shafts” already described can be supported by the support structure of FIG. Note that the shaft Sa1 and the gears G1 and G2 may be configured as an integral (single) member or may be configured to be integrated by connecting separate members.

  3, the inner rings B1a and B2a of the bearings B1 and B2 and the shaft Sa1 can be relatively slightly displaced in the radial direction between the inner rings B1a and B2a of the bearings B1 and B2 and the shaft Sa1. A gap S1 is formed. In addition, in the example of FIG. 3, in addition to the clearance S1, between the outer rings B1b and B2b of the bearings B1 and B2 and the casings (support members) Ca1 and Ca2, the outer rings B1b and B2b of the bearings B1 and B2 A gap S2 that allows the casings Ca1 and Ca2 to be relatively displaced in the radial direction relative to each other is also formed.

  In this embodiment, the gaps S1 and S2 are set to have a size (in the radial direction) of about 0.3% (3/1000) with respect to the outer diameter db of the bearings B1 and B2.

  The setting of the sizes of the gaps S1 and S2 is an example. If the formation position (which axis is formed), the number of formations, or the size (interval) of the gaps S1 and S2 is changed, the mode of displacement of the member (or member group) that can be minutely displaced differs. It is possible to adjust a frequency component in a region where the load fluctuation can be satisfactorily absorbed. From this viewpoint, for example, one of the gaps S1 and S2 may not be provided, and the size of the gaps S1 and S2 may be different depending on the frequency component and amplitude of the region in which the fluctuation is to be absorbed. It is valid.

  The shaft Sa1 and the inner rings B1a and B2a of the bearings B1 and B2 can be relatively displaced in the radial direction (or the casings Ca1 and Ca2 and the outer rings B1b and B2b of the bearings B1 and B2 are relatively minute in the radial direction. As a result, it is possible to change the substantial pitch circles d1 and d2 with the counterpart gear (not shown in FIG. 5) meshing with the gears G1 and G2 incorporated in the shaft Sa1. It is synonymous with that. If the pitch circles d1 and d2 are changed, the meshing state between the gears G1 and G2 incorporated in the shaft Sa1 and the mating gear naturally changes.

  It should be noted that the “shaft” that is the object of forming the gap according to the present invention includes each of the intermediate rotating shafts (with the divided power) (eight first intermediate rotating shafts 31 to 38, four second intermediate rotating shafts 61). -64, four third intermediate rotating shafts 91-94, and two fourth intermediate rotating shafts 121, 122) are included, for example, for example, only one input shaft or one output shaft. You may make it apply invention. Since the relative displacement in the radial direction is literally “relative”, for example, when applied to the input shaft, the input gear 22 on the input shaft and the eight first intermediate rotating shafts 31 to 38 are applied. This is because the relative position between can be adjusted.

  The lubricant in the gear box 20 is filled in the gaps S1 and S2. The filling of the lubricant is basically performed by a normal method of lubricating the bearings B1 and B2, for example, a structure in which the bearings B1 and B2 are immersed in the lubricant contained in the gearbox 20. It's okay. In the present embodiment, the members facing each other through the gaps S1 and S2 basically move integrally (does not rotate relative to each other), and thus, for example, an automatic alignment function by radial displacement (described later) is called. When attention is paid only to the point, it is not always necessary that the gaps S1 and S2 are always “maintained with the lubricant completely”. However, in order to obtain an appropriate damper effect, which will be described later, and to extend the service life, it is desirable that the lubricant is surely filled in the gaps S1 and S2.

  Therefore, as a device for always filling the gaps S1 and S2 satisfactorily, it is effective to form a lubrication passage 150 that opens in the gap as shown by a broken line in FIG. is there. When the lubrication passage 150 is formed, the axial passage 152 formed at the position of the axial center O1 in the shaft Sa1, the radial passages 154 and 156 communicating with the axial passage 152 and opening into the clearances S1 and S2; In this way, it is possible to construct a lubrication system using a pumping action by centrifugal force with a simple configuration.

  Next, the effect | action of the gearbox 20 for wind power generation which concerns on this embodiment is demonstrated.

