WO2008041687A1 - Engrenage réducteur différentiel de type oscillant - Google Patents

Engrenage réducteur différentiel de type oscillant Download PDF

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Publication number
WO2008041687A1
WO2008041687A1 PCT/JP2007/069236 JP2007069236W WO2008041687A1 WO 2008041687 A1 WO2008041687 A1 WO 2008041687A1 JP 2007069236 W JP2007069236 W JP 2007069236W WO 2008041687 A1 WO2008041687 A1 WO 2008041687A1
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WO
WIPO (PCT)
Prior art keywords
gear
input shaft
motor
output shaft
disposed
Prior art date
Application number
PCT/JP2007/069236
Other languages
English (en)
Japanese (ja)
Inventor
Katsuhiko Yokoyama
Original Assignee
Nabtesco Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nabtesco Corporation filed Critical Nabtesco Corporation
Publication of WO2008041687A1 publication Critical patent/WO2008041687A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type

Definitions

  • the present invention relates to a differential rocking reducer used in a drive device, a pitch drive device, and the like.
  • a jaw drive device for driving the nacelle in any turning direction
  • a pitch drive device for changing the direction of a blade
  • the reduction gear used in the driving device or the like has a motor 101, a reduction gear main body 102, a cylindrical portion 103, and a pinion 104 coaxially disposed as shown in FIG. 7, for example.
  • a reduction mechanism (not shown) is disposed in the reduction gear main body 102, and the reduction mechanism is connected to the pinion 104 through the cylindrical portion 103.
  • the speed reducer is constructed so that the tubular portion 103 is positioned between a pair of fixed frames 107 and 108 disposed at a distance from each other.
  • Patent Document 1 Japanese Patent Application Publication No. 2001-289149
  • Patent Document 2 Japanese Patent Publication No. 8-16474
  • the reduction gear main body 102 and the motor 101 are disposed above the fixed frame 107 on the upper side of the drawing, the reduction gear is axially long and the internal equipment 110 in the device 110 And interfere. Therefore, it is conceivable to arrange the speed reduction mechanism and the motor 101 at right angles.
  • a worm gear is used to connect the speed reduction mechanism and the motor 101 in direct communication with each other. This is a car that reduces the reduction gear with a reduction gear in the reduction mechanism and reduces the size of the reduction gear because the reduction gear is used for reduction.
  • An object of the present invention is to provide a differential rocking reducer that solves the above problems.
  • Another object of the present invention is to provide a driving device which can be disposed on an axially short space which is not broken even if an excessive wind acts.
  • a differential rocking reducer comprising: a cylindrical body having a large number of pin teeth disposed inside; and a lid configured to be connectable to an end of the body.
  • An input shaft portion rotatably supported by the lid and having an input shaft gear, and an input shaft portion interlocked with a motor, a driven gear portion interlocked with the input shaft gear, and rotation interlocked with the driven gear portion Crank shaft, a plurality of eccentric portions provided on the crank shaft, and a plurality of rotary members provided corresponding to the plurality of eccentric portions and rotating while interlocking with the corresponding eccentric portions while meshing with the pin teeth
  • a differential rocking reducer comprising: an external gear member; and an output shaft gear, wherein the output shaft portion rotates in conjunction with the external gear member, the drive shaft of the motor.
  • Has a drive side bevel gear and the input shaft portion is engaged with the drive side bevel gear It has a driven bevel gear, wherein the drive shaft of the motor and the output shaft portion, a positional
  • the drive shaft of the motor is in a positional relationship in which the drive shaft of the motor is bent relative to the output shaft portion, so the motor length in the extension line direction of the output shaft portion (or The width S can be shortened.
  • the reduction gear can be applied even when there is no space in the axial direction.
  • the bevel gear is used, even if an excessive force is applied to the output shaft in the direction opposite to the driving direction by the motor, it is possible to adapt to the force. That is, when a worm gear is used, when a reverse force is applied to the output shaft, the worm gear having a high reduction ratio may be damaged without being reversed.
