KR101375847B1 - Planetary gears unit for a wind power generator - Google Patents

Abstract

The present invention relates to a planetary gear device for a wind turbine, wherein a plurality of shear planetary gears (103) inside the ring gear (102) coupled to the input shaft (101) as a main shaft on which the propeller of the wind turbine is mounted rotates with the ring gear. And the rear planetary gears 105 are externally engaged with the sun gear 107, the sun gear 107 is integrally connected to the output shaft 109, the output shaft 109 is a rotor of the generator In the planetary gear unit for a wind power generator which is integrally connected to the shaft and transmitted to the rotor shaft of the generator through the rotational force of the wind, the increase in accordance with the assembly error of the shear planetary gear 103 and the ring gear 102 Each of the planetary gears 103 has a relatively hard planetary gear shaft 106 equipped with rear planetary gears 105 through a flexible flexible shaft 104 to absorb and reduce the engagement loads to the elastic deformation. By being integrally connected, the increase in the mating load due to the assembly error is absorbed by the elastic deformation of the flexible shaft portion, thereby improving the load distribution between the planetary gears, reducing the design load, and reducing the design load. By reducing the weight and volume of the wind turbine generator, there is an effect to increase the weight and maintainability.

Description

Planetary gears unit for a wind power generator

The present invention relates to a planetary gear device for a wind power generator, in particular a load distribution function between planetary gears provided to convert the rotational speed and torque of the main shaft in the gear box installed between the main shaft and the generator is installed propeller The improved planetary gear unit for a wind turbine.

Wind power generator is produced by rotating the rotor of the generator by the rotation of the propeller is fixed by the wind propeller is rotated by the wind, the gearbox is provided between the main shaft and the generator to adjust the rotational speed and torque of the main shaft for power generation Convert.

In order to prepare for the depletion of fossil energy and to prevent the destruction of the natural environment, wind power is increasing along with photovoltaic power generation as green energy, and these wind power generators are becoming larger and larger, including the main components of wind power generators. The design focuses on reducing the weight and volume of the nussel.

To this end, some wind power transmission systems use a combination of a gearbox using a planetary gear called a compound planetary stage and a permanent magnet synchronous generator with multiple poles. The gearbox using the compound planetary gear train increases the rotational speed by 15 to 30 times to match the low speed rotor rotation with electricity production.

Unlike the general planetary gear train, the compound planetary gear train is designed so that the planetary gear does not undergo reverse bending, and the two planetary gears are connected to the front and rear planets on one axis, and the shear planetary gear is the ring gear and the rear planetary gear. The gear consists of a sun gear and a gear bite so that the gear train in the first stage can have a speed increase ratio in the second stage.

Conventional planetary gear trains reduce load by designing flexible pins to reduce load, and reduce weight and volume of gearbox by reducing design load. Can be.

However, in the case of using a compound planetary gear train, the engagement between the planetary gear and the ring gear and the planetary gear and the sun gear are separated from each other. Improvement of load distribution effect cannot be expected.

1 shows a composite planetary gear train of a conventional planetary gear system using a rigid shaft, in which the power generated by the wind is transmitted to the gearbox through the input shaft 1 as the main shaft connected to the propeller.

A ring gear 2 is fixed to the input shaft 1, and the ring gear 2 is engaged with the shear planetary gear 3 (bited) to transmit rotational force, and the shear planetary gear 3 is a hard planetary gear shaft. (6) transmits the rotational force to the rear planetary gear (5), the rear planetary gear (5) meshes with the sun gear (7) and transmits the rotational force through the solar gear shaft (9) to the generator. Axle bearings are used for each of the shafts (21, 22) and (23, 24), and are installed at both ends of the shaft. That is, generally the axial gears are located between both bearings.

The compound planetary gears generally use three or more planetary gear assemblies 3 and 5, and the conventional compound planetary gear trains employ rigid rotation shafts 6 and 9, and thus, when the composite planetary gear trains are manufactured, the shaft assembly positions Even if the machine is slightly misaligned, the load dispersion is rapidly worsened. Therefore, the conventional planetary gear trains cannot uniformly distribute the load distribution between the planetary gears, and thus, four or more planetary gear assemblies (3, 5) are not generally used. More specifically with reference to FIGS. 2 and 3.

