Planetary transmission and wind turbine generator

Abstract

To provide a planetary transmission device and a wind power generation device capable of suppressing occurrence of damage by enhancing rigidity of a support structure of a planetary gear without complicating a manufacturing process.SOLUTION: The planetary gear transmission includes an annular ring gear 61 having teeth formed on an inner peripheral surface, a sun gear 65 disposed on a central axis of the ring gear 61 and having teeth 63 formed on an outer peripheral surface, a plurality of planetary gears 51 disposed between the ring gear 61 and the sun gear 65 and meshing with each other's teeth 63,67, and a single carrier 53 rotatably supporting the plurality of planetary gears 51. The rotational speed of the second rotating shaft 43 connected to the carrier 53 with respect to the first rotating shaft 41 connected to the sun gear 65 is changed. The plurality of planetary gears 51 are rotatably supported by a support shaft 55 fixed to the carrier 53 via a bearing.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present invention relates to a planetary transmission and a wind turbine generator. [Background technology]

[0002] There are known speed-increasing devices used in wind turbine generators that generate electricity using wind power, which increase the rotation speed of the windmill and transmit the increased rotation speed to the generator (see, for example, Patent Documents 1 and 2). Patent Document 1 describes a planetary gear transmission unit, as shown in FIG. 12, which includes a ring gear 81, a sun gear 82 arranged on the central axis of the ring gear 81, multiple planetary bearings 84 having planetary gears 83 arranged between the ring gear 81 and the sun gear 82, and a planetary carrier 85 to which the multiple planetary bearings 84 are rotatably attached. The multiple planetary bearings 84 are supported on the planetary carrier 85 by flexpin shafts 86. This planetary gear transmission unit has been improved to suppress tilting of the low-rigidity flexpin shaft 86 when a tilting moment M is applied to the planetary gears 83.

[0003] Patent Document 2 describes a planetary gear transmission unit in which inner rings 93a, 93b of a needle bearing 92 arranged on the inner diameter side of a planetary gear 91 have a double structure, and the interface between the inner rings 93a, 93b is configured with a spherical seat 94 made of a spherical surface, as shown in Fig. 13. With this planetary gear transmission unit, even if a large load and torque act on a sun shaft 95 (planet pin), the spherical seat 94 absorbs uneven contact in the tooth width direction. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2010-270911 [Patent Document 2] Japanese Patent Application Laid-Open No. 2009-144532 Summary of the Invention [Problem to be solved by the invention]

[0005] However, with the configuration of Patent Document 1, even if tilting of flexpin shaft 86 is suppressed, deformation cannot be completely suppressed, resulting in a structure that is prone to misalignment between gears. This causes uneven contact between the tooth surfaces of each gear, which can easily cause damage due to excessive surface pressure. Furthermore, the configuration of Patent Document 2 has problems in that it is difficult to machine the spherical seat, and the sliding between the interfaces of spherical seat 94 can easily cause damage due to wear and other factors.

[0006] SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a planetary transmission and a wind turbine generator that can increase the rigidity of the support structure for the planetary gears and suppress the occurrence of damage without complicating the manufacturing process. [Means for solving the problem]

[0007] The present invention comprises the following configurations. (1) A planetary transmission comprising: an annular ring gear with teeth formed on its inner peripheral surface; a sun gear arranged on the central axis of the ring gear with teeth formed on its outer peripheral surface; a plurality of planet gears arranged between the ring gear and the sun gear and meshing with each other's teeth; and a single carrier supporting the plurality of planet gears rotatably, the planetary transmission changing the rotational speed of a second rotating shaft connected to the carrier relative to a first rotating shaft connected to the sun gear, The plurality of planetary gears are rotatably supported via bearings on a support shaft fixed to the carrier. Planetary transmission. (2) A wind power generation device having a blade portion that rotates when exposed to wind, a speed increaser that increases the rotation speed of the blade portion, and a generator that converts rotational energy generated by the increased rotation speed into electrical energy, The speed increaser is the planetary transmission described in (1), and the rotation of the blade portion is transmitted to the second rotating shaft, and the rotation of the first rotating shaft is transmitted to the generator. Wind power generation equipment. [Effects of the Invention]

