WO2011068160A1 - 歯車装置 - Google Patents
歯車装置 Download PDFInfo
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- WO2011068160A1 WO2011068160A1 PCT/JP2010/071588 JP2010071588W WO2011068160A1 WO 2011068160 A1 WO2011068160 A1 WO 2011068160A1 JP 2010071588 W JP2010071588 W JP 2010071588W WO 2011068160 A1 WO2011068160 A1 WO 2011068160A1
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- gear
- shaft
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- external
- eccentric body
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- 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
Definitions
- the present invention relates to a gear device, and more particularly, to a gear device in which a fitting mode between a gear and a shaft member is devised to achieve both an increase in load capacity (improvement of durability) and an improvement in compactness.
- Patent Document 1 discloses an eccentric rocking inscribed meshing gear device.
- the eccentric body shaft 14 is rotated by the rotation of the input shaft 12, and the eccentric body shaft 14 is rotated by the eccentric bodies 14A and 14B.
- the external gears 16 and 17 are internally meshed with the internal gear 18 (the internal roller 18A which is an internal tooth thereof) while being eccentrically swung.
- relative rotation is generated between the external gears 16 and 17 and the internal gear 18 according to the difference in the number of teeth of the external gears 16 and 17 and the internal gear 18 (in this example, one). Therefore, the rotation of either the internal gear 18 or the external gears 16 and 17 is restricted, and the relative rotational component is output from the other side.
- the plurality of rollers 20 and 21 are positioned by the retainers 22 and 23 in the circumferential direction and the axial direction along the axial direction (parallel to the shaft).
- the life of the fitting portion between the external gear and the eccentric body shaft is a major factor that determines the life of the entire speed reducer.
- the load capacity of the eccentric bearing (roller) is mainly determined by the size (diameter and length) of the roller, the number of rollers, and the pitch circle diameter of the rollers (for example, in JIS B 1518, based on these factors) Calculation formula for allowable load is defined).
- the present invention has been made to solve such a conventional problem, and includes an increase in load capacity (improvement of durability) and an improvement in compactness in a gear / shaft member fitting structure using rollers. It is an object of the present invention to provide a gear device that balances the above.
- the present invention provides a gear device including a gear having a shaft insertion hole formed in the axial direction; An inner peripheral surface provided with a shaft member fitted in the shaft insertion hole, and a plurality of rolling elements arranged between the gear and the shaft member, wherein the shaft insertion hole of the gear is formed, or
- the above-mentioned problem is solved by adopting a configuration in which a plurality of concave portions that accommodate the plurality of rolling elements are formed in the circumferential direction on the outer peripheral surface of the shaft member.
- the shaft member to be fitted into the gear and the shaft insertion hole of the gear according to the present invention has a recess for accommodating a part of a rolling element such as a roller disposed between the gear and the shaft member on either side thereof. It is provided in the axial direction. For this reason, an element of “sliding contact (surface contact)” can be added to the fitting structure of the shaft member and the gear, which has been conventionally “rolling contact (line contact or point contact)”. It is possible to simultaneously obtain the two actions of reducing the sliding resistance due to the rotation of the rolling element and increasing the load capacity by increasing the contact area between the inner wall surface of the recess and the rolling element.
- the retainer which has been essential in the past, is not required to define the circumferential position and the axial position of the plurality of rolling elements. Therefore, it becomes possible to newly add and arrange rolling elements in the space occupied by the retainer itself in the circumferential direction.
- the rolling element is a “roller”
- the axial length of the roller can be further extended by an amount corresponding to the space occupied by the retainer itself in the axial direction of the roller. For this reason, if the axial direction length of the whole gear apparatus can be ensured equally, the load capacity can be increased accordingly. Alternatively, if the same load capacity is sufficient, the axial length of the gear device can be reduced accordingly.