  The rotation of the windmill blade 5 is transmitted to the input shaft (not shown) of the speed increaser 20 via the main shaft of the rotor head 4 and the input gear 22 rotates. Then, the eight first intermediate rotating shafts 31 to 38 are simultaneously rotated in the same direction by meshing between the input gear 22 and the first intermediate gears 41 to 48. Thereby, the power of a single input shaft (input gear 22) is divided into eight first intermediate rotation shafts 31 to 38.

  When the eight first intermediate rotation shafts 31 to 38 rotate, the meshing of the four front-stage second intermediate gears 51, 53, 55, 57 and the front-stage third intermediate gears 71, 73, 75, 77, and The four second intermediate rotating shafts 61 to 64 are engaged with the remaining four rear stage second intermediate gears 52, 54, 56, and 58 and the rear stage third intermediate gears 72, 74, 76, and 78. Rotate. As a result, the power of the eight first intermediate rotating shafts 31 to 38 is integrated and integrated into the four second intermediate rotating shafts 61 to 64.

  When the four second intermediate rotation shafts 61 to 64 rotate, the four third intermediate rotation shafts 91 to 94 rotate through the meshing of the fourth intermediate gears 81 to 84 and the fifth intermediate gears 101 to 104. . When the four third intermediate rotation shafts 91 to 94 rotate, the two fourth intermediate rotation shafts 121 are engaged with the rear-stage sixth intermediate gears 111 and 113 and the front-stage sixth intermediate gears 112 and 114. , 122 rotate. The rotation of the two fourth intermediate rotating shafts 121 and 122 is integrated into one output shaft through two gears (not shown).

  As a result, the power from the wind force input from the rotor head 4 side is eventually divided and transmitted from one input shaft to the eight first intermediate rotating shafts 31 to 38, and further four second intermediate rotating shafts. It is transmitted through the shafts 61 to 64, the four third intermediate rotating shafts 91 to 94, and the two fourth intermediate rotating shafts 121 and 122 while being consolidated and integrated again into one output shaft. Become.

  Since the output shaft of the speed increaser 20 is connected to the generator 11 (FIG. 6), the generator 11 can be rotated after the rotation of the windmill blade 5 is increased by the above configuration, which is efficient. Wind power generation.

  Hereinafter, the operations related to the gaps S1 and S2 will be described in detail with reference mainly to FIG.

  When the rotor head 4 rotates, the shaft Sa1 rotates with respect to the casings Ca1 and Ca2 via the bearings B1 and B2. At this time, a relative rotation hardly occurs between the shaft Sa1 and the inner rings B1a and B2a of the bearings B1 and B2 and between the casings Ca1 and Ca2 and the outer rings B1b and B2b of the bearings B1 and B2. This is because the rolling resistance of the bearings B1 and B2 is originally small, while the clearances S1 and S2 are extremely narrow, and if the relative rotation is attempted, shearing stress is applied to the lubricant in the clearances S1 and S2. This is because the resistance to the relative rotation becomes very large.

  Here, in rough weather, especially when a strong wind is blowing such that the wind direction changes frequently, the rotational torque of the windmill blade 5 fluctuates and sometimes changes suddenly. The meshing reaction force of G2 also varies, and as a result, the radial load applied to the clearance S1 of the shaft Sa1 integrated with the gears G1 and G2 (or the clearance S2 with the casing Ca1) varies.

  As a result, each shaft Sa1 is automatically aligned by a small radial displacement, and automatically shifts to a state where the meshing state of the gears G1 and G2 with the counterpart gear is most stable. As a result, the plurality of shafts Sa1 can jointly handle the peak torque, and the peak torque is prevented from being concentrated and applied only to the specific shaft Sa1.

  This self-aligning function is used not only when peak torque occurs, but also when strong torque is continuously input, so the torque of the input shaft is divided into multiple axes. The original function of the locked train that is transmitted can be fully exhibited.

  Further, when the shaft Sa1 is slightly displaced, the shaft Sa1 is displaced while narrowing an interval of a certain portion in the circumferential direction of the gap S1 existing on the outer periphery (while pushing the lubricant separately). At this time, the gap S1 on the diametrically opposite side tends to be wider and is displaced while drawing in the surrounding lubricant. In the gap S2, an action almost opposite to the action of the gap S1 occurs. Therefore, after all, the lubricant in the gaps S1 and S2 functions as a damper with respect to the displacement of the shaft Sa1. As a result, if there is no clearance S1, S2 (that is, the shaft Sa1 and the inner rings B1a and B2a of the bearings B1 and B2 or the outer rings B1b and B2b of the bearings B1 and B2 and the casings Ca1 and Ca2 are in direct contact with each other. Therefore, it is possible to prevent a shocking torque that suddenly rises sharply and drops sharply immediately after that from being transmitted as it is.