[0008] According to the present invention, the rigidity of the support structure for the planetary gear can be increased and the occurrence of damage can be suppressed without complicating the manufacturing process. [Brief explanation of the drawings]

[0009] [Figure 1] FIG. 1 is a schematic diagram of a wind turbine generator. [Figure 2] FIG. 2 is a schematic cross-sectional view of a radial type generator. [Figure 3] FIG. 3 is a schematic cross-sectional view of an axial type generator shown for reference. [Figure 4] FIG. 4 is a schematic diagram showing the configuration of the speed-increasing gearbox, with a partial cross section. [Figure 5] FIG. 5 is an exploded perspective view of the main components of the gearbox. [Figure 6] FIG. 6 is a perspective view of the carrier unit. [Figure 7] FIG. 7 is a perspective view of the appearance of the planetary gears and needle bearings. [Figure 8] 8 is a cross-sectional view taken along line VIII-VIII in FIG. 7, showing a state in which a support shaft is inserted into the planetary gear via a needle bearing. [Figure 9] FIG. 9 is a perspective view of a ring gear. [Figure 10] FIG. 10 is a cross-sectional view taken along line X-X in FIG. 4, illustrating a schematic diagram of the meshing between the ring gear and the planetary gears, and the meshing between the sun gear connected to the first rotation shaft and the planetary gears. [Figure 11] FIG. 11 is a schematic cross-sectional view of the sun shaft side needle bearing taken along line XI-XI shown in FIG. [Figure 12] FIG. 12 is a schematic diagram of a conventional planetary gear transmission unit. [Figure 13] FIG. 13 is a schematic cross-sectional view of a planet bearing portion of a conventional planetary speed-increasing gearbox. DETAILED DESCRIPTION OF THE INVENTION

[0010] Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings. Here, an example in which a planetary transmission according to the present invention is applied to a gearbox used in a wind turbine generator will be described, but the application examples of planetary transmissions are not limited to this.

[0011] 1 is a schematic diagram of a wind turbine generator 100. The wind turbine generator 100 includes a blade section 11, a gearbox 13, and a generator 15. The blade section 11 is a vertical axis wind turbine having a rotating shaft 17 that is erected in the vertical direction and a plurality of blades 19 attached to the rotating shaft 17. Note that the wind turbine generator 100 is not limited to the vertical axis wind turbine described above, and may also be a horizontal axis wind turbine in which the rotating shaft 17 is arranged horizontally.

[0012] In this wind turbine generator 100, the vanes 19 of the blade section 11 catch the wind and rotate the rotating shaft 17 in one direction, and this rotation of the rotating shaft 17 is transmitted to the gearbox 13. The gearbox 13 increases the rotation of the rotating shaft 17 and transmits it to the generator 15. The generator 15 generates electricity by converting the rotational energy of the increased rotation into electrical energy. The blade section 11 shown here is a Darrieus-type lift wind turbine, and multiple vanes 19 (three in this example) are arranged at equal intervals around the rotating shaft 17. Both ends of each vane 19 are connected to the rotating shaft 17, and the center has a curved shape that bulges outward in the radial direction.

[0013] The speed increaser 13 is provided between the blade portion 11 and the generator 15, and includes a planetary transmission in which a plurality of planetary gears revolve around a sun gear while rotating on their own axes, as will be described in detail later.

[0014] 1 illustrates a basic configuration, and other functional components may be provided. For example, a clutch may be provided between the blade section 11 and the gearbox 13, making it possible to cut off the transmission of rotation of the blade section 11 to the gearbox 13. In this case, cutting off the power transmission of the clutch can reduce resistance to the initial rotational movement of the blade section 11 and also prevent excessive rotation from being transmitted to the generator side.

[0015] The generator 15 is a radial type generator. Generally, generators are classified into radial type and axial type. FIG. 2 is a schematic cross-sectional view of a radial-type generator 15. The radial-type generator 15 has a shaft body 21, a rotor 23, and a stator 25 supported by a fixed portion (not shown). The rotor 23 has a plurality of permanent magnets. Each permanent magnet is fixed around the shaft body 21 so that the polarity of its magnetic poles alternates in the circumferential direction. The stator 25 is provided with a coil 27 and is formed in a cylindrical shape so as to cover the outer periphery of the rotor 23. This radial-type generator generates electricity by rotating the shaft body 21, causing the coil 27 of the stator 25 to receive the rotating magnetic field of the rotor 23 and generate electromotive force. This radial-type generator 15 can generate electricity efficiently at high speeds.