- the rolling element since a part of the rolling element is accommodated in the recess, it can be assembled in a state in which a part of the rolling element enters the gear or shaft member side, so that the radial size of the gear device is the same. If so, it is possible to increase the load capacity by arranging a rolling element having a larger diameter. Conversely, if the diameter of the rolling element is kept the same, the size of the gear device in the radial direction can be further reduced. In addition, when the recess is formed on the gear side, the pitch circle diameter of the rolling elements can be increased.
- an increase in load capacity (improvement of durability) and an improvement in compactness can be rationally achieved in a gear / shaft member fitting structure using rolling elements.
- Sectional drawing which shows the gear apparatus which concerns on an example of embodiment of this invention.
- Sectional view taken along line II-II in FIG. Partial enlarged sectional view near arrow III Front view of a single external gear in the above gear device
- Sectional drawing which shows the example in which the said gear apparatus was used for the yaw drive of a wind power generator The effect of downsizing the gear device is shown in comparison with a conventional gear device.
- (A) is a conventional gear device (cross-sectional view corresponding to Va-Va in FIG. 12), and
- (B) is according to the above embodiment.
- Partial sectional view showing a modified example of forming a recess Sectional drawing which shows the gear apparatus which concerns on an example of further another embodiment of this invention.
- Sectional view along line XX in FIG. The fragmentary sectional view which shows the vicinity of the planetary gear of the gear apparatus which concerns on an example of other embodiment of this invention.
- Sectional drawing equivalent to FIG. 1 which shows an example of the conventional gear apparatus
- the gear device rotates a power generation unit (nacelle) arranged at the top of a cylindrical column of a wind power generation system (not shown) in the horizontal direction and is rotatably attached to the nacelle. It is used to change the rotation axis of the windmill blade (blade) according to the wind direction or the like. The manner of incorporation into the wind power generation system will be described later, starting with the configuration of the gear device itself.
- nacelle power generation unit
- a wind power generation system not shown
- FIG. 1 is a cross-sectional view of a gear device G1 according to an example of an embodiment of the present invention
- FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1
- FIG. 4 and 4 are front views of the external gear alone.
- this gear device G1 is formed by connecting an input side reduction mechanism 40 and an output side reduction mechanism 42 of an eccentric rocking intermeshing planetary gear mechanism in series. This is because the gear device G1 requires an extremely high reduction ratio of 1/1000 to 1/3000 in function.
- the input-side deceleration mechanism 40 and the output deceleration mechanism 42 have substantially the same configuration in terms of mechanistics, although the sizes of the input-side deceleration mechanism 40 and the output deceleration mechanism 42 are different because of different torques.
- the output side reduction mechanism 42 since the present invention is applied to the output side reduction mechanism 42, the output side reduction mechanism 42 will be described in detail for convenience, and the detailed description of the input side reduction mechanism 40 will be omitted.
- the output-side deceleration mechanism 42 includes an input shaft 43 that is integral with (combined with) the output shaft of the input-side deceleration mechanism 40.
- the input shaft 43 is supported at both ends by a self-aligning roller bearing 45 and a bearing 47.
- An eccentric body shaft 44 is incorporated in the input shaft 43 so as to be integrally rotatable.
- the eccentric body shaft 44 is disposed at the center in the radial direction of the gear device G1 and has two eccentric bodies 44A and 44B.
- a plurality of rollers 46 and 48 are arranged along the axial direction on the outer circumferences of the eccentric bodies 44A and 44B, respectively.
- External gears 50 and 52 are fitted to the outer circumferences of the plurality of rollers 46 and 48 via shaft insertion holes 50A and 52A.
- the external gears 50 and 52 are in mesh with the internal gear 54. That is, in this embodiment, the external gears 50 and 52 are “a gear having a shaft insertion hole formed in the axial direction”, the rollers 46 and 48 are “a plurality of rolling elements”, and the eccentric body shaft 44 is “the shaft”. It corresponds to the “shaft member fitted in the insertion hole”.
- the fitting structure of the eccentric body shaft 44, the rollers 46 and 48, and the external gears 50 and 52 will be described in detail later.
