JP2010065542A - Drive device for wind turbine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drive device for a wind turbine capable of increasing the output torque, with a smaller size, and suppressing a drop of the durability in each deceleration part. <P>SOLUTION: A first stage deceleration part 13 is equipped with first stage internal teeth 18, a first stage gear 19, a first stage crankshaft 20, and a first stage carrier 21 fitted with a bush pin 21b. A second stage deceleration part 14 is equipped with second stage internal teeth 28, a second stage external gear 29, a second stage center crankshaft 30, a plurality of second stage guide crankshafts 31, a second carrier 32 having a base carrier part 34 and an end carrier part 35, and a pair of main bearings 33 to retain the second stage carrier 32 rotatably with respect to a case 11. On the base carrier part 34, an output shaft 15 is formed integrally, with which a pinion 101 for output is coupled. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a windmill drive device that is provided in a windmill and is used as a drive device that drives equipment in the windmill.

  In windmills, devices in windmills are driven, such as a drive device for yaw drive that turns the nacelle provided at the top of the tower of the windmill and a drive device for pitch drive that changes the pitch angle of the blades attached to the nacelle. A windmill driving device used as a driving device is provided (see, for example, Patent Document 1). Patent Document 1 discloses a yaw drive device that includes a pinion that meshes with a ring gear at the top of a tower. In the above-described windmill, in recent years, there is a demand for a high-power specification windmill drive device that improves the output torque because the windmill size tends to increase or the blade diameter tends to increase. . On the other hand, since the space for disposing the wind turbine drive device in the wind turbine is limited, a more compact structure is also required.

  On the other hand, as a reduction gear capable of realizing a large reduction ratio necessary for improving output torque and downsizing, as disclosed in Patent Document 2, 2 for rotating the arm of an industrial robot. What was comprised as an eccentric type reduction gear of a stage structure is known. In the reduction gear disclosed in Patent Document 2, a first-stage reduction unit to which a driving force is input from an electric motor, and a second-stage reduction unit to which a driving force is input from the first-stage reduction unit. And an external gear that rotates eccentrically at each speed reduction portion. In the second speed reduction portion, the carrier formed as the first and second output flanges (266, 268) fixed by the carrier pin (280) is formed as the conical roller bearing (270, 272). A pair of main bearings are rotatably held with respect to the case. The speed reducer is provided to rotate the second arm (14) with respect to the first arm (12) of the industrial robot, and the carrier of the second-stage speed reduction unit corresponds to the output shaft. The two arms (14) are attached with bolts.

JP 2001-289149 A JP 2004-301273 A

  In the wind turbine drive device disclosed in Patent Document 1, it is conceivable to apply the speed reducer disclosed in Patent Document 2 to improve the output torque and reduce the size. However, in the speed reducer disclosed in Patent Document 2, the carrier of the second-stage speed reduction portion held by the pair of main bearings is attached to the second arm (14) corresponding to the output shaft via a bolt. It has become. For this reason, when the speed reducer disclosed in Patent Document 2 is used as a wind turbine driving device, the driving force output from the output shaft increases, and as a reaction, a large torque acts on the output shaft from the wind turbine side. There is a possibility that an inclination is likely to occur between the carrier held by the main bearing and the output shaft fixed to the carrier with a bolt. When such an inclination occurs, in particular, in the second-stage reduction part, it is easy for the eccentric gear and the internal gear that engages with the external gear to be easily deviated. There is a problem that it falls.

  In view of the above circumstances, an object of the present invention is to provide a windmill drive device that can improve output torque and reduce the size, and can also suppress a decrease in durability in a speed reduction portion.

  A windmill drive device according to a first invention for achieving the above object is a windmill drive device provided in a windmill and used as a drive device for driving a device in the windmill, the case being housed in the case. And a first-stage reduction part that is a first-stage reduction part to which the driving force from the electric motor is input, and a second stage that is housed in the case and receives the driving force from the first-stage reduction part A second-stage reduction part, which is a reduction part, and an output shaft fixed to the second-stage reduction part. In the wind turbine drive device according to the first aspect of the present invention, the first stage reduction portion includes a first stage inner tooth provided on an inner circumference of the case and an outer tooth meshing with the first stage inner tooth on the outer circumference. The first-stage external gear provided, the first-stage crankshaft that is disposed at the center in the radial direction and eccentrically rotates the first-stage external gear, and the first-stage external gear are formed. A first stage carrier provided with a bush pin penetrating through the hole in a loosely fitted state, and the second stage reduction part includes a second stage internal tooth provided on an inner periphery of the case, and the first stage A second-stage external gear having external teeth meshing with the two-stage internal teeth, and a second-stage external gear disposed at the center in the radial direction and fixed to the first-stage carrier and decentering the second-stage external gear. And a plurality of second stage center crankshafts that are rotated in a circumferential direction around the second stage center crankshaft. A second-stage guide crankshaft that passes through a hole formed in the second-stage external gear, and one end side of each of the second-stage center crankshaft and the second-stage guide crankshaft are rotatable via a bearing. A second carrier having a base carrier to be held on the end carrier and an end carrier to rotatably hold the other end side of each other via a bearing, and a pair of the second carrier to hold the second carrier in a rotatable manner with respect to the case And a main bearing, wherein the output shaft is integrally formed with the base carrier, and an output pinion is coupled to the output shaft.

