JP5894099B2 - Reduction gear - Google Patents

Description

  The present invention relates to a reduction gear.

  Patent Document 1 discloses a reduction gear used for a yaw drive system of a wind power generation facility.

  The reduction gear device includes an internal gear and an external gear inscribed in the internal gear. The internal gear is configured by a first pin member whose internal teeth are arranged in a pin groove formed in the casing.

  In this reduction gear, relative rotation of the external gear with respect to the internal gear is taken out from the output member. The output member is supported on the casing via a pair of bearings. Patent Document 1 discloses a structure in which the anti-load-side bearing among them is configured by a second pin member disposed in the pin groove. The outer diameter of the second pin member is set to be the same as the outer diameter of the first pin member.

JP 2010-216562 A (FIGS. 1 to 4)

  However, in the configuration disclosed in Patent Document 1, the radial load to be applied to the second pin member that supports the output member is applied to the first pin member that constitutes the internal teeth of the internal gear. There was a problem that there was a risk of end.

  The present invention has been made to solve such a problem, and the radial load to be applied to the second pin member supporting the output member is applied to the first pin member constituting the internal teeth of the internal gear. It is an object of the present invention to provide a speed reducer that can reduce the occurrence of the problem.

The present invention includes an internal gear, and an output member that is supported by a casing via a bearing and rotates with respect to the internal gear, and the internal gear has an internal gear main body and the casing. together are integrated, the internal teeth are constituted by a first pin member disposed in the pin groove formed in the casing, said bearing is a second pin member disposed in the pin groove of said casing The above-mentioned problem is solved by adopting a configuration in which the outer diameter of the second pin member is larger than the outer diameter of the first pin member.

  In this invention, the outer diameter of the 2nd pin member which supports an output member is formed larger than the outer diameter of the 1st pin member which comprises the internal tooth of an internal gear.

  That is, in the present invention, since the second pin member is incorporated with less play than the first pin member in the same pin groove, the radial load of the output member is more reliably received by the second pin member. As a result, it is possible to reduce the radial load to be applied to the second pin member on the first pin member.

  ADVANTAGE OF THE INVENTION According to this invention, the reduction gear which can reduce that the radial load which should be applied to the 2nd pin member which supports an output member is applied to the 1st pin member which comprises the internal tooth of an internal gear is provided. it can.

Sectional drawing of the principal part of the reduction gear device which concerns on an example of embodiment of this invention. II enlarged view of the reduction gear shown in FIG. Sectional drawing which follows the III-III line in the reduction gear shown in FIG. Sectional drawing which follows the IV-IV line in the reduction gear shown in FIG. The perspective view which shows typically the yaw drive system of the wind power generation equipment to which the said reduction gear device is applied Sectional drawing which shows a mode that the speed reducer of FIG. 1 is integrated in the yaw drive system of FIG. Sectional drawing of the principal part which shows an example of other embodiment of this invention

  Hereinafter, an example of an embodiment of the present invention (first embodiment) will be described in detail with reference to the drawings.

  In the present embodiment, the present invention is applied to the reduction gear G1 of the yaw drive system 14 in the wind power generation facility 10.

  With reference to FIGS. 5 and 6, the yaw drive system 14 includes an electric motor M <b> 1, a reduction gear G <b> 1 with an output pinion 24, and a turning gear 28 that meshes with the output pinion 24.

  In this example, four reduction gears G1 are arranged and fixed to the structure 12A of the nacelle 12, respectively. On the other hand, the turning gear 28 with which the output pinions 24 of the four reduction gears G1 are engaged is fixed to the cylindrical column 11 side and constitutes the inner ring of the yaw bearing 27. The outer ring 29 of the yaw bearing 27 is fixed to the structure 12 </ b> A of the nacelle 12.

  Reference numeral 30 denotes a brake device. The brake device 30 may be omitted when the electric motor M1 has a brake device (not shown), for example. Moreover, in this embodiment, although the turning gear 28 is comprised with the internal gear, it may be comprised with the external gear which the output pinion 24 circumscribes.