[0016] FIG. 3 is a schematic cross-sectional view of an axial-type generator shown for reference. The axial-type generator includes a shaft body 31, multiple (e.g., two) rotor plates 33, and a stator 35. The rotor plates 33 are fixed to the shaft body 31 at intervals and rotate together with the shaft body 31. A stator 35, supported by a fixed portion (not shown), is disposed between the rotor plates 33. Permanent magnets 37 are provided on the surface of the rotor plate 33 facing the stator 35. The permanent magnets 37 are disposed opposite the stator 35 and are arranged with their magnetic poles alternately reversed along the circumferential direction. A plurality of coils 39 are arranged in a ring shape on the stator 35. This axial-type generator generates electricity when the shaft body 31 rotates, causing the coils 39 to receive a rotating magnetic field generated by the rotor plates 33 and generate electromotive force. This axial-type generator is used as a generator when the rotation speed is relatively low. However, axial type generators tend to be expensive because of their large diameter and mass.

[0017] Wind power generators with Darrieus-type lift-type wind turbines have traditionally mainly used axial-type generators because the rotation speed of the turbine is relatively slow. However, in the wind power generator 100 with this configuration, the speed-up gear 13 can increase the rotation of the blades 11 and transmit the rotation to the generator 15, making it possible to use a radial-type generator 15 that can generate electricity efficiently at high speeds.

[0018] Next, the structure of the speed increaser 13, which is a planetary transmission, will be described in detail. Fig. 4 is a schematic diagram showing the configuration of the speed increaser 13, partially in cross section. Fig. 5 is an exploded perspective view of the main components of the speed increaser 13. The speed increaser 13 includes a first rotating shaft 41 serving as an output shaft, a second rotating shaft 43 serving as an input shaft, a planetary gear mechanism 45 (Fig. 4) that transmits rotation of the first rotating shaft 41 to the second rotating shaft 43, a first housing 47, and a second housing 49.

[0019] The planetary gear mechanism 45 generally includes an annular ring gear 61 with teeth 63 formed on its inner peripheral surface, a sun gear 65 disposed on the central axis (axis L2) of the ring gear 61 with teeth 67 formed on its outer peripheral surface, a plurality of planetary gears 51 disposed between the ring gear 61 and the sun gear 65 and meshing with each other's teeth 63, 67, and a single carrier 53 that rotatably supports the plurality of planetary gears 51. The term "single" here means that the plurality of planetary gears 51 revolve together around the axis L1. The axis L1 is the central axis of the second rotating shaft 43, and the axis L2 is the central axis of the first rotating shaft, with the axes L1 and L2 being coaxial.

[0020] The first rotating shaft 41 is rotatably supported in the first housing 47 via a rolling bearing BL1 and is prevented from coming off by a retaining ring SR. A seal SL1 is provided on the inside (left side in FIG. 4) of the rolling bearing BL1 in the axial direction (direction of axis L1). The second rotating shaft 43 and a carrier 53, which will be described in detail later, are supported in the second housing 49 via a rolling bearing BL2, and are supported in the first housing 47 via a rolling bearing BL3. A seal SL2 is provided on the outside (left side in FIG. 4) of the rolling bearing BL2 in the axial direction (direction of axis L2). The seals SL1 and SL2 are sealing members made of rubber or the like that prevent dust from entering the first housing 47 and the second housing 49.

[0021] Next, the configuration of the planetary gear mechanism 45 will be described in the order in which rotation is transmitted from the input shaft to the output shaft when it functions as a speed increaser. The second rotating shaft 43, which is the input shaft, is integrated with a carrier 53 that supports multiple planetary gears 51 to form the carrier unit 40.