  • the bevel gear when used, the bevel gear does not break because it rotates in the opposite direction when it receives an excessive force S in the opposite direction. Therefore, the reduction gear can be suitably used for a wind power generator in which a reverse force may act on the reduction gear rapidly or in a pitch drive.
  • a differential rocking reducer comprising: a cylindrical body having a large number of pin teeth disposed inside; and a lid configured to be connectable to an end of the body.
  • An input shaft portion rotatably supported by the lid and interlocked with a motor; and an input shaft provided on the input shaft portion A gear, a driven gear portion interlocking with the input shaft gear, a crankshaft rotating in interlock with the driven gear portion, a plurality of eccentric portions provided on the crankshaft, and the plurality of eccentric portions
  • It has a plurality of external gear members, which are provided, and rotate while interlocking with the corresponding eccentric parts while engaging with the pin teeth, and an output shaft gear, and is interlocked with the external gear members and rotates around the shaft.
  • a differential rocking reducer comprising a rotating output shaft, wherein the body has a flange for fixing to a fixed body, and the crankshaft, the pin teeth and the external gear member are: It is disposed between the flange in the axial direction of the output shaft portion and the output shaft gear.
  • FIG. 1 is a perspective view of a wind turbine generator to which a first embodiment of a differential rocking reducer according to the present invention is applied.
  • FIG. 2 is a cross-sectional view of a first embodiment of a differential rocking reducer according to the present invention.
  • FIG. 3 is a cross-sectional view taken along line III-III in FIG.
  • FIG. 4 is a cross-sectional view of a second embodiment of a differential rocking reducer according to the present invention.
  • FIG. 5 is a cross-sectional view of a third embodiment of the differential rocking reducer according to the present invention.
  • FIG. 6 is a side view showing a motor body, a fan and a fan case.
  • FIG. 7 is a cross-sectional view of a conventional differential rocking reducer.
  • FIG. 1 shows a wind turbine generator to which an embodiment of a differential rocking reducer according to the present invention is applied. Part 1 is shown partially.
  • the wind turbine generator 1 includes a support 2 erected on the ground, and a nacelle 3 provided at an upper end of the support 2.
  • the nacelle 3 houses a gearbox, a generator and the like not shown. Further, the nacelle 3 is provided with a rotor connected to the gear box, and the hub 5 of this rotor is provided with a blade 6.
  • a differential rocking reducer (hereinafter simply referred to as a reducer) 10 is applied to a Y-drive device for turning the nacelle 3.
  • the reduction gear 10 includes an outer case 12.
  • the outer case 12 includes a body 13 formed in a cylindrical shape and a lid 14 coupled to one end of the body 13.
  • a flange 13a for fixing to a fixing frame 16 as an example of a fixing body is provided at one end of the body portion 13.
  • the flange 13a is provided with a bolt hole, and the body 13 is fixed to the fixed frame 16 by screwing the bolt 18 inserted through the bolt hole into the fixing frame 16. .
  • the other end of the body 13 is slightly thinner, and this end is inserted into the through hole of the fixed frame 19 fixed in the nacelle 3.
  • the fixed frame 19 and the fixed frame 16 are provided in the nacelle 3 at a predetermined interval, and the speed reducer 10 is supported by both fixed frames 16 and 19.
  • the lid 14 is coupled to the body 13 so as to close the opening at one end of the body 13.
  • the lid 14 has a cylindrical main body 21 extending in parallel to the axial direction of the body 13, a flange 22 provided at one end of the main body 21, and an intermediate portion in the axial direction of the main body 21. And a branch portion 23 extending in a direction orthogonal to the axial direction of the 13.
  • the collar portion 22 is formed so as to cover the end opening of the body portion 13 and is configured to be able to be fastened to the end portion of the body portion 13. Further, the flange portion 22 is provided with an extending portion 25 extending from the end of the body 13 to the other end along the body 13. The extension 25 is located inside the body 13 and a ring gear 26 is provided at the tip of the extension 25. That is, the ring gear 26 is disposed within the range between both ends of the body 13 and inside the body 13. In the first embodiment, the ring gear 26 is located in the vicinity of the flange 13 a in the axial direction of the body portion 13.