  With this configuration, when the output pinion 24 is rotated by the electric motor M1 via the speed reducer G1, the output pinion 24 tries to rotate the swivel gear 28. It can be swiveled around the heart 37 (FIG. 5). As a result, the nose cone 18 can be directed in a desired direction (for example, the windward direction), and the wind pressure can be efficiently received.

  FIG. 1 is a cross-sectional view of a main part of the reduction gear G1. 2 is an enlarged view of a portion II of the reduction gear G1, and FIGS. 3 and 4 are cross-sectional views taken along lines III-III and IV-IV of the reduction gear G1, respectively.

  The reduction gear G1 includes, as main components, an electric motor M1, a first reduction mechanism 41 that reduces the rotation of the electric motor M1, and a second reduction mechanism 42 that further reduces the output rotation of the first reduction mechanism 41. . The aforementioned output pinion 24 is integrally formed at the tip of the output shaft 44 of the second reduction mechanism 42.

  The first reduction mechanism 41 includes an input shaft 46 that receives the rotation of the electric motor M1 via a joint 38 (see FIG. 6), and two sets of eccentric bodies 50 that are integrated with the input shaft 46 and a key 48. There are provided two external gears 54 which are incorporated in an outer periphery of the eccentric body 50 via an eccentric body bearing 52 so as to be swingable, and an internal gear 56 which the external gear 54 is in mesh with. That is, the first reduction mechanism 41 is an eccentric oscillating planetary gear reduction mechanism called a center crank type in which the input shaft 46 constituting the eccentric body shaft is located at the axis O1 of the internal gear 56.

  The internal gear 56 is externally fitted to an internal gear main body 56A integrated with the casing 58 of the first reduction gear mechanism 41 and a support pin 56B supported by the internal gear main body 56A. It is comprised with the outer roller 56C which comprises a tooth | gear. The number of teeth of the internal gear 56 (the number of the outer rollers 56C) is slightly larger than that of the external gear 54 (in this example, “1”).

  The external gear 54 is loosely fitted with an inner pin 62 on which the sliding promotion member 60 is fitted. The inner pin 62 is press-fitted into the carrier 64. The carrier 64 is integrated with the output shaft 66 of the first reduction mechanism 41.

  The output shaft 66 of the first reduction mechanism 41 constitutes the input shaft 66 of the second reduction mechanism 42 (the output shaft 66 of the first reduction mechanism 41 = the input shaft 66 of the second reduction mechanism 42). A center gear 70 is integrated with the input shaft 66 of the second reduction mechanism 42 via a key 68. The center gear 70 meshes simultaneously with the four sorting gears 72 (see FIG. 3). Each sorting gear 72 is integrated with four eccentric body shafts 76 via spline engaging portions 74. Each eccentric body shaft 76 is integrally formed with two sets of eccentric bodies 78 that are eccentric in the same phase at the same axial position. The eccentric phase of each set of eccentric bodies 78 is 180 degrees. An external gear 80 is incorporated in each set of eccentric bodies 78 via an eccentric bearing 82. The external gear 80 is in mesh with the internal gear 84. That is, the second speed reduction mechanism 42 includes a plurality of eccentric body shafts 76 at positions offset from the axis O1 of the internal gear 84, and is an eccentric oscillating planetary gear speed reduction mechanism called a distribution type. .

  The internal gear 84 includes an internal gear main body 84A integrated with a casing 86 (specifically, a casing main body 86A described later) of the second reduction gear mechanism 42, and a pin groove 84B formed in the internal gear main body 84A. And an internal pin (first pin member) 84 </ b> C constituting the internal teeth of the internal gear 84. The number of teeth of the internal gear 84 (the number of internal teeth pins 84C) is slightly larger (in this example, “1”) than that of the external gear 80.

  On the other hand, the eccentric body shaft 76 is supported by a first carrier 87 and a second carrier 88 disposed on both sides in the axial direction of the external gear 80 via a pair of tapered roller bearings 85. The first carrier 87 and the second carrier 88 are connected by a bolt 90 via a carrier pin 89 projecting integrally from the second carrier 88 side. Specifically, in this embodiment, the tip 89A of the carrier pin 89 is fitted in a recess 87A formed in the first carrier 87, and the bolt 90 is the portion where the fitting is performed. The carrier pin 89 is connected.