[0022] FIG. 6 is an external perspective view of the carrier unit 40. A carrier 53, which is generally cylindrical and has a larger diameter than the second rotating shaft 43, is connected to the base end side (lower side in FIG. 6) of the second rotating shaft 43 of the carrier unit 40, coaxially with the axis L2 of the second rotating shaft 43. Three planetary gears 51 are rotatably supported on the carrier 53 at equal intervals in the circumferential direction, centered on the axis L2 of the second rotating shaft 43. The planetary gears 51 are supported at a longitudinally intermediate portion of the support shaft 55 via bearings, preferably via needle bearings 57, and part of their outer peripheries protrude radially outward from openings 53a formed in the carrier 53. In other words, the needle bearings 57 are provided between the inner diameter surface 51a of the planetary gears 51, into which the support shaft 55 is inserted, and the outer diameter surface of the support shaft 55, and the planetary gears 51 are rotatably supported on the support shaft 55 by the needle bearings 57.

[0023] Fig. 7 is an external perspective view of the planetary gear 51 and the needle bearing 57. Fig. 8 is a cross-sectional view taken along line VIII-VIII in Fig. 7, showing the state in which the support shaft 55 is inserted into the planetary gear 51 via the needle bearing 57. As shown in Figs. 7 and 8, the needle bearing 57 includes a plurality of needles 57a and a cage (not shown) that rotatably holds each needle 57a. This needle bearing 57 does not have an inner ring or an outer ring, and the inner diameter surface 51a of the planetary gear 51 and the outer diameter surface of the support shaft 55 form the raceway surfaces.

[0024] 4, a pair of support holes 53b, 53c are formed coaxially in parallel to the axis L2 in the carrier 53. These pairs of support holes 53b, 53c are formed at multiple locations in the carrier 53 according to the number of planetary gears 51 (three in this example). One end of a support shaft 55 is supported in the support hole 53b of the carrier 53, and the other end is supported in the support hole 53c, so that each planetary gear 51 is rotatably supported with both ends of the support shaft 55 supported by the support holes 53b, 53c of the carrier 53.

[0025] 9 is a perspective view of the ring gear 61. The ring gear 61 is disposed radially outward of the carrier 53 shown in FIG. 4 and is sandwiched between the first housing 47 and the second housing 49 in the axial direction. Teeth 63 formed on the inner diameter side of the ring gear 61 mesh with the three planetary gears 51.

[0026] 10 is a cross-sectional view taken along line X-X in FIG. 4, illustrating a schematic diagram of the meshing between the ring gear 61 and the planetary gears 51, and the meshing between the sun gear 65 connected to the first rotating shaft 41 and the planetary gears 51. When the second rotating shaft 43 shown in FIG. 4 rotates together with the carrier 53, each planetary gear 51 rotates in the Rc direction (clockwise revolution in FIG. 10), for example. In this case, each planetary gear 51 rotates in the Rp direction (counterclockwise rotation on its axis in FIG. 10) due to meshing with the teeth 63 of the ring gear 61.

[0027] A sun gear 65 is disposed on the central axis of the ring gear 61. The sun gear 65 is fitted coaxially with the axis L1 into a recess 41a formed on the base end side (left side in FIG. 4) of the first rotating shaft 41 shown in FIG. 4. The sun gear 65 has a large-diameter portion 65a that is the connecting end with the first rotating shaft 41, a small-diameter portion 65b on the axially opposite side of the large-diameter portion 65a, and an intermediate portion 65c whose outer diameter smoothly changes between the large-diameter portion 65a and the small-diameter portion 65b. Teeth 67 that mesh with the planetary gears 51 are formed on at least the portion of the sun gear 65 that faces the planetary gears 51. An inner hole 53d is formed in the carrier 53 along the axis L2, and the small-diameter portion 65b is supported in this inner hole 53d via a sun-shaft-side needle bearing 69 with inner and outer rings. In other words, the other end of the sun gear 65 opposite to the one end connected to the first rotating shaft 41 is inserted into an inner hole 53d formed along the axis L2, which is the central axis of the carrier 53, and is rotatably supported between the inner hole 53d and the carrier 53 via a sun shaft side needle bearing 69.