  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.

  Furthermore, suppose that between the gears G1 and G2 and the inner rings B1a and B2a of the bearings B1 and B2 that have been rotated integrally within the range of the shear stress in the circumferential direction of the lubricant in the gaps S1 and S2 until then. Or, when a circumferential torque exceeding the shear stress is applied between the casings Ca1 and Ca2 and the outer rings B1b and B2b, between the gears G1 and G2 and the inner rings B1a and B2a of the bearings B1 and B2, Alternatively, “slip” occurs between the casings Ca1 and Ca2 and the outer rings B1b and B2b. The slip generated in the gaps S1 and S2 functions to release the huge load particularly when a huge load is applied that momentarily destroys the speed increaser 20 itself.

  As a result, according to the present embodiment, the inherent torque dispersion effect of the locked train mechanism can be utilized to the maximum, and at the same time, each element (shaft Sa1, bearings B1, B2, or gears G1, G2) can be used. Etc.), the service life of the gearbox 20 can be greatly extended.

  As already introduced, each axis of the locked train mechanism 21 can be supported by a support structure as shown in FIG. 4, for example. That is, in the support structure of FIG. 4, the bearings B3 and B4 that support the shaft Cs1 are interposed between the gears G3 and G4 and the shaft Cs1, and the bearings B3 and B4 are integrated with the casings Ca3 and Ca4 and the like. It is incorporated in the outer periphery of the support shaft Cs1, which is a support member. In the case of this support configuration, a gap S3 according to the present invention is formed between the support shaft Cs1 and the inner rings B3a and B4a of the bearings B3 and B4.

  Further, in the configuration of FIG. 4, a ring-shaped member R1 is interposed between the bearings B3, B4 and the support shaft Cs1 as a support member, and a gap S4 is formed on the outer peripheral side of the ring-shaped member R1. Yes. The ring-shaped member R1 is incorporated in such a manner that the movement in the axial direction is restricted but the minute movement in the radial direction is allowed. With such a configuration, coupled with the design of the ring-shaped member R1, the degree of freedom in design related to gap formation can be greatly expanded.

  In addition, since the plurality of gaps S4 and S5 can be formed in the radial direction across the ring-shaped member R1, the damper function of the lubricant is enhanced, and the impact absorbing function itself can be further enhanced. From this viewpoint, the number of ring-shaped members R1 is not limited to one, and a plurality of rings may be arranged in the radial direction.

  Although not shown in the figure, in the same manner as in the above-described embodiment of FIG. 3, the bearings B1 and B2 are supported between the inner rings B1a and B2a and the shaft Sa1 or between the bearings B1 and B2 and the outer rings B1b and B2b. A ring-shaped member may be arranged between or both of the members Ca1 and the same additional effect can be obtained.

  If necessary, the ring-shaped member may be disposed between the gear and the bearing, between the bearing and the support member, or may be disposed only one or a plurality of them, Moreover, it does not need to arrange | position. When a ring-shaped member is arranged, the gap may be provided only on the outer peripheral side of the ring-shaped member (in a normal state) or only on the inner peripheral side, and further on the outer peripheral side and the inner peripheral side. You may provide in both.

  In the present invention, there is no particular limitation on how much the gap is specifically formed with respect to which axis of the locked train mechanism. In short, as a result, at least two of the gears, the bearings, and the support members incorporated in the shaft at any part other than the part that rotates relative to the bearing of the predetermined shaft of the locked train mechanism. May be formed so as to be relatively displaceable in the radial direction. Areas where wind power generation facilities are installed, because the frequency range that can absorb fluctuations varies depending on the axis on which the gap is formed, the number of axes to be formed, the formation position and size on the axis to be formed, etc. Considering the nature of the wind that blows, it is possible to perform more effective fluctuation absorption. As described above, the present invention can be applied not only to each intermediate rotation shaft but also to the input shaft and the output shaft. The configuration of the locked train mechanism itself is not limited to the above configuration (the locked train mechanism is an example).