Figure 2 shows the load distribution due to the manufacturing and assembly position error of the planetary gear assembly employing four shear planetary gear, the left part of the figure is a ring gear (when the composite planetary gear train is produced without fabrication and assembly error) The load distribution between 2) and the shear planetary gear is shown schematically, and it can be seen that the load distribution occurs evenly when there is no manufacturing and assembly error. The right part of FIG. 2 is an example of the shear planetary gear when the planetary gear is assembled. For example, if there is a manufacturing and assembly position error inevitably generated when assembling the second (3-2) and the third (3-3) planetary gear assemblies. The load distribution of is shown schematically. From this, excessive engagement occurs between the second shear planetary gear (3-2) and the ring gear (2), resulting in a sharp increase in load, while the third shear planetary gear (3-3). In this case, it can be seen that the load decreases rapidly due to the decrease in the engagement.

3 shows the load distribution between the rear planetary gear and the sun gear due to the manufacturing and assembly position error of the planetary gear assembly. The left part of FIG. 3 schematically shows the load distribution between the rear planetary gears 5-1 to 5-4 and the sun gear 7 when the composite planetary gear train is manufactured without theoretically manufacturing and assembling errors. It can be seen that the load distribution occurs evenly if there is no manufacturing and assembly error. On the other hand, manufacturing and assembling errors are inevitably involved in the manufacture of a plurality of planetary gears. For example, if the assembly position error of the second (5-2) and the third (5-3) planetary gear assemblies occurs, Shows. As shown in the figure, it can be seen that the engagement decreases between the second shear planetary gear 5-2 and the sun gear 7 and the load is drastically reduced, and in the case of the third rear planetary gear 5-3. It can be seen that excessive load occurs and the load increases rapidly.

When the four or more planetary gear trains are adopted in the existing composite planetary gear trains from FIGS. 2 and 3, since the planetary gears are disposed to face each other, the planetary gear trains and the sun gears due to the errors inevitably generated when the planetary gears are manufactured and assembled. The nonuniformity of the load distribution in EW causes the premature damage and noise of the planetary gears and shafts. Therefore, the use of high load distribution coefficients in the design increases the weight and volume of the gearbox. Assembly error has a sensitive effect on the load distribution of the gearbox has a problem that it is difficult to produce and manage a homogeneous product.

The present invention is a composite planetary gear train so as to be absorbed by the elastic deformation in accordance with the increase in the engagement load due to the manufacturing and assembly error in the composite planetary gear train applied to the wind turbine so that the load distribution as a whole can be made to a stable and acceptable level It is an object of the present invention to provide a planetary gear unit for a wind power generator having a flexible shaft in the shaft portion connecting the planetary gears and the shaft portion connecting the planetary gears and the sun gear.

In order to achieve the above object, the planetary gear unit for a wind turbine according to the present invention is coupled to a plurality of shear planetary gears to rotate together with the ring gear inside the ring gear coupled to the input shaft as a main shaft on which the propeller of the wind turbine is mounted. The planetary gears of the rear stage are externally engaged with the sun gear, and the sun gear is integrally connected to the output shaft, and the output shaft is integrally connected to the rotor shaft of the generator and transmitted to the rotor shaft of the generator through rotational force by wind. In the planetary gear device for a wind power generator is configured to generate power, each of the planetary gears are flexible flexible shaft portion to absorb and reduce the engagement load increased by the elastic deformation of the shear planetary gear and the ring gear Integrally connected with relatively hard planetary gear shafts equipped with rear planetary gears through It is configured to feature.

The sun gear may be integrally connected to a relatively light output shaft through a flexible flexible shaft so as to absorb and reduce the engagement load increased according to the assembly error of the rear planetary gear and the sun gear with elastic deformation.

The hard planetary gear shaft supporting the rear planetary gear is preferably supported by bearings disposed at front and rear ends thereof.