[0028] Fig. 11 is a schematic cross-sectional view of the sun shaft side needle bearing 69 taken along line XI-XI shown in Fig. 4. As shown in Figs. 4 and 11, the inner ring 71 of the sun shaft side needle bearing 69 is fixed to the small diameter portion 65b, and the outer ring 73 is fixed to the inner diameter surface of the inner hole 53d of the carrier 53. A plurality of needles 75 are arranged between the inner ring 71 and the outer ring 73. In this way, the carrier 53 rotatably supports the sun gear 65 coaxially with the second rotating shaft 43, thereby making the speed increaser 13 compact in configuration.

[0029] Next, the operation of the speed increaser 13 having the above-described configuration will be described. When the second rotating shaft 43, which is the input shaft shown in FIG. 4, is rotated, the carrier 53 rotates, and the three planetary gears 51 supported by the carrier 53 mesh with the ring gear 61 and revolve integrally with the carrier 53 while rotating about their own axes. When the planetary gears 51 revolve while rotating, they rotate and drive the sun gear 65, which is rotatably supported by the carrier 53. The rotation of this sun gear 65 is accelerated from the rotational speed of the second rotating shaft 43 in accordance with the speed transmission ratio of the planetary gear mechanism 45. The first rotating shaft 41 is rotated and driven at this accelerated rotational speed. When the first rotating shaft 41 is used as the input shaft, the second rotating shaft 43 becomes the output shaft and functions as a reducer that decelerates the rotation of the input shaft.

[0030] In the planetary gear mechanism 45 of this configuration, the planetary gear 51 shown in Fig. 4 is supported at both ends of the carrier 53 by the support shaft 55. Therefore, even if a large load or moment acts on the second rotating shaft 43, the bending rigidity of the support shaft 55 is increased compared to when the support shaft 55 is supported at one end, and deformation of the support shaft 55 is suppressed. For example, if the root diameter of the planetary gear 51 is 14.25 mm, the diameter of the support shaft 55 is preferably 3 mm or more and 5 mm or less. Within this range, sufficient bending rigidity is obtained, and deformation of the support shaft 55 due to external forces is suppressed.

[0031] Furthermore, the needle bearing 57 disposed in the gap between the planetary gear 51 and the support shaft 55 is a bearing that does not have an inner ring or an outer ring. This eliminates the fitted portion that is a likely source of creep. This results in high rigidity, improved load resistance, and a longer lifespan. Furthermore, by not having an inner ring or an outer ring, the needle diameter φdn of the needle bearing 57 shown in FIG. 8 can be expanded to a size equal to the gap δ between the planetary gear 51 and the support shaft 55. The inner diameter φds of the inner diameter surface 51a of the planetary gear 51 is, for example, 8 mm, and is set according to the sizes of the needle bearing 57 and the planetary gear 51.

[0032] It is preferable that the ratio h / d of the rim thickness h from the tooth bottom 51b of the planetary gear 51 to the raceway surface of the needle bearing 57 to the tooth bottom circle diameter φd of the planetary gear 51 is set so as to satisfy equation (1). 0.086≦h / d≦0.25 (Formula 1)

[0033] By adopting a planetary gear 51 with a ratio h / d close to 0.086 and a relatively thin rim thickness h, the outer diameter of the support shaft 55 can be increased. This allows a relatively large torque load to be applied compared to the size (capacity) of a typical planetary gear mechanism 45 itself, enabling the device to be made more compact. It also allows for greater torque transmission even with the same device size. Furthermore, by increasing the diameter of the support shaft 55 and the needle diameter φdn of the needle bearing 57 as described above, the rigidity of the support structure for the planetary gear 51 can be increased. This reduces misalignment between gears, making it less likely that uneven contact will occur between the teeth of the planetary gear 51, etc.

[0034] On the other hand, by using planetary gears 51 with a ratio h / d close to 0.25 and a relatively thick rim thickness h, the needle diameter of the needle bearings 57 becomes relatively small. In this case, it is possible to realize a planetary gear mechanism 45 that can start rotating even with low torque. In this way, an h / d ratio of 0.25 reduces the rotational resistance of the planetary gears 51, resulting in the effect of enabling smoother rotation.

[0035] The ratio h / d is 0.086 or more and 0.25 or less, so that the above-mentioned effects can be realized in a balanced manner. Furthermore, the above-mentioned planetary gear mechanism 45 does not have any parts that complicate the processing steps, such as a spherical seat, so that the manufacturing cost can be reduced.