  According to the present invention, the wind turbine driving device is configured as a two-stage eccentric reduction gear provided with external gears that rotate eccentrically in the first-stage reduction part and the second-stage reduction part, respectively. For this reason, a large reduction ratio can be ensured and the output torque can be improved. And since it is comprised as an eccentric type reduction gear of 2 steps | paragraphs, a big reduction ratio is realizable with a small structure. In the wind turbine driving device of the present invention, the base carrier in the second stage carrier of the second stage reduction part is formed integrally with the output shaft to which the output pinion is coupled, and the second stage carrier is attached to the case. It is held by a pair of main bearings. For this reason, since it is a windmill application, even when the driving force output from the output shaft increases and a large torque acts on the output shaft as a reaction, the output shaft is formed integrally with the base carrier. Is held by the pair of main bearings together with the second stage carrier. As a result, even if a large torque acts as a reaction from the pinion, the inclination of the output shaft and the second-stage carrier is reduced, and the second-stage internal gear and the second-stage external gear are unevenly contacted. It is suppressed. For this reason, a decrease in durability of the second stage external gear is suppressed, and a decrease in durability as the second stage reduction gear is also suppressed.

  Therefore, according to the present invention, it is possible to provide a windmill drive device that can improve the output torque and reduce the size, and can also suppress a decrease in durability in the speed reduction portion.

  An eccentric type reduction gear according to a second aspect of the invention is the eccentric type reduction gear of the first aspect, wherein the first stage external gear is provided as one external gear, and the second stage external gear is provided as three pieces. It is provided as an external gear.

  According to the present invention, since the first stage external gear has a low load, the first stage due to friction loss caused by sliding between the first stage external gear and the first stage internal teeth even when the bush pin is used. A reduction in drive efficiency of the speed reduction unit is suppressed. And since it is comprised as one external gear, it can reduce external gears and can reduce cost. Further, in this wind turbine drive device, although the load is increased in the second-stage reduction part, the second-stage guide crankshaft that transmits the rotation of the second-stage external gear to the second-stage carrier is connected to the base via the bearing. By being held by the carrier and the end carrier, it is possible to suppress a decrease in driving efficiency of the entire second-stage reduction unit. Furthermore, the second stage external gear is composed of three pieces, so that the second stage reduction part has a small diameter while maintaining the surface pressure between the second stage external gear and the second stage internal gear. be able to. Therefore, according to this wind turbine drive device, it is possible to reduce the size and the diameter without reducing the drive efficiency.

  The eccentric speed reducer according to a third aspect of the present invention is the wind turbine drive device according to the first aspect or the second aspect of the invention, wherein the rotational speed of the first stage carrier is in a range of 19 rpm to 65 rpm. A reduction ratio of the first stage reduction part and a reduction ratio of the second stage reduction part are set.

  According to this invention, the reduction ratios of the first stage reduction part and the second stage reduction part are set so that the magnitude of the rotation speed of the first stage carrier is 19 rpm or more and 65 rpm or less. For this reason, the first stage carrier can be rotated in the range of the rotational speed at which the driving efficiency is extremely good in the first stage reduction section where the driving efficiency is lower than that of the second stage reduction section. Thereby, the fall of drive efficiency can further be suppressed. As a result of verification by the inventors of the present invention regarding the magnitude of the rotational speed of the first stage carrier, it was confirmed that the driving efficiency rapidly deteriorates because the speed approaches the boundary lubrication region at less than 19 rpm. Moreover, when it exceeded 65 rpm, it became a fluid lubrication area | region, and it has confirmed that the fixed loss of the stirring resistance and frictional resistance accompanying a rotational speed increase became large, and efficiency deteriorated.

  An eccentric type speed reducer according to a fourth aspect of the invention is characterized in that, in the wind turbine drive device according to the third aspect of the invention, the reduction ratio of the second stage reduction part is larger than the reduction ratio of the first stage reduction part. .

  According to the present invention, the speed reduction ratio is set to be larger in the second speed reduction part than in the first speed reduction part. Here, the “reduction ratio” refers to the ratio of the rotational speed on the input side to the rotational speed on the output side. For this reason, according to the present invention, the reduction ratio is set to be small in the first stage reduction part where the drive efficiency is lower than that of the second stage reduction part, and the overall drive efficiency is further improved. Can do.

  ADVANTAGE OF THE INVENTION According to this invention, while aiming at the improvement and size reduction of an output torque, the drive device for windmills which can also suppress the fall of durability in a deceleration part can be provided.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. A windmill drive device according to an embodiment of the present invention is provided in a windmill and can be widely used as a drive device for driving devices in the windmill, and in particular, a pitch drive device for pitch drive and a yaw drive device for yaw drive. Can be used as In the present embodiment, the case where it is used as a yaw drive device will be described as an example. However, the present invention is not limited to this example, and can be widely applied to other wind turbine drive devices including a pitch drive device.

  FIG. 1 is a cross-sectional view showing a windmill drive device 1 according to an embodiment of the present invention. The windmill drive device 1 is used as a yaw drive device, and decelerates and transmits the rotation input from an electric motor (not shown) arranged on the upper side and outputs it. The windmill drive device 1 includes a case 11, an input shaft 12, a first stage reduction unit 13, a second stage reduction unit 14, and an output shaft 15.