  The first carrier 87 and the second carrier 88 integrated through the carrier pin 89 are integrated with the output shaft 44 through the spline engaging portions 91 and 91. The integrated first carrier 87, second carrier 88, and output shaft 44 constitute an output member Om1 of the second reduction mechanism 42. Various modifications can be considered for the configuration of the output member Om1. Specific modifications will be described later.

  The aforementioned output pinion 24 is formed integrally with the output shaft 44. As described above, the output pinion 24 meshes with the turning gear 28.

  The casing 86 of the second speed reduction mechanism 42 includes a casing main body 86A and a load side cover body 86B and an anti-load side cover body 86C that are connected to both sides in the axial direction via bolts 86E and 86F. . A flange portion 86D that protrudes from the casing main body 86A is fixed to the structure 12A of the nacelle 12 via a bolt 86G, whereby the entire reduction gear G1 is fixed to the nacelle 12. As shown in FIG. 6, in the speed reduction device G <b> 1, the casing 86 is fixed to the lower structure 12 </ b> A <b> 1 of the nacelle 12. Accordingly, most of the second reduction mechanism 42 of the reduction gear G1 can be disposed between the two-stage structures 12A of the nacelle 12, and the volume occupied by the reduction gear G1 in the space P1 of the narrow nacelle 12 is reduced. It is suppressed.

  Hereinafter, regarding the configuration related to the support of the internal tooth pin (first pin member) 84C, the bearing pin 96P (second pin member) of the second bearing 96, and the output member Om1 constituting the internal teeth of the internal gear 84, This will be described in detail.

  As described above, the internal gear 84 of the second reduction gear mechanism 42 is configured by the internal tooth pin (first pin member) 84C. The internal tooth pin 84C is rotatably disposed in a pin groove 84B formed in the casing 86 (the casing main body 86A). The pin groove 84B is formed in a substantially semicircular shape having a cross section perpendicular to the axis (cross section in FIG. 4) having an inner diameter D1 (a shape corresponding to half of a circle having an inner diameter D1) (see FIG. 4). The outer diameter d1 of the internal tooth pin 84C is smaller than the inner diameter D1 of the pin groove 84B (d1 <D1). That is, the internal tooth pin 84C is engaged with the pin groove 84B with a clearance fit, and is rotatable. The pitch circle diameter of the internal tooth pin 84C is d5.

  The internal tooth pin 84C protrudes L1 from the end surface 80A of the external gear 80 on the anti-load side toward the anti-load side in the axial direction, and the outer peripheral surface 87B near the load side of the first carrier 87 faces the protruding portion 84C1. This prevents the anti-load-side dropout from the pin groove 84B.

  The internal tooth pin 84C protrudes by L2 from the end face 80B of the load-side external gear 80, and the protruding portion 84C2 is opposed to the outer peripheral face 88B of the second carrier 88 on the side opposite to the load side. The load side drop-off from the groove 84B is prevented.

  The internal tooth pin 84C is restricted from moving toward the axial load side by a stepped portion (terminal portion of the pin groove 84B) 86H formed in the casing body 86A. Further, the end surface 84C3 of the internal tooth pin 84C is restricted from moving toward the axially opposite load side by abutting against the axial load side end surface 96P1 of the bearing pin 96P described below.

  The ring-shaped groove 86K formed at the end of the pin groove 84B on the load side is a tool escape when the pin groove 84B is formed.

  On the other hand, the output member Om1 composed of the integrated first carrier 87, second carrier 88, and output shaft 44 includes a load-side first bearing 94 composed of a self-aligning roller bearing, and a bearing pin 96P. It is supported by the casing 86 (the casing body 86A thereof) with the second bearing 96 on the side opposite to the load, which is composed of (second pin member).