  • a bearing portion 27 is provided in the main body portion 21 of the lid 14, and the input shaft portion is mounted on the bearing portion 27. 30 are rotatably supported.
  • the input shaft portion 30 is disposed on the central axis of the body portion 13.
  • the driven bevel gear 31 is provided at one end (upper end in FIG. 2) of the input shaft 30, and the other end (lower end in FIG. 2) of the input shaft 30 is provided.
  • An input shaft gear 32 with external teeth is provided!
  • a motor 35 is fixed to the branch 23 of the lid 14.
  • the motor 35 includes a motor body 35a and a drive shaft 35b extended from the motor body 35a.
  • the motor 35 is disposed in a posture in which the motor body 35a has a long and narrow shape in the direction orthogonal to the axial direction of the body portion 13. In other words, the motor 35 is disposed in parallel to the fixed frame 16.
  • the drive shaft 35 b of the motor 35 and the input shaft portion 30 have an arrangement relationship in which the extension lines thereof are orthogonal to each other.
  • the motor 35 is provided with a fan case 38 on the opposite side to the drive shaft 35b with respect to the motor main body 35a.
  • the drive shaft 35 b of the motor 35 passes through the inside of the branch 23 of the lid 14 and is rotatably supported by the branch 23.
  • a drive bevel gear 39 is provided at the tip of the drive shaft 35b of the motor 35.
  • the drive bevel gear 39 and the driven bevel gear 31 are engaged with each other inside the main body 21 of the lid.
  • the reduction gear 10 includes the input shaft portion 30, a reduction mechanism at a front stage, a reduction mechanism at a rear stage, and a carrier 41 as an example of an output shaft portion.
  • the reduction gear 10 can be disposed, for example, such that the input shaft 30 is at the top and the carrier 41 is at the bottom, as shown in FIG. In this case, the carrier 41 is rotated about the vertical axis.
  • the explanation will be continued assuming that it is arranged in this posture.
  • the front stage reduction mechanism is a mechanism for reducing the number of revolutions of the motor 35 at a predetermined ratio.
  • the pre-deceleration mechanism is included in the concept of the driven gear portion in the present invention.
  • the second stage reduction mechanism is a mechanism for further decelerating the rotational speed decelerated by the first stage reduction mechanism at a predetermined ratio and transmitting it to the carrier 41.
  • the front stage reduction mechanism includes the input shaft gear 32, the ring gear 26, a planetary gear 42, an intermediate shaft portion 43, and a next stage planetary gear 44.
  • the planetary gear 42 is in mesh with the input shaft gear 32 and the ring gear 26, and the planetary gear 42 revolves around the input shaft portion 30 as the input shaft portion 30 rotates.
  • the intermediate shaft portion 43 includes an intermediate shaft portion main body 43a coaxially arranged with the input shaft portion 30, an arm portion 43b extending radially outward from the intermediate shaft portion main body 43a, and an intermediate shaft portion main body 43a. And a drive external gear 43c provided on the lower part of the vehicle.
  • the intermediate shaft portion main body 43a is disposed immediately below the input shaft portion 30, and is rotatably supported by an end plate portion 52 described later.
  • the tip of the arm 43 b is inserted into a through hole provided at the center of the planetary gear 42. Then, when the planetary gear 42 revolves, the arm 43b also revolves accordingly, and the intermediate shaft main body 43a rotates at a rotational speed reduced at a predetermined ratio to the rotational speed of the input shaft 30. It will As a result, the next stage planetary gear 44 with which the driving external gear 43c is engaged is rotated.
  • the rear stage reduction mechanism includes a crankshaft 46, eccentric portions 47a and 47b, pin teeth 48, and external gear members (first external gear member 49a and second external gear member 49b).
  • a large number of pin teeth 48 are provided, and these pin teeth 48 are disposed on the inner circumferential portion at the axially intermediate portion of the body portion 13 over the entire circumferential direction.