  As shown in FIG. 1, the wind turbine drive device 1 is configured such that an output pinion 101 is coupled by spline coupling to an output shaft 15 positioned so as to protrude from the case 11 on one end side disposed on the lower side. An electric motor (not shown) is attached to the case 11 on the other end side. Then, the driving force from the electric motor is input to the first stage reduction unit 13 that is the first stage reduction unit, and the first stage reduction unit 13 is driven to the second stage reduction unit 14 that is the second stage reduction unit. Force is input. The output shaft 15 is fixed to the second stage speed reduction unit 14. As described above, in the wind turbine driving device 1, the driving force input from the electric motor disposed on the upper side is decelerated through the first stage reduction unit 13 and the second stage reduction unit 14 housed in the case 11. And transmitted to the pinion 101 coupled to the output shaft 15.

  When the windmill drive device 1 is used as a yaw drive device as in this embodiment, the windmill drive device 1 is arranged so that the pinion 101 meshes with a gear fixed to the upper part of the tower of the windmill. . And the windmill drive device 1 is actuated by the driving force from the electric motor and the pinion 101 is rotated, whereby the nacelle of the windmill is turned. In the following description, in the wind turbine drive device 1, the output side on which the output shaft 15 is disposed is described as one end side, and the input side on which the electric motor is mounted is described as the other end side.

  As shown in FIG. 1, the case 11 has a cover case 16 that is disposed on the other end side to which the electric motor is attached, and a cylindrical shape that is disposed on the one end side and is coupled to the cover case 16 by bolts at the edges. And a main body case 17. The cover case 16 is arranged in series from one end side to the other end side along the axial direction that is the direction of the rotation center line P (illustrated by a one-dot chain line in FIG. 1) of the windmill drive device 1 and is coupled by bolts. The first cover case portion 16a, the second cover case portion 16b, and the third cover case portion 16c are configured. The first cover case portion 16a is formed in a disc shape having a through hole through which the input shaft 12 and a first-stage crankshaft 20 of a first-stage speed reduction unit 13 (to be described later) penetrate at the center, and an electric motor on the other end side. Is fixed. The second cover case portion 16b is formed in a ring shape in which the other end side is coupled to the first cover case portion 16a and one end side is coupled to the third cover case portion 16c. Step internal teeth 18 are arranged. The third cover case portion 16c is formed in a cylindrical shape whose diameter changes so as to expand into a flange shape. The third cover case portion 16c protrudes in a flat plate shape toward the inner side in the radial direction on the inner periphery, and the first step reduction portion 13 is formed. The first stage carrier 21 is rotatably supported via a ball bearing 27 so as to form a carrier support portion 16d. The main body case 17 is formed in a cylindrical shape, and the other end side is coupled to the third cover case portion 16c with a bolt, and one end side is formed with an opening. A second-stage internal tooth 28 of the second-stage deceleration unit 14 to be described later is disposed on the inner periphery of the main body case 17. The input shaft 12, the first-stage reduction unit 13 and the second-stage reduction unit 14 arranged in the case 11, and the output shaft 15 are arranged in series along the axial direction of the wind turbine driving device 1. ing.

  As shown in FIG. 1, the input shaft 12 is provided as a short shaft-like member and is disposed on the rotation center line P. The other end of the input shaft 12 is coupled to the output shaft 100 of the electric motor, and one end of the input shaft 12 is formed integrally with the first stage crankshaft 20 of the first stage reduction unit 13.

  FIG. 2 is an enlarged cross-sectional view showing the first stage reduction unit 13 and the second stage reduction unit 14 in FIG. 1 and the vicinity thereof. As shown in FIGS. 1 and 2, the first stage reduction unit 13 includes a first stage internal tooth 18, a first stage external gear 19, a first stage crankshaft 20, a first stage carrier 21, and the like. It is configured as a crank-type eccentric reduction part. A plurality of first-stage inner teeth 18 are provided, and are provided on the inner periphery of the cover case 16 in the case 11 in a state of being fitted in and attached to a pin groove formed on the inner periphery of the second cover case portion 16b. ing. The first-stage internal teeth 18 (in FIG. 1 and FIG. 2, the outer shape is shown in cross section) are formed as pin-shaped members (round bar-shaped members), and the longitudinal direction thereof is positioned parallel to the rotation center line P. Is arranged. The first stage internal teeth 18 are arranged at equal intervals along the circumferential direction on the inner periphery of the cover case 16 and are configured to mesh with the external teeth of the first stage external gear 19.

  The first stage crankshaft 20 shown in FIGS. 1 and 2 is formed integrally with the output shaft 100 of the electric motor at the other end. The first-stage crankshaft 20 is arranged at the center in the radial direction of the wind turbine drive device 1 (that is, the direction perpendicular to the rotation center line P), and the axial direction is arranged along the rotation center line P. Has been. The other end of the first stage crankshaft 20 is rotatably held via a ball bearing 22 with respect to the inner periphery of the first cover case portion 16 a, and one end of the first stage crankshaft 20 is a ball bearing 23 with respect to the first stage carrier 21. It is hold | maintained rotatably via. The first stage crankshaft 20 has an eccentric portion 24 having a circular cross section disposed so that the center position in the radial direction is eccentric with respect to the rotation center line P on the outer periphery of the intermediate portion via the key 25. It is fixed. The first stage crankshaft 20 passes through a through hole 19a formed in the central portion of the first stage external gear 19, and a cylindrical roller bearing (or needle roller bearing) 26 is inserted into the through hole 19a. The eccentric part 24 is rotatably held via the. Thus, the first stage crankshaft 20 is provided as a shaft member that rotates and rotates the first stage external gear 19 eccentrically.