  The bearing pin 96P is disposed on the non-load side of the pin groove (pin groove in which the internal pin 84C is disposed) 84B formed in the casing 86. That is, the pin groove 84B is formed so as to extend to the axially opposite load side than the oppositely loaded end surface 80A of the external gear 80, and this extending portion 84B1 forms a rolling surface with the bearing pin 96P. While constituting, it also serves as the outer ring of the second bearing 96. Further, the bearing pin 96P is in contact with the outer peripheral surface 87B of the first carrier 87 on the side opposite to the load side. That is, the outer peripheral surface 87B of the first carrier 87 on the side opposite to the load side constitutes a rolling surface with the bearing pin 96P and also serves as an inner ring of the second bearing 96. The bearing pin 96P is restricted from moving in the axial direction anti-load side when the end surface 96P2 on the anti-load side abuts on the casing 86 (the anti-load side cover body 86C), and the end surface 96P1 on the load side is the internal tooth. Movement to the axial load side is restricted by contacting the end face 84C3 of the pin 84C.

  The outer diameter d3 of the bearing pin 96P is larger than the outer diameter d1 of the inner tooth pin 84C. That is, d1 <d3. However, the outer diameter d3 of the bearing pin 96P is smaller than the inner diameter D1 of the pin groove 84B. That is, d1 <d3 <D1, and the bearing pin 96P is engaged with the pin groove 84B with a clearance fit and is rotatable within the pin groove 84B.

  In the specific setting of the magnitude relationship d1 <d3 <D1, it is necessary to consider manufacturing errors of the internal tooth pin 84C, the bearing pin 96P, and the pin groove 84B. For example, the inner tooth pin 84C has a plus error (an error that causes the outer diameter to become larger than the set value), and the bearing pin 96P has a minus error (an error that causes the outer diameter to become smaller than the set value). Even if it has, it is necessary to maintain the state where the outer diameter d3 of the bearing pin 96P is larger than the outer diameter d1 of the inner tooth pin 84C. Even if one of the circumferentially adjacent pin grooves 84B has a plus error and the other has a minus error, in other words, even if the formation of each pin groove 84B varies (external gear 80). Therefore, it is necessary to reliably receive the radial load from the output member Om1 on the bearing pin 96P side (even when the pin is engaged with the inner tooth pin 84C of any pin groove 84B in the circumferential direction). Considering these circumstances, the outer diameter d3 of the bearing pin 96P is preferably larger than the tolerance unit W by five times or more than the outer diameter d1 of the inner tooth pin 84C. That is, 5 · W ≦ (d3−d1).

Here, the tolerance unit W is 3 of d5 when the pitch circle diameter (diameter) of the internal gear pin 84C is d5 and the outer diameter (diameter) of the internal gear pin 84C of the internal gear 84 is d1. Value obtained by adding 0.65 times d1 to the root, ie,
W = d5 ^(1/3) + 0.65 · d1 (1)
Points to the corresponding value.

  Incidentally, the pitch circle diameter d5 of the internal tooth pin 84C tends to be larger than the pitch circle diameter d6 of the bearing pin 96P. This is because an inner tooth pin 84C having an outer diameter d1 smaller than the outer diameter d3 of the bearing pin 96P is incorporated into the same pin groove 84B.

  On the other hand, if the difference (d3−d1) between the two is excessively large (due to the restriction of d3 <D1, the internal tooth pin 84C becomes too thin), the internal tooth pin 84C may flutter in the pin groove 84B. Therefore, the difference (d3−d1) between the outer diameter d3 of the bearing pin 96P and the outer diameter d1 of the inner tooth pin 84C is preferably 15 times or less of the tolerance unit W. After all, the range of 5 · W ≦ (d3−d1) ≦ 15 · W is preferable.

  Next, the operation of the reduction gear G1 will be described.