  • the pin teeth 48 are arranged in axially extending postures and are equally spaced. Each pin tooth 48 constitutes an internal tooth of an internal gear.
  • the carrier 41 is disposed radially inward of the body portion 13, and the carrier 41 is disposed rotatably about the same axis as the axis of the input shaft portion 30.
  • the carrier 41 is rotatably supported by the body 13 by bearings provided at two locations in the axial direction.
  • the carrier 41 rotates around an axis that coincides with the axial center of the body 13.
  • Carrier 41 includes base 51, end plate 52 disposed above base 51, and shaft 53 integrally formed on base 51 so as to extend toward end plate 52. ing.
  • the lower end portion of the base 51 is configured to project downward from the body 13, and the lower end portion of the base 51 is provided with an output shaft gear 55 so as to be coaxial with the axis of the body 13. Is fitted around.
  • the output shaft gear 55 applies a rotational driving force to the pivot shaft of the nacelle 3.
  • the shaft portion 53 is formed in a columnar shape extending in the upward direction from the upper surface of the base portion 51 in the axial direction. Further, as shown in FIG. 3, three shaft portions 53 are provided at intervals in the circumferential direction, and each shaft portion 53 is formed in a substantially triangular shape in cross section.
  • the shaft portion 53 is provided with a bottomed bolt hole, and the end plate portion 52 is provided. There are bolt through holes at positions corresponding to the bolt holes. Then, a bolt 57 which is threaded through the boreto hole is screwed into the bolt hole of the shaft portion 53.
  • the base 51 and the end plate 52 are fixed so as not to be misaligned with each other.
  • the base portion 51 and the end plate portion 52 integrally rotate around the axial center of the body portion 13.
  • a closed space is formed between the base 51 and the end plate 52 on the inside of the body 13.
  • the first external gear member 49a and the second external gear member 49b are disposed in the closed space.
  • the first and second external gear members 49a and 49b have the same shape and the same outer diameter.
  • the first and second external gear members 49a, 49b are formed to be slightly smaller than the inner diameter of the body portion 13 and have external teeth 58 (see FIG. 3) that engage with the pin teeth 48 of the body portion 13.
  • the number of external teeth 58 of the first and second external gear members 49a, 49b is slightly less than the number of pin teeth 48, for example, by one!
  • the crankshaft 46 penetrates the first and second external gear members 49a and 49b.
  • crankshafts 46 are provided at intervals in the circumferential direction (see Fig. 3). Each crankshaft 46 is rotatably supported by a pair of upper and lower crank bearings 60, 60 as shown in FIG.
  • the upper crank bearing 60 is fitted in a through hole formed in the end plate 52.
  • the lower crank bearing 60 is fitted in a recess formed in the upper surface of the base 51.
  • next-stage planetary gears 44 are respectively provided. These next-stage planetary gears 44 are engaged with the drive external gear 43c.
  • the crankshaft 46 is decelerated at a gear ratio between the driving external gear 43 c and the next stage planetary gear 44 to rotate and revolve integrally with the next stage planetary gear 44.
  • the eccentric portions 47 a and 47 b are provided two each on each crankshaft 46. These eccentric parts 47a and 47b are disposed along the axial direction, and form a first eccentric part 47a and a second eccentric part 47b in order from the bottom of FIG.
  • the first and second eccentric portions 47a and 47b are formed in a cylindrical shape eccentric with respect to the axial center of the crankshaft 46 by the same amount of eccentricity.
  • the first and second eccentric portions 47a and 47b have substantially the same outer diameter. Also, they have a phase difference of 180 degrees with each other.
  • the first external gear member 49a and the second external gear member 49b are externally fitted to the first eccentric portion 47a and the second eccentric portion 47b, respectively.
  • the first eccentric part 47a and the second eccentric part 47b have the same configuration except that they are out of phase.
  • a first through hole 62 and a second through hole 63 are provided in the first external gear member 49a. Since the first through holes 62 are provided corresponding to the crankshaft 46, three first through holes 62 are provided at equal intervals in the circumferential direction. Each first through hole 62 is formed in a circular shape, and a first eccentric portion 47a is inserted through each of the first through holes 62 in a state in which a bearing is interposed. Similarly, a second eccentric portion 47b is threaded through the first through hole 62 of the second external gear member 49b with a bearing interposed.