  The first stage external gear 19 shown in FIGS. 1 and 2 is provided as a single external gear. As described above, the first stage external gear 19 is formed with the through hole 19a through which the first stage crankshaft 20 passes in the central portion, and the eccentric portion of the first stage crankshaft 20 is formed in the through hole 19a. 24 is rotatably held via a cylindrical roller bearing 26. The first stage external gear 19 is also formed with a plurality of (for example, four) through-holes 19b arranged at equal angular positions along the circumferential direction. The bush pin 21b of the first stage carrier 21 passes through the through hole 19b in a loosely fitted state. Further, external teeth that mesh with the first stage internal teeth 18 are provided on the outer periphery of the first stage external gear 19. The number of external teeth of the first stage external gear 19 is provided to be one or more than the number of teeth of the first stage internal teeth 18. For this reason, every time the first stage crankshaft 20 rotates, the meshing between the external teeth of the first stage external gear 19 and the first stage internal teeth 18 shifts, and the first stage external gear 19 swings eccentrically. It is configured to rotate. The position of the first step external gear 19 in the axial direction is defined by a protrusion formed so as to protrude from one end side of the first cover case portion 16a and the other end side of the third cover case portion 16c. Yes.

  A first stage carrier 21 shown in FIG. 1 and FIG. 2 is arranged around a rotation center line P, and is formed in a disk shape that is gradually enlarged in a flange shape, and in addition to the carrier body 21a. A plurality of (for example, four) bush pins 21b provided so as to protrude to the end side. The carrier body 21 a rotatably holds one end side of the first stage crankshaft 20 via a ball bearing 23 in a recess formed in the central portion on the other end side. Then, one end side of the carrier body 21a is rotatable via a ball bearing 27 with respect to the carrier support portion 16d formed so as to protrude inward and project in a ring shape on the inner periphery of the third cover case portion 16c. Is retained. Furthermore, one end side of the carrier body 21a is fixed to the other end side of the second stage center crankshaft 30 of the second stage reduction part 14 described later by spline coupling. A plurality of bush pins 21b are arranged at equal angular positions along the circumferential direction of the carrier body 21a, and are loosely fitted in the through holes 19b formed in the first stage external gear 19 as described above. It is provided to penetrate. Further, the bush pin 21b is provided with a roller body in sliding contact with the through hole 19b in the outer peripheral portion.

  As shown in FIGS. 1 and 2, the second stage reduction unit 14 includes a second stage internal tooth 28, a second stage external gear 29, a second stage center crankshaft 30, a second stage guide crankshaft 31, A two-stage carrier 32, a pair of main bearings 33, and the like are provided and configured as a center crank type eccentric reduction part. A plurality of second-stage internal teeth 28 are provided, and are provided on the inner periphery of the case 11 in a state of being fitted and attached to pin grooves formed on the inner periphery of the main body case 17. The second-stage inner teeth 28 (the outer shape is not shown in cross section in FIGS. 1 and 2) is formed as a pin-shaped member (round bar-shaped member), and its longitudinal direction is positioned parallel to the rotation center line P. Is arranged. The second stage internal teeth 28 are arranged at equal intervals along the circumferential direction on the inner periphery of the main body case 17, and are configured to mesh with the external teeth of the second stage external gear 29.

  The second stage center crankshaft 30 shown in FIGS. 1 and 2 is arranged at the center in the radial direction of the wind turbine drive device 1, and the axial direction thereof is arranged along the rotation center line P. The second stage center crankshaft 30 is rotatably held with respect to the second stage carrier 32 at one end side via a tapered roller bearing 37 and the other end side via a tapered roller bearing 38. The end of the second stage center crankshaft 30 on the other end side is fixed to the first stage carrier 21 by spline coupling as described above. Further, the second stage center crankshaft 30 is formed with a first eccentric part 30a, a second eccentric part 30b, and a third eccentric part 30c in the middle of the second stage center crankshaft 30, and is provided in series in this order from one end side. Yes. The first to third eccentric portions (30 a to 30 c) are formed so that a cross section perpendicular to the axial direction is a circular cross section, and each center position is eccentric with respect to the rotation center line of the second stage center crankshaft 30. It is provided to do. Further, the second stage center crankshaft 30 is disposed so as to penetrate a center crank hole 39 formed in the center portion of the second stage external gear 29, and is rotated to rotate the second stage external gear. 29 is provided as a shaft member that rotates eccentrically.

  The second stage external gear 29 shown in FIG. 1 and FIG. 2 is provided as three external gears, and is arranged in parallel with the first external gear 29a and the second external gear accommodated in the case 11. It comprises a tooth gear 29b and a third external gear 29c. In the three external gears (29a to 29c) of the second stage external gear 29, as described above, the center crank holes 39 through which the second stage center crankshaft 30 passes are circular holes in the respective central portions. It is formed as. In each center crank hole 39, the first external gear 29a is connected to the first eccentric portion 30a via the cylindrical roller bearing 40a, and the second external gear 29b is connected to the second eccentric portion 30b via the cylindrical roller bearing 40b. The third external gear 29c rotatably holds the third eccentric portion 30c via the cylindrical roller bearing 40c. The cylindrical roller bearings (40a to 40c) may be configured as needle roller bearings.