  When the rotation of the electric motor M1 is transmitted to the input shaft 46 of the first speed reduction mechanism 41 via the joint 38, the outer periphery of the eccentric body 50 integrated with the input shaft 46 via the key 48 rotates eccentrically. The external gear 54 oscillates via the eccentric body bearing 52. In the first reduction gear mechanism 41, since the internal gear 56 (the internal gear main body 56A) is fixed to the casing 58, the external gear 54 swings once every time the input shaft 46 rotates once. Thus, it rotates relative to the internal gear 56 by an angle corresponding to the difference in the number of teeth “1” (rotates relative to the internal gear 56). The relative rotation (rotation) of the external gear 54 with respect to the internal gear 56 is transmitted to the carrier 64 via the sliding promotion member 60 and the internal pin 62 penetrating the external gear 54, and 1 / (external gear). A reduction ratio of 54 (the number of teeth) is realized. Note that the oscillation (movement in the radial direction) of the external gear 54 is absorbed by the gap (free fitting) between the sliding promotion member 60 and the external gear 54.

  In the speed reduction device G1, the carrier 64 of the first speed reduction mechanism 41 is integrated with the output shaft 66, and the output shaft 66 constitutes the input shaft 66 of the second speed reduction mechanism 42. The rotation transmitted to the carrier 64 of the first reduction mechanism 41 becomes the rotation of the input shaft 66 of the second reduction mechanism 42 as it is.

  In the second reduction mechanism 42, when the input shaft 66 rotates, the center gear 70 connected to the input shaft 66 via the key 68 rotates, and the four distribution gears 72 meshed with the center gear 70 are identical to each other. Rotate at the same speed in the direction. As a result, the four eccentric body shafts 76 connected to the respective distribution gears 72 through the spline engaging portions 74 rotate at the same speed in the same direction, and are formed with the phases aligned with the eccentric body shafts 76. The eccentric body 78 is rotated synchronously.

  As a result, each time each eccentric body shaft 76 rotates once, the external gear 80 swings once and rotates relative to the internal gear 84 by an angle corresponding to the difference in the number of teeth “1” (internal teeth). It rotates with respect to the gear 84). The relative rotation (spinning) of the external gear 80 with respect to the internal gear 84 is the first and second carriers that support the eccentric body shaft 76 via the eccentric body shaft 76 that passes through the external gear 80. 87, 88.

  The rotation transmitted to the first and second carriers 87 and 88 is transmitted to the output shaft 44 through the spline engaging portions 91 and 91 and further transmitted to the output pinion 24 integrated with the output shaft 44. . The rotation of the output pinion 24 tries to rotate the swivel gear 28. However, since the swivel gear 28 is attached to the cylindrical column 11 side of the wind power generation facility 10, the output pinion 24 itself and the swivel gear 28 are reacted. Revolving around the axis 37 of the swivel gear 28 while meshing. As a result, the nacelle 12 to which the reduction gear G1 supporting the output pinion 24 is fixed pivots about the axis of the cylindrical column 11 (the axis of the pivoting gear 28) 37 as the pivot axis.

  Here, for example, when a situation occurs in which the nacelle 12 is forcibly swiveled due to the influence of a strong wind, a gust of wind, etc., the output pinion 24 side receives a reaction force from the swivel gear 28 fixed to the cylindrical column 11. Therefore, a strong radial load is input. This radial load is applied to the output member Om1 including the output shaft 44 integrated with the output pinion 24. Specifically, the output member Om1 tends to tilt its axis O1 with the first bearing 94 as a fulcrum. The radial load of the output member Om1 is sometimes extremely large. If the radial load is applied to the internal tooth pin 84C, the smooth engagement between the external gear 80 and the internal gear 84 is hindered, and the eccentric body. The durability of the bearing 82 is lowered, or the tooth surface of the external gear 80 is easily damaged.

  However, with respect to this problem, according to the present reduction gear G1, the following action can be obtained.

  First, the second bearing 96 supporting the output member Om1 on the non-load side is provided by the bearing pin 96P disposed in the pin groove 84B for disposing the internal tooth pin 84C constituting the internal tooth of the internal gear 84. Since it is configured, the pitch circle diameter d6 of the second bearing 96 (bearing pin 96P) is very large. Therefore, sufficient load resistance can be exhibited with respect to the radial load transmitted to the output member Om1.