- the external gears 50 and 52 are formed at positions offset from the center O1 (see FIG. 4) and have inner pin holes 50B and 52B penetrating in the axial direction, respectively.
- the inner pin holes 50B and 52B are formed at equal intervals in the circumferential direction, but are not necessarily equal.
- An inner pin 60 (with inner roller 62) is loosely fitted in the inner pin holes 50B and 52B.
- the external gears 50 and 52 are 180 ° out of phase with each other, and are internally meshed with the internal gear 54.
- the internal gear 54 also serves as the casing 56 of the output side reduction mechanism 42.
- the internal teeth of the internal gear 54 are constituted by cylindrical outer pins 58.
- the number of internal teeth of the internal gear 54 (the number of external pins 58) is one more than the number of external teeth of the external gears 50 and 52.
- the inner pin 60 is press-fitted and integrated with the output flange 64, and the output flange 64 is integrated with the output shaft 66.
- symbol 68 of a figure is an inner pin support ring which supports the several inner pin 60 collectively.
- the inner pin support ring 68 is formed of a thick member and is rotatably held by the casing 70, so that the inner pin support ring 68 has a "bearing" function.
- the inner pin 60 is supported at both ends by the inner pin support ring 68 and the output flange 64, and an external radial load (a load reversely input from the wind turbine blade side by the wind pressure) is supported by the support portion of the inner pin 60. It is shut off.
- the eccentric body shaft 44, the rollers 46 and 48, and the external gears 50 and 52 are assembled in a state without a gap by an interference fit so as to have a self-locking function.
- the effect of being able to block the external radial load from adversely affecting the eccentric movement of the external gears 50 and 52 by the both-end support of the inner pin 60 is great.
- the gear device G ⁇ b> 1 is connected to a motor Mo, and is fixed to a casing body 74 of a nacelle (a power generation unit to which wind turbine blades are rotatably attached) together with casings 70 and 56 by bolts 71.
- a nacelle a power generation unit to which wind turbine blades are rotatably attached
- the wall thickness in the vicinity of the bolts 71 of the casings 70 and 56 of the gear device G1 is formed so thin is that the rigidity of the casing body 74 of the nacelle can be used as “back”.
- a yaw driving pinion (pinion for rotating the nacelle in a horizontal plane) 75 in a nacelle (not shown) of the wind power generation system is connected and fixed to the output shaft 66 of the gear device G1.
- the yaw drive pinion 75 meshes with the turning internal gear 77 (which constitutes the inner ring of the yaw bearing 76).
- the turning internal gear 77 is fixed to a cylindrical column side (not shown) of the wind power generation system, and the outer frame portion 78 constituting the outer ring of the yaw bearing 76 is fixed to the casing body 74 side of the nacelle.
- Reference numeral 79 in FIG. 6 denotes a brake unit including a brake thruster 79A, a yaw brake caliper 79B, a brake disc 79C, and the like.
- the inner peripheral surfaces of the shaft insertion holes 50A, 52A of the external gears 50, 52 have a plurality of recesses 50C, 52C that respectively accommodate a part of the plurality of rollers 46, 48 in the circumferential direction along the axial direction. Is formed.
- the number of the inner pin holes 50B, 52B and the inner pins 60 formed in the external gears 50, 52 is twelve, the rollers 46, 48 and the recesses 50C,
- the number of 52C is the same number of twelve.
- the recess 50C of the external gear 50 is formed on the radially inner inner peripheral surface between the inner pin hole 50B and the inner pin hole 50B, and similarly, the recess 52C of the external gear 52 is formed on the inner pin hole. It is formed on the inner peripheral surface on the radially inner side between 52B and the inner pin hole 52B.
- “the inner peripheral surface on the radially inner side between the inner pin hole 50B (52B) and the inner pin hole 50B (52B)” means the outer gear 50 (52) as shown in FIG. It means that the center O3 of the roller 46 (48) does not exist on the line Li1 connecting the center O1 and the center O2 of the inner pin hole 50B (52B).