  Each external gear (29a-29c) of the second stage external gear 29 has a guide crank hole 41 through which the second stage guide crankshaft 31 penetrates, in addition to the center crank hole 39, and will be described later. A support hole 42 through which the support 36 of the second stage carrier 32 passes is further formed. In the first to third external gears (29a to 29c), the positions of the center crank hole 39, the guide crank hole 41, and the column hole 42 correspond to each other in the direction parallel to the rotation center line P. Are arranged as follows. The guide crank hole 41 is formed as a circular hole passing therethrough, and a plurality of (for example, three) are provided at equal angular positions along the circumferential direction of the second stage external gear 29 corresponding to the second stage guide crankshaft 31. ) Is arranged. Further, a plurality (for example, three) of the support holes 42 are arranged at equal angular positions along the circumferential direction of the second-stage external gear 29 corresponding to the support 36 of the second-stage carrier 32. Further, the support hole 42 is formed alternately with the guide crank hole 41 in the circumferential direction of the second stage external gear 29. In addition, the support | pillar 36 penetrates the support | pillar hole 42 in the non-contact loose fitting state.

  In addition, external teeth that mesh with the second-stage internal teeth 28 are provided on the outer circumferences of the first to third external gears (29 a to 29 c). The number of external teeth of the first to third external gears (29 a to 29 c) is provided to be one or more than the number of teeth of the second stage internal teeth 28. For this reason, every time the second stage center crankshaft 30 rotates, the meshing between the external teeth of the second stage external gear 29 (29a to 29c) and the second stage internal teeth 28 shifts, and the second stage external gear 29 (29a-29c) is configured to be eccentric and swing and rotate.

  The second stage guide crankshaft 31 shown in FIG. 1 and FIG. 2 is positioned at an equal angle around the second stage center crankshaft 30 along the circumferential direction (that is, the circumferential direction around the rotation center line P). A plurality (for example, three) are arranged, and are arranged so that their axial directions are parallel to the rotation center line P. Each second stage guide crankshaft 31 is rotatably held with respect to the second stage carrier 32 at one end side via a tapered roller bearing 43 and the other end side via a tapered roller bearing 44. Each second-stage guide crankshaft 31 is disposed so as to penetrate each guide-crank hole 41 of the second-stage external gear 29 as described above.

  Each second-stage guide crankshaft 31 is formed with a first eccentric portion 31a, a second eccentric portion 31b, and a third eccentric portion 31c in the middle of the second-stage guide crankshaft 31, and is provided in series in this order from one end side. ing. The first to third eccentric portions (31 a to 31 c) are formed so that a cross section perpendicular to the axial direction is a circular cross section, and each center position is eccentric with respect to the rotation center line of the second stage guide crankshaft 31. It is provided to do. In each guide crank hole 41 of the second stage external gear 29, the first eccentric portion 31a is in a needle shape with respect to the first external gear 29a via the needle roller bearing 45a. The third eccentric portion 31c is rotatably held with respect to the second external gear 29b via the roller bearing 45b and is rotatably supported with respect to the third external gear 29c via the needle roller bearing 45c. The needle roller bearings (45a to 45c) may be configured as cylindrical roller bearings. With the arrangement as described above, the second-stage guide crankshaft 31 rotates while the second-stage external gear 29 oscillates and rotates inside the guide-crank hole 41, so that the second-stage external teeth. As the gear 29 rotates, a revolving operation is performed around the rotation center line P around the second stage center crankshaft 30. In addition, the phase of each eccentric part (30a-30c) of the 2nd stage center crankshaft 30 and each eccentric part of the 2nd stage guide crankshaft 31 so that the revolution operation | movement of the 2nd stage guide crankshaft 31 may be performed smoothly. The phase of (31a to 31c) is adjusted as appropriate.

  The second stage carrier 32 shown in FIGS. 1 and 2 includes a base carrier 34, an end carrier 35, and a column 36. The base carrier 34 is disposed in the case 11 with the output shaft 15 integrally formed at one end thereof. On the other hand, a center crank holding hole 46 and a guide crank holding hole 47 are formed on the other end side of the base carrier 34. The center crank holding hole 46 is provided at the center of the base carrier 34, and the guide crank holding hole 47 is provided at a position at an equal angle along the circumferential direction around the rotation center line P. The base carrier 34 holds the one end side of the second stage center crankshaft 30 through the tapered roller bearing 37 so as to be rotatable at the center crank holding hole 46, and the second stage guide crank at the guide crank holding hole 47. One end side of the shaft 31 is rotatably held via a tapered roller bearing 43.

  The end carrier 35 is connected to the base carrier 34 via a support column 36 and is provided as a disk-shaped member. A center crank holding hole 48 and a guide crank holding hole 49 are formed in the end carrier 35 as through holes. The center crank holding hole 48 is provided at the center of the end carrier 35, and the guide crank holding hole 49 is provided at a position at an equal angle along the circumferential direction around the rotation center line P. The end carrier 35 holds the other end side of the second stage center crankshaft 30 through the tapered roller bearing 38 so as to be rotatable at the center crank holding hole 48, and the second stage at the guide crank holding hole 49. The other end side of the guide crankshaft 31 is rotatably held via a tapered roller bearing 44. The positions on the other end side in the axial direction of the tapered roller bearing 38 and the tapered roller bearing 44 are respectively defined in a preload state by ring-shaped stopper members fitted in the center crank holding hole 48 and the guide crank holding hole 49, respectively. ing.