  • the shaft portion 53 is passed through the second through holes 63 of the first and second external gear members 49a, 49b.
  • the second through hole 63 is formed in a substantially triangular shape larger than the cross section of the shaft portion 53 so that a predetermined gap with the shaft portion 53 is formed. Since the second through holes 63 are provided corresponding to the shaft portion 53, three second through holes 63 are provided at equal intervals in the circumferential direction.
  • the revolution of the first and second external gear members 49 a, 49 b is significantly reduced relative to the revolution of the crankshaft 46. Then, along with the revolution of the first and second external gear members 49a and 49b, the shaft portion 53 revolves and the entire carrier 41 rotates. As a result, the output shaft gear 55 rotates at a rotational speed significantly reduced with respect to the rotational speed of the motor 35.
  • the drive shaft 35 b of the motor 35 is a circuit of the carrier 41. Since the arrangement relationship is bent with respect to the rotation shaft, the length (or the width of the motor) of the motor 35 in the rotation axis direction of the carrier 41 can be shortened. As a result, the reduction gear 10 can be installed even in a driving device where there is no space in the axial direction of the body portion 13. Moreover, since the bevel gears 39 and 31 are used, even if the output shaft gear 55 is subjected to an excessive force S in the opposite direction to the driving direction by the motor 35, it is possible to adapt to that force. It becomes.
  • the input shaft portion 30 is configured to enter the inside of the body portion 13. You can As a result, the axial length of the speed reducer 10 can be shortened.
  • FIG. 4 shows a second embodiment of the present invention.
  • the motor 35 is disposed such that the drive shaft 35b of the motor 35 is orthogonal to the rotation shaft of the carrier 41.
  • the drive shaft 35b of the motor 35 is The drive shaft 35 b is disposed so as to enter the inside of the body 13 while the drive shaft 35 b is disposed parallel to the rotation axis of the carrier 41.
  • Specific description will be made below.
  • the same components as in Embodiment 1 will be assigned the same reference numerals and detailed explanations thereof will be omitted.
  • the lid 14 has a cylindrical main body 21 extending parallel to the axial direction of the body 13, a flange 22 provided on one end (upper end) of the main body 21, and the other parts of the main body 21. And a bearing 27 provided at the end (lower end).
  • the collar portion 22 is formed at the upper end portion of the main body portion 21.
  • the collar portion 22 is in axial contact with one end portion (upper end portion) of the trunk portion 13.
  • the main body 21 is disposed along the inner surface of the body 13 from the upper end to the other end (lower end) of the body 13.
  • the bearing 27 extends from the lower end of the main body 21 toward the axial center so as to close the space between the main bodies 21.
  • a through hole is formed at the inner end of the bearing 27.
  • the bearing 27 is located below the upper end of the body 13. Therefore, the motor 35 is extended to the inside of the body 13 It is possible to get in!
  • the cover 14 has a mounting portion 67 for fixing the motor 35.
  • the mounting portion 67 is configured separately from the collar portion 22 and is fastened to the trunk portion 13 together with the collar portion 22.
  • the mounting portion 67 is configured to project from the end of the body 13 to the inside of the body.
  • the motor 35 is disposed in a state in which the drive shaft 35 b enters the inside of the body portion 13 and is fixed to the mounting portion 67. Thereby, the axial length of the reduction gear 10 can be shortened.
  • the input shaft portion 30 is formed in a tubular shape having substantially the same length as the drive shaft 35b, and the input shaft portion 30 is externally fitted to the drive shaft 35b.
  • the input shaft portion 30 is configured to rotate integrally with the drive shaft 35b.
  • the axial length of the reduction gear 10 is longer than in the configuration in which the drive shaft 35b and the input shaft portion 30 are axially connected to each other. Can be shortened.
  • the input shaft portion 30 is inserted into the through hole of the bearing portion 27 and rotatably supported by the bearing portion 27.