  Further, in the above embodiment, an example in which a lubrication passage is formed in order to ensure the lubricant in the gap at all times has been shown. However, with regard to “securing the lubricant in the gap”, for example, the gap It is also possible to configure such that (or a minute space including a gap) is isolated and sealed from the space inside the gearbox, and the lubricant is positively sealed in this sealed space. In addition, when adopting a configuration in which the gap is isolated and sealed from the space inside the gear box, the lubricant filled in the gap is made different from the lubricant in the space inside the gear box. Further, it may be a liquid that can function well as a damper, not a so-called lubricant. The configuration for sealing the gap is excellent in that a liquid such as a predetermined lubricant can be reliably held in the gap.

  Furthermore, the formation of the lubrication passage and the sealing configuration may be combined so that the gap or the minute space including the gap is sealed at a portion other than the opening of the lubrication passage to the gap. As this structure has a qualitative tendency, the faster the rotation of the support shaft and the gear as the support member, the higher the pressure of the lubricant in the gap (since the centrifugal force becomes larger). It is possible to generate a stronger repulsive force when the squeeze is narrowed and to obtain a damper effect more reliably.

  Moreover, in the said embodiment, although the ball bearing was employ | adopted as all the bearings, in the present invention, the kind of bearing is not necessarily limited to a ball bearing. Depending on the power generation capacity or the configuration of the locked train mechanism, for example, a roller bearing or a needle bearing may be employed. For example, when the gear is a helical gear, it may be an angular ball bearing or a tapered roller bearing capable of receiving an axial load.

  Furthermore, 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. Therefore, there is a separate gap according to the present invention in addition to the portion where 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 category of 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 20 ... Speed up gear 21 ... Locked train mechanism 31-38 ... 1st intermediate rotating shaft 61-64 ... 2nd intermediate rotating shaft 91 ˜94: Third intermediate rotating shaft 121, 122: Fourth intermediate rotating shaft G1, G2: Gears B1, B2: Bearing Ca1, Ca2: Casing S1, S2: Clearance

Claims (5)

In the gearbox for wind power generation with the locked train mechanism,
A gear constituting one element of the locked train mechanism;
A shaft integrated with the gear;
A support member that rotatably supports the shaft via a bearing,
A gap is formed between at least one of the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member,
Provided with a lubrication passage that opens into the gap and supplies a lubricant to the gap ;
A plurality of ring-shaped members are interposed between at least one of the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member,
At least one of the inner periphery side and the outer periphery side of the ring-shaped member, the speed increaser for a wind power generation provided with a locked train mechanism, wherein the gap that has been formed. In the gearbox for wind power generation with the locked train mechanism,
A gear constituting one element of the locked train mechanism;
A shaft integrated with the gear;
A support member that rotatably supports the shaft via a bearing,
A gap is formed between at least one of the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member,
Liquid is sealed in the gap or a minute space including the gap, and the minute space including the gap or the gap is isolated and sealed from the space in the speed increaser ,
A plurality of ring-shaped members are interposed between at least one of the inner ring of the bearing and the shaft and between the outer ring of the bearing and the support member,
A speed increasing device for wind power generation provided with a locked train mechanism , 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 the gearbox for wind power generation with the locked train mechanism,
A gear constituting one element of the locked train mechanism;
A shaft that rotatably supports the gear via a bearing,
A gap is formed between at least one of the gear and the outer ring of the bearing and between the shaft and the inner ring of the bearing,
Liquid is sealed in the gap or a minute space including the gap, and the minute space including the gap or the gap is isolated and sealed from the space in the speed increaser ,
A plurality of ring-shaped members are interposed between at least one of the gear and the outer ring of the bearing and between the shaft and the inner ring of the bearing,
A speed increasing device for wind power generation provided with a locked train mechanism , 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 2 or 3 ,
A speed increasing device for wind power generation having a locked train mechanism, wherein the gap or a minute space including the clearance is filled with a liquid different from the lubricant sealed in the space inside the speed increasing device. . In any of the claims 2-4,
Comprising a lubricating passage that opens into the gap and supplies a lubricant to the gap;
A speed increasing device for wind power generation provided with a locked train mechanism, wherein the gap or a minute space including the gap is sealed at a portion other than the opening of the lubrication passage.

Images