  The support column 36 is disposed between the base carrier 34 and the end carrier 35 and is provided as a columnar member that connects the base carrier 34 and the end carrier 35. A plurality of (for example, three) columns 36 are arranged at equal angular positions along the circumferential direction around the rotation center line P, and are arranged so that their axial directions are parallel to the rotation center line P. . In addition, the support | pillar 36 and the 2nd stage guide crankshaft 31 are alternately arrange | positioned along the circumferential direction centering on the rotation centerline P. As shown in FIG. Each column 36 is coupled to the base carrier 34 and the end carrier 35 via bolts (50, 51). The bolt 50 that joins the base carrier 34 and the column 36 is inserted into the base carrier 34 from one end side and screwed into the column 36. On the other hand, the bolt 51 that joins the end carrier 35 and the column 36 is inserted into the end carrier 35 from the other end side, and the column 36 is fitted in a recess formed on one end side of the end carrier 35. Screwed to the other end of the screw.

  A pair of main bearings 33 shown in FIGS. 1 and 2 includes a main bearing 33 a provided as a tapered roller bearing that rotatably holds the base carrier 34 with respect to the main body case 17, and an end carrier 35 attached to the main body case 17. A main bearing 33b provided as a tapered roller bearing that is rotatably held against the main bearing 33b. Accordingly, the pair of main bearings 33 hold the second stage carrier 32 so as to be rotatable with respect to the case 11. The main bearing 33 a is positioned in a pressurized state with one end engaged with the outer peripheral edge of the base carrier 34 and the other end engaged with the inner peripheral step of the main body case 17. On the other hand, the main bearing 33 b is positioned by engaging one end side with an inner peripheral step portion of the main body case 17 and engaging the other end side with an outer peripheral edge portion of the end carrier 35. Then, the base carrier 34 and the end carrier 35 are fastened by bolts (50, 51) via the support column 36, so that the case 11 is sandwiched between the base carrier 34 and the end carrier 35 via the pair of main bearings 33. The second stage carrier 32 is held rotatably with respect to the case 11.

  In the windmill drive device 1 described above, the reduction ratio of the first stage reduction unit 13 and the second stage reduction unit 14 are set so that the rotation speed of the first stage carrier 21 is in the range of 19 rpm to 65 rpm. The reduction ratio is set. Further, the reduction ratio of the second stage reduction unit 14 is set to be larger than the reduction ratio of the first stage reduction unit 13. Here, the rotational speed of the electric motor that inputs the driving force to the windmill driving device 1 is set in the range of 1000 rpm to 1800 rpm. And the sum of the reduction ratio which is the ratio of the rotational speed on the input side to the rotational speed on the output side in the wind turbine drive device 1 (that is, the reduction ratio of the first stage reduction part 13 and the reduction ratio of the second stage reduction part 14) Product) is set in the range of about 1000 to about 3000. The ratio of the reduction ratio of the first stage reduction unit 13 to the reduction ratio of the second stage reduction unit 14 (that is, the speed ratio of the first stage reduction unit 13 to the second stage reduction unit 14) is, for example, about 0. .8 to about 0.9. Based on these conditions, for each of the cases where the total reduction ratio is about 1000, about 2000, and about 3000, each combination when the speed ratio ratio is about 0.8 and about 0.9 If the reduction ratio of the first stage reduction unit 13 and the reduction ratio of the second stage reduction unit 14 are set so that, for example, the following can be set.

(When the total reduction ratio is about 1000)
By setting the reduction ratio of the first stage reduction unit 13 to 28 and setting the reduction ratio of the second stage reduction unit 14 to 35, the total reduction ratio becomes 980, and the first stage with respect to the second stage reduction unit 14 The speed ratio of the speed reduction unit 13 can be set to 0.8. In this case, when the rotation speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotation speed of the first stage carrier 21 is in the range of 35.7 rpm to 64.3 rpm. In addition, by setting the reduction ratio of the first stage reduction unit 13 to 30 and setting the reduction ratio of the second stage reduction unit 14 to 33, the total reduction ratio is set to 990, and the second reduction unit 14 has a second reduction ratio. The speed ratio of the first stage reduction unit 13 can be set to about 0.9. In this case, when the rotation speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotation speed of the first stage carrier 21 is in the range of 33.3 rpm to 60.0 rpm.

(When the total reduction ratio is about 2000)
By setting the reduction ratio of the first stage reduction unit 13 to 40 and setting the reduction ratio of the second stage reduction unit 14 to 50, the total reduction ratio becomes 2000, and the first stage with respect to the second stage reduction unit 14 The speed ratio of the speed reduction unit 13 can be set to 0.8. In this case, when the rotation speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotation speed of the first stage carrier 21 is in the range of 25.0 rpm to 45.0 rpm. In addition, by setting the reduction ratio of the first stage reduction unit 13 to 42 and setting the reduction ratio of the second stage reduction unit 14 to 48, the total reduction ratio is set to 2016, and the second reduction unit 14 has a second reduction ratio. The speed ratio of the first stage reduction unit 13 can be set to about 0.9. In this case, when the rotational speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotational speed of the first stage carrier 21 is in the range of 23.8 rpm to 42.9 rpm.