  • the lid 14 is provided with an extension 25 extending along the trunk 13 from the other end of the main body 21.
  • the ring gear 26 is fixed to the lower end of the extension 25.
  • the position of the ring gear 26 is the same height as the input shaft gear 32 provided at the lower end of the input shaft portion 30. In other words, the ring gear 26 penetrates the inside of the body 13.
  • the crankshaft 46, the pin teeth 48 and the external gear member 49a, 49b are disposed between the flange 13a and the output shaft gear 55 in the rotation axis direction. . Therefore, the body portion 13 can be installed between the two fixed frames 16 and 19 so that the crankshaft 46, the pin teeth 48 and the external gear members 49a and 49b can be accommodated. Therefore, the space between fixed frames 16 and 19 can be used effectively. Also, since the worm gear is not used, even if an excessive force S may be applied to the output shaft gear 55 in the direction opposite to the driving direction by the motor 35, the force can be adapted to that force.
  • the input shaft portion 30 for driving the speed reduction mechanism of the front stage is configured to enter the inside of the body portion 13. be able to.
  • the axial length of the reduction gear 10 can be made shorter than that of the conventional reduction gear.
  • the motor body 35a of the motor 35 is intruding inside the body 13
  • the axial length of the speed reducer 10 is reduced by that amount.
  • the lid 14 to which the ring gear 26 is fixed is attached to the end of the body 13 when the reduction gear 10 is assembled.
  • the ring gear 26 can be disposed inside the body 13 by being coupled to Therefore, the work of assembling the ring gear 26 to the inside of the body can be performed easily.
  • the ring gear 26 is disposed in the vicinity of the inner surface of the body portion 13, the number of teeth of the ring gear 26 can be increased. This makes it possible to increase the reduction ratio of the ring gear 26 and the planetary gear 42 while maximizing the space inside the barrel.
  • FIG. 5 shows a third embodiment of the present invention.
  • the configuration in which the motor 35 is mounted on the mounting portion 67 and the input shaft portion 30 is supported by the bearing portion 27 of the lid 14 has been described, but in the third embodiment, The bearing 27 of the lid 14 is omitted.
  • the shape of the mounting portion 67 for supporting the motor 35 is different from that of the second embodiment. Specific description will be made below.
  • the same components as in Embodiment 2 will be assigned the same reference numerals and detailed explanations thereof will be omitted.
  • the lid 14 includes an attachment portion 67 for supporting the motor 35, a support portion 70 for supporting the attachment portion 67, and a flange 22 for fastening to the body portion 13.
  • the support 70 is located in the vicinity of the flange 13 a of the body 13.
  • the extension portion 25 is extended downward from the support portion 70, and a ring gear 26 is provided at the lower end portion of the extension portion 25.
  • the attachment portion 67 is formed in a flat plate shape, and is integrally formed at an end portion of the motor main body 35a.
  • the drive shaft 35b of the motor 35 enters the inside of the body 13 and is located below the flange 13a of the body 13.
  • the fan case 38 is configured to be separable and removable. Specifically, as shown in FIG. 6, the fan case 38 has a top portion 38a and a side wall portion 38b cylindrically extending from the top portion 38a, and the side wall portion 38b is a part of the circumferential direction Minutes It is configured to be removable. That is, the side wall portion 38b includes a side wall portion main body 38c integrally formed with the top portion 38a, and a side wall portion subportion 38d separately formed from the side wall portion main body 38c. The side wall main body 38 c and the side wall sub-portion 38 d are each formed in an arc shape.
  • the side wall main body 38c constitutes a part of the side wall 38b in the circumferential direction
  • the side wall sub-portion 38d constitutes a remaining part of the side wall 38b in the circumferential direction.
  • the side wall main body 38c and the side wall subportion 38d are configured to be attachable to the outer peripheral surface of the motor main body 35a from the outside, and are fastened to the motor main body 35a by bolts, for example.