[0036] Next, power generation by the wind turbine generator 100 equipped with the speed-increasing gear (planetary transmission) 13 having the planetary gear mechanism 45 described above will be described. When the wind blows, the vanes 19 catch the wind, generating a rotational force in the blade section 11. This rotation of the blade section 11 is transmitted to the speed-up gear 13. The speed-up gear 13 increases the rotation transmitted from the blade section 11 using the planetary gear mechanism 45 described above, and transmits the rotation to the generator 15. In this configuration, by providing the speed-up gear 13 between the blade section 11 and the generator 15, a high-speed rotating radial type generator 15 using radially opposed magnets can be used. This allows the diameter of the generator 15 to be reduced, resulting in a more compact design and reduced costs for manufacturing, maintenance, installation, etc. Furthermore, high-speed rotation improves power generation efficiency.

[0037] Furthermore, the planetary gear mechanism 45 of this configuration improves the bending rigidity of the support shaft 55 that supports the planetary gears 51. Therefore, even if a large load acts on the second rotating shaft 43, etc., it is possible to prevent one-sided contact between the gears and prevent damage to the components. As a result, it is expected that each component will achieve its original design life. Furthermore, even in situations where the rotating shaft 17 rotates at a low speed in a light breeze, if the planetary gears 51 are supported by needle bearings 57 with a small needle diameter, they can rotate with low torque. This enables reliable power generation even at low speeds. Moreover, since the blade section 11 is a Darrieus-type lift-type wind turbine that rotates over a wide range of wind speeds, it is possible to generate power with high efficiency.

[0038] In the above embodiment, a Darrieus-type lift wind turbine is provided as the blade section 11, but the blade section 11 may also be a straight blade lift wind turbine in which multiple straight blades are supported in parallel at intervals on the rotation axis 17.

[0039] As such, the present invention is not limited to the above-described embodiments, and the present invention also contemplates the mutual combination of the various components of the embodiments, as well as modifications and applications by those skilled in the art based on the description in the specification and well-known techniques, and these modifications and applications are included in the scope of protection sought.

[0040] As described above, the present specification discloses the following: (1) A planetary transmission comprising: an annular ring gear with teeth formed on its inner peripheral surface; a sun gear arranged on the central axis of the ring gear with teeth formed on its outer peripheral surface; a plurality of planet gears arranged between the ring gear and the sun gear and meshing with each other's teeth; and a single carrier supporting the plurality of planet gears rotatably, the planetary transmission changing the rotational speed of a second rotating shaft connected to the carrier relative to a first rotating shaft connected to the sun gear, The plurality of planetary gears are rotatably supported via bearings on a support shaft fixed to the carrier. Planetary transmission. In this planetary transmission, multiple planetary gears rotate around a support shaft while meshing with a ring gear and revolving around it, and the planetary gears mesh with a sun gear to rotate the sun gear, and the speed of rotation of a first rotating shaft connected to the sun gear and a second rotating shaft connected to the carrier is changed by a planetary gear mechanism.

[0041] (2) The planetary transmission according to (1), wherein the bearing is a needle bearing that does not have an inner ring or an outer ring. In this planetary transmission, each planet gear is rotatably supported by the carrier via a needle bearing that does not have an inner or outer ring. This allows the needle diameter of the needle bearing to be expanded to a size equal to the gap between the planet gear and the support shaft. Furthermore, by not having an inner or outer ring, the fitted parts that are prone to causing creep can be eliminated. This results in high rigidity, improved load resistance, and a longer life.

[0042] (3) The planetary transmission according to (1), wherein the support shaft is supported at both ends by the carrier. With this planetary transmission, compared to when the support shaft is cantilevered by the carrier, the rigidity of the support shaft against bending can be improved even when a large load or moment acts on the second rotating shaft.

[0043] (4) The planetary transmission according to any one of (1) to (3), wherein the second rotation shaft is arranged coaxially with the central axis on which the sun gear is arranged. According to this planetary transmission, the sun gear is arranged coaxially with the second rotation shaft, allowing the entire device to have a compact configuration.