(When the total reduction ratio is about 3000)
By setting the reduction ratio of the first stage reduction unit 13 to 49 and setting the reduction ratio of the second stage reduction unit 14 to 61, the total reduction ratio becomes 2989, and the first stage with respect to the second stage reduction unit 14 The speed ratio of the speed reduction unit 13 can be set to about 0.8. In this case, when the rotation speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotation speed of the first stage carrier 21 is in the range of 20.4 rpm to 36.7 rpm. Further, by setting the reduction ratio of the first stage reduction unit 13 to 52 and setting the reduction ratio of the second stage reduction unit 14 to 58, the total reduction ratio is set to 3016, and the second reduction unit 14 has a second reduction ratio. The speed ratio of the first stage reduction unit 13 can be set to about 0.9. In this case, when the rotation speed of the electric motor is set from 1000 rpm to 1800 rpm, the magnitude of the rotation speed of the first stage carrier 21 is in the range of 19.2 rpm to 34.6 rpm.

  As illustrated above, when the reduction ratio of the first stage reduction unit 13 and the reduction ratio of the second stage reduction unit 14 are set, the reduction ratio of the second stage reduction unit 14 is greater than the reduction ratio of the first stage reduction unit 13. Is set to be larger, and the rotation speed of the first stage carrier 21 is set to be in a range of 19 rpm to 65 rpm.

  Next, the operation of the windmill drive device 1 described above will be described. The windmill drive device 1 operates when an electric motor (not shown) is operated. When the operation of the electric motor is started, the input shaft 12 and the first stage crank shaft 20 rotate together with the output shaft 100 of the electric motor. When the first stage crankshaft 20 rotates together with the eccentric part 24, a load is applied from the eccentric part 24 to the first stage external gear 19, and the first stage external gear 19 having a single configuration is connected to the first stage internal gear 18. It rotates eccentrically so as to swing while shifting the mesh. And the 1st stage carrier 21 rotates with the 1st stage external gear 29 via bush pin 21b.

  When the first stage carrier 21 rotates as described above, the second stage center crankshaft 30 rotates together. When the second stage center crankshaft 30 rotates together with the eccentric parts (30a to 30c), a load acts on the external gears (29a to 29c) of the second stage external gear 29 from the eccentric parts (30a to 30c). The three-stage second-stage external gear 29 rotates eccentrically so as to swing while shifting the mesh with the second-stage internal gear 28. Then, as the second stage external gear 29 rotates, each second stage guide crankshaft 31 performs a revolving operation while rotating. By the revolving operation of the second stage guide crankshaft 31, the one end side and the other end side of the second stage center crankshaft 30 and the second stage guide crankshaft 31 are rotatably held by the base carrier 34 and the end carrier 35. The second stage carrier 32 to be rotated rotates. Then, the output shaft 15 formed integrally with the base carrier 34 of the second stage carrier 32 held rotatably with respect to the case 11 via the pair of main bearings 33 rotates, and a large torque is generated by the pinion 101. Will be output.

  According to the windmill drive device 1 described above, the windmill drive device 1 is provided with external gears (19, 29) that rotate eccentrically in the first-stage reduction unit 13 and the second-stage reduction unit 14, respectively. It is configured as a stage-type eccentric speed reducer. For this reason, a large reduction ratio can be ensured and the output torque can be improved. And since it is comprised as an eccentric type reduction gear of 2 steps | paragraphs, a big reduction ratio is realizable with a small structure. Further, in the wind turbine driving device 1, the base carrier 34 in the second stage carrier 32 of the second stage reduction unit 14 is formed integrally with the output shaft 15 to which the output pinion 101 is coupled, and the second stage carrier 32 is formed. The case 11 is held by a pair of main bearings 33. For this reason, since it is used for a windmill, even when the driving force output from the output shaft 15 increases and a large torque acts on the output shaft 15 from the pinion 101 as a reaction, it is formed integrally with the base carrier 34. The output shaft 15 thus held is held by the pair of main bearings 33 together with the second stage carrier 32. As a result, even if a large torque acts as a reaction from the pinion 101, the inclination of the output shaft 15 and the second stage carrier 32 is reduced, and the deviation between the second stage internal gear 28 and the second stage external gear 29 is reduced. It is suppressed that the hit occurs. For this reason, a decrease in durability of the second-stage external gear 29 is suppressed, and a decrease in durability as the second-stage reduction gear unit 14 is also suppressed.

  Therefore, according to the present embodiment, it is possible to provide the wind turbine drive device 1 that can improve the output torque and reduce the size, and can also suppress a decrease in durability in the speed reduction portion.