According to the present invention, by connecting the shear planetary gear to the flexible shaft portion of the rear planetary gear in a flexible planetary gear train in the composite planetary gear train, the increase in the engagement load according to the assembly error is absorbed by the elastic deformation of the flexible shaft portion The load distribution between planetary gears can be improved, the design load can be reduced, and the weight and volume of the gearbox can be reduced by reducing the design load, thereby improving the weight and maintenance of the wind turbine.

1 is a schematic cross-sectional view showing the configuration of a conventional planetary gear device for a wind turbine.
FIG. 2 is a view schematically illustrating a theoretical state and a load distribution state due to an error when fabricating and assembling a planetary gear assembly employing four shear planetary gears in the planetary gear device of FIG. 1; FIG.
3 is a view schematically showing the load distribution between the rear planetary gear and the sun gear due to the manufacturing and assembly position error of the planetary gear assembly;
Figure 4 is a schematic configuration diagram of a planetary gear device having a flexible shaft portion in accordance with the present invention.
5 is a view schematically showing an improvement in load distribution by a flexible shaft connected to a shear planetary gear in the planetary gear apparatus of FIG.
6 is a view schematically showing an improvement in load distribution by a flexible shaft connected to a sun gear having a flexible shaft according to the present invention.
Figure 7 is an enlarged view showing the load distribution effect between the planetary gear and the sun gear shown by the dotted line in FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will now be described more fully hereinafter with reference to the accompanying drawings, in which embodiments of the invention are shown.

4 and 5, four planetary gears 103 are engaged to rotate together with the ring gears to face each other inside the ring gear 102 coupled to the input shaft 101 as the main shaft on which the propeller of the wind turbine is mounted. Each of the planetary gears 103 is integrally connected to the hard planetary gear shaft 106 on which the rear planetary gears 105 are mounted through the flexible shaft unit 104, and the hard planetary gear shaft 106 is moved forward and backward. Bearings 121 and 122 are disposed and supported at the side ends, respectively. The rear planetary gears 105 are externally engaged with the sun gear 107, and the sun gear 107 is integrally connected to the output shaft 109 through the flexible shaft 108, and the output shaft 109. Is supported by two shaft bearings (123, 124) is integrally connected to the rotor shaft of the generator (not shown) so that the rotational force of the wind through the input shaft, ring gear, front and rear planetary gears and solar gear It is delivered to develop.

It should be noted that the planetary gear device used in the present specification should be understood not only to refer to planetary gears but also to a gear device in which a plurality of planetary gears and a sun gear are combined.

In the planetary gear device according to the present invention, an arrangement structure of four planetary planetary gears which are inscribed in the conventional planetary gear device and the ring gear of FIG. However, the structural difference is that each of the four oppositely arranged front planetary gears is connected by the flexible shaft part 104 to respective hard planetary gear shafts 106 supporting the rear planetary gears. There is a difference in that only the hard planetary gear shaft 106 of the rear planetary gear is supported by the bearing at both front and rear ends, and the sun gear 107 is also connected to the output shaft 109 by the flexible shaft 108. The shear planetary gears 102 are connected with respect to the hard planetary gear axis 106 and the sun gear 107 with respect to the light output shaft 109 through the flexible flexible shafts 104 and 108, which is like a cantilever beam. It may be flexible or flexible due to the load acting on the shear planetary gear and the sun gear, and accordingly, depending on the load acting on the shear planetary gear and the sun gear due to tolerances and assembly position errors in the manufacture of gears and shafts. It can be compliant and elastically deformed to accommodate such errors.

As can be seen in the left part of FIG. 5, four shear planetary gears 103-1, 103-2, 103-3, and 103-4 are internally engaged to face the ring gear 102 as shown in the theoretical design. When manufactured and ideally assembled, the same mating load is received as indicated by the arrow, but in reality, for example, the planetary gear 103-2 is shown in the right part of FIG. 2 due to manufacturing tolerances and assembly errors. When the assembly error occurs in (3-3), the increased engagement load is absorbed by the elastic deformation of the flexible flexible shaft portion 104 to which the planetary gear 102 is connected, and the planetary gear 103-2 has a dotted line. The position changes from the position to the position of the solid line, and the engagement load of the planetary gear 103-3 is reduced. Therefore, even if an assembly error occurs in the shear planetary gears, the increase in the engagement load thereby is absorbed by the elastic deformation in the flexible flexible shaft portion 104 and is transmitted from the four shear planetary gears to the shafts of the rear planetary gears as a whole. The load is improved in load distribution as indicated by arrows of the same size on the right side of FIG. 5 compared to the load distribution of the conventional gearbox of FIG. 2.