  • the side wall main body 38c and the side wall subportion 38d respectively constitute half of the side wall 38b in the circumferential direction. Therefore, the side wall main body 38c and the side wall subportion 38d can be removed from the motor main body 35a by moving in the direction orthogonal to the drive shaft 35b. Therefore, even if there is not enough space above the fan case 38, that is, on the opposite side of the motor 35, it is possible to prevent the removal of the fan case 38 from being complicated.
  • the side wall portion 38 b is not limited to the structure separated into two. Sidewall 38b is configured to be separable into three or more!
  • the third embodiment it is possible to remove only the necessary members of the components of the fan case 38 or to remove the respective members in order. For this reason, even when there is no space in the space around the fan case 38, for example, it is possible to suppress that the operation at the time of maintenance of the fan becomes complicated.
  • the driven gear portion includes a ring gear disposed inside the body portion, and a planetary gear that revolves around the input shaft portion while being engaged with the ring gear and the input shaft gear. It is preferable to have.
  • the input shaft portion for driving the driven gear portion may be configured to enter the inside of the body. it can. As a result, the axial length of the differential rocking reducer can be shortened.
  • the driven gear portion includes a ring gear disposed inside the body portion, and a planetary gear that revolves around the input shaft portion while meshing with the ring gear and the input shaft gear. It is preferable to have.
  • the input shaft portion for driving the driven gear portion can be configured to intrude inside the barrel.
  • the axial length of the differential rocking reducer can be made shorter than that of the conventional reducer.
  • the lid includes an extension having a form extending from one end to the other end of the trunk when the lid is connected to the trunk, and the extension is attached to the extension.
  • the ring gear is fixed.
  • the ring gear can be arranged on the inner side of the trunk by connecting the lid to which the ring gear is fixed to the end of the trunk. Therefore, it is possible to force the ring gear to the inside of the body with ease.
  • the ring gear be disposed close to the inner surface of the barrel.
  • the force S can be obtained by increasing the reduction ratio of the ring gear and the planetary gear while making maximum use of the space inside the body.
  • the fan case is configured by a plurality of members and each member is configured to be separately removable.
  • each member is configured to be separately removable.
  • the differential rocking reducer according to the present embodiment, it can be disposed in a space short in the axial direction which can not be damaged even if an excessive wind acts.

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Abstract

L'invention concerne un engrenage réducteur différentiel de type oscillant ayant une section corps avec une longueur axiale réduite. L'engrenage réducteur différentiel de type oscillant présente une partie corps (13) à l'intérieur de laquelle un grand nombre de dents - broches (48) sont disposés, une partie de l'arbre d'entrée (30) ayant un engrenage d'arbre d'entrée (32), un vilebrequin (46) en association fonctionnelle avec l'engrenage d'arbre d'entrée(32), des sections excentriques (47a, 47b) disposées sur le vilebrequin (46), des éléments d'engrenage dentés à l'extérieur (49a, 49b) disposés de façon à correspondre aux section excentriques (47a, 47b) et tournant tout en engrenant avec les dents - broches (48), et un support (41) ayant un engrenage d'arbre de sortie (55) et tournant autour de son axe en association fonctionnelle avec les éléments d'engrenage dentés à l'extérieur (49a, 49b). Un arbre de transmission (35b) d'un moteur (35) présente un engrenage conique côté entraînement (39), et une partie d'arbre d'entrée (30) présente un engrenage conique côté entraîné (31) s'engrenant avec l'engrenage conique côté entraînement (39). L'arbre de transmission (35b) du moteur (35) et le support (41) sont disposés de telle façon que des lignes de prolongement partant de là se croisent les unes avec les autres.