  Further, the outer diameter d3 of the bearing pin 96P is formed larger than the outer diameter d1 of the inner tooth pin 84C. For this reason, the bearing pin 96P is incorporated in a pin groove 84B having the same inner diameter D1 with a smaller gap than the internal tooth pin 84C. For this reason, when the output member Om1 receives a radial load and tilts about the first bearing 94, the bearing pin 96P contacts the pin groove 84B first (faster than the inner tooth pin 84C contacts the pin groove 84B), and the casing The reaction force can be received from the 86 side. At this time, since the outer diameter d1 is small on the inner tooth pin 84C side, a slight gap is ensured between the pin groove 84B and hardly receives the radial load. Therefore, most of the radial load input via the output member Om1 can be received by the bearing pin 96P, and the radial load applied to the internal tooth pin 84C can be reduced accordingly.

  Further, according to the reduction gear G1 according to the present embodiment, the outer diameter d3 of the bearing pin 96P is further set to be greater than five times the tolerance unit W than the outer diameter d1 of the inner tooth pin 84C. For example, even if the inner tooth pin 84C has a plus error and the bearing pin 96P has a minus error, the outer diameter d3 of the bearing pin 96P is larger than the outer diameter d1 of the inner tooth pin 84C. A relationship can be maintained. Further, even when one of the circumferentially adjacent pin grooves 84B has a plus error and the other has a minus error, in other words, even if the formation of each pin groove 84B varies (external gear 80). (Even when engaged with the internal pin 84C of any pin groove 84B in the circumferential direction), the bearing pin 96P can reliably receive the radial load from the output member Om1.

  Furthermore, in the present embodiment, the difference (d3-d1) between the outer diameter d3 of the bearing pin 96P and the outer diameter d1 of the inner tooth pin 84C is set to 15 times or less of the tolerance unit W. For example, it is possible to prevent the internal tooth pin 84C from becoming too small relative to the pin groove 84B and causing the internal tooth pin 84C to flutter within the pin groove 84B.

  The outer diameter d3 of the bearing pin 96P is set smaller than the inner diameter D1 of the pin groove 84B (although it is larger than the outer diameter d1 of the inner tooth pin 84C). For this reason, for example, the bearing pin 96P becomes too large relative to the pin groove 84B, and the bearing pin 96P cannot be smoothly rotated in the pin groove 84B, or the bearing pin 96P is inserted into the pin groove 84B. It is possible to prevent the bearing pin 96P from coming into contact with the pin groove 84B only near the end of the pin groove 84B.

  Furthermore, in the reduction gear G1 according to the present embodiment, the bearing pin 96P is disposed on the side opposite to the axial load side from the internal tooth pin 84C (that is, the external gear 80 between the first bearing 94 and the second bearing 96). When the output member Om1 is supported by the casing 86 so as to sandwich the meshing portion of the internal gear 84), the axial center O1 of the output member Om1 tends to tilt around the first bearing 94 due to the radial load. In addition, the bearing pin 96P is located on the side where the displacement becomes larger than the internal tooth pin 84C. For this reason, it is possible to more reliably secure a gap between the internal tooth pin 84C and the pin groove 84B, and to prevent the radial load from being applied to the internal tooth pin 84C. Further, since the bearing pin 96P is arranged on the axially opposite load side than the internal tooth pin 84C, a large bearing span between the first bearing 94 and the second bearing 96 can be obtained. Coupled with the large pitch circle diameter d6, the output member Om1 can be supported in a more stable state.

  Further, in the present reduction gear G1, since the second bearing 96 is positioned on the outer peripheral surface 87B of the first carrier 87, there is no expansion of the axial space due to the provision of the second bearing 96, and the reduction gear. The axial length of the entire G1 can be kept short.

  In the speed reduction device G 1, the outer ring of the second bearing 96 is configured by a pin groove 84 B formed in the casing 86, and the inner ring is configured by the outer peripheral surface 87 B of the first carrier 87. That is, since the second bearing 96 does not have a dedicated inner and outer ring, it is possible to prevent the reduction gear G1 from becoming large in the overall radial direction due to the arrangement of the second bearing 96. Since the two bearings 96 are disposed, the number of parts can be prevented from increasing.