In the left part of FIG. 6, when the rear planetary gears 105-1, 105-2, 105-3, and 105-4 are ideally assembled to the outer sun gear 107, the rear planetary gears are connected to the sun gear by the rear planetary gears. The load acting is the same, but the position of the sun gear 107 indicated by the dotted line when the rear planetary gears 105-2 and 105-3 have an error in assembly position as shown in the right part of FIG. 6 and FIG. The elastic gear of the flexible shaft 108 is moved to the position indicated by the solid line by the engagement load at, and a uniform load distribution effect is obtained as indicated by the arrow compared to the conventional gearbox of FIG. 3.

The flexible flexible shaft portion of the elastic deformation is formed at the portion connecting the front planetary gears and the rear planetary gears, and the flexibility of the elastic deformation at the portion connecting the output shaft and the sun gear meshed with the rear planetary gears. By forming the flexible shaft portion, the coupling load caused by the assembly error of the rear planetary gear or the sun gear is absorbed by the elastic deformation of the flexible shaft portion, and the axial load distribution effect is obtained as a whole.

The flexibility of the flexible shaft portion, that is, the degree of elastic deformation, should be designed in consideration of the size of the planetary gear device according to the generation capacity and the magnitude of the engagement load acting on the shaft according to the error in assembling the planetary gear and the sun gear. For this elastic deformation, it is appropriately designed in such a way as to select the diameter reduction rate of the flexible shaft portion and form the hollow portion in consideration of the diameter of the flexible shaft portion, the shaft of the planetary gear, and the rotor shaft of the generator. Increasing the engagement load by the elastic deformation can be accommodated, this can be easily implemented by those skilled in the art with a simple design.

According to the present invention, the increase in the joining load due to the assembly error to the shaft portion connecting the front planetary gear and the rear planetary gear to the elastic deformation without increasing the shaft diameter due to the increase of the joining load due to the assembly error in the planetary gear device. By applying a flexible shaft portion having flexibility to absorb the overall celebration during the absorption, it can be applied, for example, to increase the size and weight of the wind power generator.

101: input shaft 102: ring gear
103: shear planetary gear 104, 108: flexible shaft portion
105: rear planetary gear 106: (planetary gear) shaft
107: sun gear 109: output shaft
121.122: (Planetary Gears) Shaft Bearings
123,124: (Sun Gear) Shaft Bearing

Claims (3)

A plurality of front planetary gears 103 are engaged to rotate with the ring gears inside the ring gear 102 coupled to the input shaft 101 as the main shaft on which the propeller of the wind turbine is mounted, and the rear planetary gears 105 are sun It is engaged externally to the gear 107, the sun gear 107 is integrally connected to the output shaft 109, the output shaft 109 is integrally connected to the rotor shaft of the generator through the rotational force by the wind generator In the planetary gear unit for a wind turbine is configured to be transmitted to the rotor shaft of the power generator,
Each of the planetary gears 103 is provided through the flexible flexible shaft 104 to absorb and reduce the engagement load increased by the assembly error of the shear planetary gear 103 and the ring gear 102 by elastic deformation. Planetary gear device for a wind turbine, characterized in that the rear planetary gear 105 is integrally connected to the relatively hard planetary gear shaft 106 is mounted. According to claim 1, The sun gear 107 is a flexible flexible shaft (A) so as to absorb and reduce the engagement load increases according to the assembly error of the rear planetary gear 105 and the sun gear 107 by elastic deformation. Planetary gear device for a wind turbine, characterized in that integrally connected to the relatively light output shaft (109) through 108. 3. The planetary gear apparatus of claim 1, wherein the hard planetary gear shafts 106 supporting the rear planetary gears are supported by bearings 121 and 122 disposed at front and rear ends thereof.

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