PCT/JP2007/069236 2006-10-04 2007-10-02 Engrenage réducteur différentiel de type oscillant WO2008041687A1 (fr)

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JP2006273041A JP5069892B2 (ja) 2006-10-04 2006-10-04 差動揺動型減速機
JP2006-273041 2006-10-04

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EP2172673A1 (fr) * 2008-10-02 2010-04-07 Gamesa Innovation & Technology, S.L. Unité d'embrayage comportant une ou plusieurs étapes planétaires
WO2010038380A1 (fr) * 2008-10-03 2010-04-08 ナブテスコ株式会社 Dispositif de commande de pas pour une roue éolienne
JP2012031827A (ja) * 2010-08-02 2012-02-16 Sumitomo Heavy Ind Ltd 風力発電設備の減速装置
WO2011128291A3 (fr) * 2010-04-12 2012-03-22 Wobben, Aloys Commande d'azimut ou commande de pas variable pour éolienne
US8482435B2 (en) 2006-02-16 2013-07-09 Aloys Wobben Wind turbine comprising approach lighting
CN107989976A (zh) * 2017-11-28 2018-05-04 西安航天精密机电研究所 一种具有换向功能的rv减速器
CN109333339A (zh) * 2018-10-17 2019-02-15 福州大学 一种轮毂数控抛光机及其工作方法
CN109707829A (zh) * 2014-05-09 2019-05-03 纳博特斯克有限公司 轴向变换齿轮装置
CN111828550A (zh) * 2019-04-15 2020-10-27 纳博特斯克有限公司 减速器和机器人

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JP5088963B2 (ja) * 2008-07-14 2012-12-05 ナブテスコ株式会社 ナセル旋回機構
JP5477044B2 (ja) * 2009-06-30 2014-04-23 株式会社ジェイテクト 遊星歯車機構
KR101168724B1 (ko) * 2010-04-19 2012-07-30 주식회사 해성산전 풍력발전기 타워 회전용 싸이클로이드 감속기
JP5425700B2 (ja) * 2010-04-30 2014-02-26 住友重機械工業株式会社 風力発電設備の減速装置及びその据え付け方法
CN102235326B (zh) * 2010-04-30 2013-12-25 住友重机械工业株式会社 动力传递装置及动力传递装置的联轴器单元
JP2012251595A (ja) * 2011-06-02 2012-12-20 Sumitomo Heavy Ind Ltd 風力発電設備の減速装置
JP6088395B2 (ja) * 2013-10-10 2017-03-01 住友重機械工業株式会社 減速装置のシリーズ
EP3584468B1 (fr) * 2018-06-20 2020-11-04 Heidrive GmbH Système modulaire destiné à la fabrication de systèmes de servomoteur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8482435B2 (en) 2006-02-16 2013-07-09 Aloys Wobben Wind turbine comprising approach lighting
EP2172673A1 (fr) * 2008-10-02 2010-04-07 Gamesa Innovation & Technology, S.L. Unité d'embrayage comportant une ou plusieurs étapes planétaires
WO2010038380A1 (fr) * 2008-10-03 2010-04-08 ナブテスコ株式会社 Dispositif de commande de pas pour une roue éolienne
EP2330297A1 (fr) * 2008-10-03 2011-06-08 Nabtesco Corporation Dispositif de commande de pas pour une roue éolienne
EP2330297A4 (fr) * 2008-10-03 2012-03-28 Nabtesco Corp Dispositif de commande de pas pour une roue éolienne
WO2011128291A3 (fr) * 2010-04-12 2012-03-22 Wobben, Aloys Commande d'azimut ou commande de pas variable pour éolienne
CN102884315A (zh) * 2010-04-12 2013-01-16 乌本普罗帕蒂斯有限公司 风能设备方位或变桨驱动装置
JP2012031827A (ja) * 2010-08-02 2012-02-16 Sumitomo Heavy Ind Ltd 風力発電設備の減速装置
CN109707829A (zh) * 2014-05-09 2019-05-03 纳博特斯克有限公司 轴向变换齿轮装置
CN107989976A (zh) * 2017-11-28 2018-05-04 西安航天精密机电研究所 一种具有换向功能的rv减速器
CN109333339A (zh) * 2018-10-17 2019-02-15 福州大学 一种轮毂数控抛光机及其工作方法
CN109333339B (zh) * 2018-10-17 2020-12-25 福州大学 一种轮毂数控抛光机及其工作方法
CN111828550A (zh) * 2019-04-15 2020-10-27 纳博特斯克有限公司 减速器和机器人

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