  Furthermore, the axial movement of the internal tooth pin 84C and the bearing pin 96P is restricted by the step 86H of the casing 86 or the casing 86 itself (the anti-load side cover body 86C). Even if a load in the thrust direction is applied to 84C or the bearing pin 96P, the load in the thrust direction can be reliably received.

  FIG. 7 shows an example (second embodiment) of another embodiment of the present invention.

  In this reduction gear G2, an electric motor M2, an orthogonal gear reduction mechanism 140, a parallel shaft reduction mechanism 142, and an eccentric oscillating planetary gear reduction mechanism 144 are arranged in this order on the power transmission path.

  The orthogonal gear reduction mechanism 140 includes a hypoid pinion 147 and a hypoid gear 150. The parallel axis reduction mechanism 142 includes a spar pinion 154 and a spar gear 156. The spur gear 156 is connected to a hollow shaft 165 having a hollow structure. An input shaft 166 of the planetary gear speed reduction mechanism 144 is connected to the hollow shaft 165 via a key 168.

  The planetary gear reduction mechanism 144 is a center crank type eccentric oscillating planetary gear reduction mechanism, and includes the input shaft 166, the two eccentric bodies 178 integrated via the input shaft 166 and the key 169, Two external gears 180 incorporated in the outer periphery of the eccentric body 178 and swung by the eccentric body 178, and an internal gear 184 in which the external gear 180 is internally meshed while swinging are provided.

  The casing 186 of the planetary gear speed reduction mechanism 144 is mainly composed of a first casing body 186A, a second casing body 186B, an anti-load side cover body 186C, and a load side cover body 186D, and the nacelle 12 is connected via a bolt 186E. It is fixed to the structure 12A.

  The internal gear 184 of the planetary gear speed reduction mechanism 144 includes an internal gear main body 184A integrated with the first casing body 186A, and the internal teeth are arranged in a pin groove 184B formed in the first casing body 186A. The internal pin (first pin member) 184C thus formed. The number of internal teeth of the internal gear 184 (the number of internal teeth pins 184C) is slightly larger (by “1” in this example) than the number of external teeth of the external gear 180.

  A plurality of internal pins 162 (12 in this example) penetrate the external gear 180 on the same circumference together with the sliding promotion member 160. The inner pin 162 is integrated with the carrier 164 by press fitting, and the carrier 164 is integrated with the output shaft 145 of the reduction gear G2 (not by a spline or the like) from the beginning.

  The output shaft 145 and the carrier 164 constitute an output member Om2. The output member Om2 is supported by a first bearing 194 configured by a self-aligning roller bearing incorporated in the second casing body 186B, and a second bearing 196 disposed on the inner periphery of the first casing body 186A. . The second bearing 196 is configured by a bearing pin 196P (second pin member) disposed in the pin groove 184B. The magnitude relationship between the internal tooth pin 184C and the bearing pin 196P is the same as that in the first embodiment. That is, the outer diameter d103 of the bearing pin 196P is formed larger than the outer diameter d101 of the inner tooth pin 184C. It should be noted that the specific setting range is preferably set to the same setting range as in the first embodiment.

  An output pinion 124 is connected to the output shaft 145 via a spline engaging portion 192, and the output pinion 124 is configured to mesh with the swivel gear 28 (FIGS. 5 and 6) already described.

  Also in this embodiment, as in the previous embodiment, the radial load that should be applied to the bearing pin 192P that supports the output member Om2 is applied to the internal tooth pin 184C that constitutes the internal teeth of the internal gear 184. The effect of reducing is obtained.

  In the first embodiment, the bearing pin 96P is disposed on the axially opposite load side of the internal tooth pin 84C. However, in the present invention, for example, as in the second embodiment, the bearing pin 196P is disposed on the axial load side of the internal gear pin 184C, and is more than the meshing portion of the external gear 180 and the internal gear 184. The output member Om2 may be supported on the axial load side.