[0044] (5) A planetary transmission device according to any one of (1) to (4), wherein the other end of the sun gear opposite to the one end connected to the first rotating shaft is inserted into an inner hole formed along the central axis of the carrier and is rotatably supported between the inner hole and the sun gear via a rolling bearing. According to this planetary transmission, the first rotating shaft on the sun gear side and the second rotating shaft on the carrier side can be arranged rotatably and coaxially.

[0045] (6) The planetary transmission according to any one of (1) to (5), wherein the diameter of the support shaft is 3 mm or more and 5 mm or less. According to this planetary transmission, the support shaft has sufficient bending rigidity, and deformation of the support shaft due to external forces is suppressed.

[0046] (7) A wind power generation device having a blade portion that rotates when exposed to wind, a speed increaser that increases the rotation speed of the blade portion, and a generator that converts rotational energy generated by the increased rotation speed into electrical energy, The speed increaser is a planetary transmission according to any one of (1) to (6), wherein the rotation of the blade portion is transmitted to the second rotating shaft, and the rotation of the first rotating shaft is transmitted to the generator. Wind power generation equipment. This wind turbine generator uses a step-up gear between the blades and the generator, allowing for the use of a high-speed radial-type generator with radially opposed magnets. This allows for a smaller generator diameter, resulting in a more compact design and reduced manufacturing, maintenance, and installation costs. High-speed rotation also improves power generation efficiency. Furthermore, the bending rigidity of the support shafts that support the planetary gears has been improved, preventing one-sided contact between the gears even if a large load acts on the second rotating shaft, etc., and ensuring that each component lasts for the full duration of its designed life. [Explanation of symbols]

[0047] 11 Blade section 13 Gearbox (planetary transmission) 15. Generator 17 Rotation axis 19 Feather 21 Shaft 23 Rotor 25 Stator 27 Coil 31 Axial body 33 rotor plate 35 Stator 37 Permanent Magnets 39 Coil 40 Carrier Unit 41 First rotation axis 41a Recess 43 Second rotation axis 45 Planetary gear mechanism 47 First Housing 49 Second Housing 51 Planetary gear 51a Inner surface 53 Career 53a opening 53b, 53c support hole 53d inner hole 55 Support shaft 57 Needle bearings 57a Needle 61 Ring Gear 63 teeth 65 Sun Gear 67 teeth 69 Sun shaft side needle bearing 71 Inner circle 73 Outer Ring 75 Needle 100 Wind power generation equipment

Claims

1. A planetary transmission comprising: an annular ring gear having teeth formed on its inner peripheral surface; a sun gear disposed on a central axis of the ring gear and having teeth formed on its outer peripheral surface; a plurality of planet gears disposed between the ring gear and the sun gear and meshing with each other's teeth; and a single carrier rotatably supporting the plurality of planet gears, the planetary transmission changing the rotational speed of a second rotating shaft connected to the carrier relative to a first rotating shaft connected to the sun gear, The plurality of planetary gears are rotatably supported via bearings on a support shaft fixed to the carrier. Planetary transmission.

2. The bearing is a needle bearing having no inner ring or outer ring.

2. The planetary transmission of claim 1.

3. The support shaft is supported at both ends by the carrier.

2. The planetary transmission of claim 1.

4. the second rotation shaft is arranged coaxially with the central axis on which the sun gear is arranged.

2. The planetary transmission of claim 1.

5. the other end of the sun gear opposite to the one end connected to the first rotation shaft is inserted into an inner hole formed along the central axis of the carrier, and is rotatably supported between the carrier and the inner hole via a rolling bearing.

2. The planetary transmission of claim 1.

6. The diameter of the support shaft is 3 mm or more and 5 mm or less.

2. The planetary transmission of claim 1.

7. A wind power generation device having a blade portion that rotates when exposed to wind, a speed increaser that increases the rotation speed of the blade portion, and a generator that converts rotational energy generated by the increased rotation speed into electrical energy, The speed-increasing gear is a planetary transmission according to any one of claims 1 to 6, wherein the rotation of the blade portion is transmitted to the second rotating shaft, and the rotation of the first rotating shaft is transmitted to the generator. Wind power generation equipment.

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