  Further, according to the wind turbine driving device 1, since the load is low in the first stage external gear 19, the sliding between the first stage external gear 19 and the first stage internal tooth 18 is possible even if the bush pin 21 b is used. A decrease in driving efficiency of the first speed reduction unit 13 due to friction loss due to movement is suppressed. Since the first stage external gear 19 is configured as one sheet, the cost can be reduced by reducing the number of the first stage external gear 19 and the cylindrical roller bearing 26. Further, in the wind turbine driving device 1, the second stage guide crankshaft 31 that transmits the rotation of the second stage external gear 29 to the second stage carrier 32, although the load is increased in the second stage reduction unit 14, By being held by the base carrier 34 and the end carrier 35 via the bearings (43, 44), it is possible to suppress a decrease in the driving efficiency of the entire second stage reduction unit 14. Further, since the second stage external gear 29 is composed of three pieces, the second stage reduction unit 14 is maintained while maintaining the surface pressure between the second stage external gear 29 and the second stage internal teeth 28. Can be reduced in diameter. Therefore, according to the wind turbine driving device 1, it is possible to reduce the size and the diameter without reducing the driving efficiency.

  Moreover, according to the windmill drive device 1, the reduction ratio of the first stage reduction unit 13 and the second stage reduction unit 14 is set so that the rotation speed of the first stage carrier 21 is 19 rpm or more and 65 rpm or less. Has been. For this reason, the first stage carrier 21 is rotated in the range of the rotational speed at which the driving efficiency is extremely good in the first stage reduction part 13 where the driving efficiency is lower than that of the second stage reduction part 14. Can do. Thereby, the fall of drive efficiency can further be suppressed. As a result of verification by the inventors of the present invention regarding the magnitude of the rotation speed of the first stage carrier 21, it was confirmed that the drive efficiency rapidly deteriorates because the speed approaches the boundary lubrication region at less than 19 rpm. Moreover, when it exceeded 65 rpm, it became a fluid lubrication area | region, and it has confirmed that the fixed loss of the stirring resistance and frictional resistance accompanying a rotational speed increase became large, and efficiency deteriorated.

  Further, according to the wind turbine driving device 1, the second stage reduction unit 14 is set to have a larger reduction ratio than the first stage reduction unit 13. For this reason, in the 1st stage reduction part 13 in which drive efficiency becomes low compared with the 2nd stage reduction part 14, the reduction ratio will be set small, and the drive efficiency as a whole can further be improved.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made as long as they are described in the claims. For example, the support column connecting the base carrier and the end carrier may be formed integrally with the base carrier. Further, the number of crankshafts and struts may be different from that illustrated in the present embodiment. Moreover, about the kind of each bearing, you may change suitably and may implement. Further, the configuration of the coupling position in the case may be changed as appropriate.

  The present invention can be widely applied as a windmill drive device that is provided in a windmill and used as a drive device that drives equipment in the windmill.

It is sectional drawing which shows the drive device for windmills which concerns on one embodiment of this invention. It is sectional drawing which expands and shows the 1st step reduction part and 2nd step reduction part in the drive device for windmills shown in FIG. 1, and its vicinity.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Windmill drive device 11 Case 13 1st stage reduction part 14 2nd stage reduction part 15 Output shaft 18 1st stage internal gear 19 1st stage external gear 20 1st stage crankshaft 21 1st stage carrier 21b Bush pin 28 Second stage internal teeth 29, 29a, 29b, 29c Second stage external gear 30 Second stage center crankshaft 31 Second stage guide crankshaft 32 Second stage carrier 33 Pair of main bearings 34 Base carrier 35 End carrier 101 Pinion

Claims (4)

A windmill drive device that is provided in a windmill and is used as a drive device that drives equipment in the windmill,
A case, a first-stage reduction part that is a first-stage reduction part that is housed in the case and receives driving force from an electric motor, and a drive that is housed in the case and that is driven from the first-stage reduction part A second-stage reduction part that is a second-stage reduction part to which force is input, and an output shaft fixed to the second-stage reduction part,
The first-stage reduction gear includes a first-stage internal gear provided on the inner periphery of the case, a first-stage external gear provided on the outer periphery with external teeth meshing with the first-stage internal teeth, and a radial direction. A first-stage crankshaft that is arranged at the center of the first-stage external gear and rotates the first-stage external gear eccentrically, and a bush pin that passes through a hole formed in the first-stage external gear in a loosely fitted state. A first stage carrier,
The second-stage reduction gear includes a second-stage internal gear provided on the inner periphery of the case, a second-stage external gear provided on the outer periphery with external teeth meshing with the second-stage internal teeth, and a radial direction. And a second stage center crankshaft that is fixed to the first stage carrier and eccentrically rotates the second stage external gear, and circumferentially around the second stage center crankshaft. A plurality of second-stage guide crankshafts arranged along the second-stage external gear, and one end side of each of the second-stage center crankshaft and the second-stage guide crankshaft. A second stage carrier having a base carrier rotatably held via a bearing and an end carrier holding each other end rotatably via a bearing, and the second stage carrier rotated with respect to the case A pair of main bearings to be freely held, And,
The wind turbine drive device, wherein the output shaft is integrally formed with the base carrier, and an output pinion is coupled to the output shaft. The windmill drive device according to claim 1,
The wind turbine driving device according to claim 1, wherein the first stage external gear is provided as one external gear, and the second stage external gear is provided as three external gears. The windmill drive device according to claim 1 or 2,
The reduction ratio of the first stage reduction part and the reduction ratio of the second stage reduction part are set so that the rotation speed of the first stage carrier is in the range of 19 rpm to 65 rpm. A windmill drive device characterized by the above. It is a drive device for windmills of Claim 3, Comprising:
The wind turbine driving device according to claim 1, wherein a reduction ratio of the second stage reduction unit is larger than a reduction ratio of the first stage reduction unit.

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