  In the first embodiment, the carrier pin 89 is integrated with the second carrier 88 from the beginning, and the carrier pin 89 protrudes from the second carrier 88 itself. However, in the present invention, the carrier pin does not necessarily have to be integrated with the second carrier (for example, it may be integrated by press-fitting or the like), and for example, the second embodiment. In this way, the configuration may be such that only the inner pin 162 is provided without the carrier pin.

  In the first embodiment, the first carrier 87 and the second carrier 88 and the output shaft 44 are integrated via the spline engaging portions 91 and 91. In this configuration, since the radial load caused by the wind load transmitted to the output shaft 44 via the output pinion 24 can be cut off to some extent at the spline engaging portions 91 and 91, the (first and second) carriers 87. The radial load transmitted to the 88 side can be reduced. However, the configuration in which the output shaft 44 is connected to the first carrier 87 and the second carrier 88 via the spline engaging portions 91 and 91 is not necessarily an essential configuration in the present invention. For example, in the second embodiment, the carrier 164 and the output shaft 145 are integrated from the beginning. When the output shaft 145 and the carrier 164 are integrated from the beginning as in the second embodiment, the shaft center of the output shaft 145 and the carrier 164 is less likely to be shaken, and the rigidity of the entire output member Om2 is maintained high. The advantage that you can do it. This configuration is a preferable structure particularly when the configuration in which the bearing pin 96P is disposed on the axial load side of the internal tooth pin 184C as in the second embodiment. In the second embodiment, unlike the first embodiment, the output shaft 145 and the output pinion 124 are not integrated but connected via a spline engaging portion 192. That is, the spline engaging portion is provided not on the first bearing 194 and the second bearing 196 but on the load side of the first bearing 194, so that the radial load of the output pinion 124 is directly applied to the output member Om2 side. It is considered not to be transmitted to.

  In each of the above embodiments, the outer periphery of the carrier also serves as the inner ring of the bearing pin. However, the present invention is not limited to this, and a dedicated (independent) inner ring for housing the bearing pin is provided. May be.

  The present invention is not only a yaw drive system for wind power generation equipment, but also a pitch drive system that changes the direction of the blades, and also a photovoltaic light receiving panel that may be subjected to wind load to cause a reverse power phenomenon. For example, the present invention can be applied to a reduction gear that changes the light receiving direction and the light receiving angle. That is, the present invention can be suitably used for a reduction device for a natural energy recovery system used in an environment where there is a risk of receiving an unexpectedly large load due to a gust or strong wind. Further, the present invention can be applied to uses other than the natural energy recovery system, for example, a turning drive device for a construction machine.

DESCRIPTION OF SYMBOLS 80 ... External gear 84 ... Internal gear 84A ... Internal gear main body 86 ... Casing 86A ... Casing main body 87 ... 1st carrier 88 ... 2nd carrier 94 ... 1st bearing 96 ... 2nd bearing 96P ... Bearing pin Om1 ... Output Element

Claims (5)

An internal gear,
An output member supported by a casing via a bearing and rotating with respect to the internal gear ,
The internal gear has an internal gear main body integrated with the casing, and the internal teeth are configured by a first pin member disposed in a pin groove formed in the casing.
The bearing is constituted by a second pin member disposed in the pin groove of the casing, and
The speed reducing device, wherein an outer diameter of the second pin member is formed larger than an outer diameter of the first pin member. In claim 1,
The reduction gear according to claim 1, wherein an outer diameter of the second pin member is at least five times greater than a tolerance unit W than an outer diameter of the first pin member. In claim 1 or 2,
The difference between the outer diameter of the second pin member and the outer diameter of the first pin member is not more than 15 times the tolerance unit W. In any one of Claims 1-3,
The speed reducing device, wherein an outer diameter of the second pin member is smaller than an inner diameter of the pin groove. In any one of Claims 1-4,
The speed reduction device, wherein the second pin member is disposed on an axially opposite load side than the first pin member.

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