- the tangent line between the adjacent inner pin holes 50B (52B) ( That is, the center O3 of the roller 46 (48) is located between the tangent line Li2 of the specific inner pin hole 50B (52B) and the tangent line Li3 of the adjacent inner pin hole 50 (52B). More preferably, the center O3 of the roller 46 (48) is located between the adjacent tangents Li2 and Li3. In these configurations, the recesses 50C and 52C are externally toothed as much as possible while ensuring a sufficient distance L1 (see FIGS.
- the axial cross sections of the inner wall surfaces 50C1 and 52C1 of the recesses 50C and 52C are “arcs”, and the diameter d1 of the arcs coincides with the diameters (d1) of the rollers 46 and 48 (see FIG. 2). That is, the entire inner wall surfaces 50C1 and 52C1 of the recesses 50C and 52C are in contact with the rollers 46 and 48, respectively.
- the convex portion 50D between the concave portions 50C and 50C of the external gear 50 (the convex portion 52D between the concave portions 52C and 52C of the external gear 52) has a circumferential positioning function of the rollers 46 and 48, respectively. Plays.
- the recesses 50C and 52C of the external gears 50 and 52 are heat-treated by drawing them with a broach together with the shaft insertion holes 50A and 52A, and then polishing the recesses 50C and 52C. Assembly is performed by inserting the eccentric body shaft 44 inside the rollers 46 and 48 after disposing the rollers 46 and 48 in the recesses 50C and 52C of the external gears 50 and 52, respectively.
- the external gears 50 and 52 and the eccentric body shaft 44 are inserted and fitted so as to have an interference fit through the recesses 50C and 52C and the rollers 46 and 48.
- the self-locking property of the wind power generation system in which the gear device G1 is incorporated can be provided. That is, even when an external force is applied from the output pinion 75 side due to a gust of wind or the like, the self-locking function that the gear device G1 is not reversely driven by the external force can be exerted. Therefore, for example, in the motor Mo to counter the external force A brake device (not shown) to be arranged can be reduced in size. Moreover, since the use frequency and load of this brake device can be reduced, the lifetime of this brake device can be kept long.
- This self-locking function is particularly effective when, for example, the present invention is applied to a gear device for adjusting the angle of a windmill blade (so-called pitch driving gear device) or the like where the brake device is frequently used (or used for a long time). is there.
- pitch driving gear device gear device for adjusting the angle of a windmill blade
- an interference fit here means that the members to be assembled with each other have a dimensional relationship that cannot be assembled as they are under the same temperature.
- the outer member is shrink-fitted to a high temperature
- the inner member is cold-fitted to a low temperature, or a strong indentation force is applied. Assembling is done using a method such as press-fitting.
- symbol 59 is the winning for positioning the rollers 46 and 48 in the axial direction
- 61 is a spacer.
- the first-stage deceleration is performed by the same operation as that of the output-side deceleration mechanism 42 described below.
- the second-stage deceleration is performed as follows. That is, in this embodiment, since the internal gear 54 is integrated and fixed with the casing 56, the external gears 50 and 52 are eccentric shafts when the input shaft 43 of the output side reduction mechanism 42 rotates once. It swings once through 44 eccentric bodies 44A and 44B. As a result, the meshing position between the external gears 50 and 52 and the internal gear 54 is shifted by one tooth (by the difference in the number of teeth). As a result, the external gears 50 and 52 rotate relative to the internal gear 54 by an angle corresponding to the difference in the number of teeth (rotates in the direction opposite to the rotation of the eccentric body shaft 44).
- the relative rotation (spinning) of the external gears 50 and 52 with respect to the internal gear 54 is taken out from the output flange 64 through loose fitting of the internal pin holes 50B and 52B and the internal pin 60 (and the internal roller 62).
- the rotation of the output flange 64 is transmitted to an output shaft 66 integrated with the output flange 64.
- the output shaft 66 is connected and fixed with a pinion 75 for yaw drive of the wind power generation system.
- the yaw drive pinion 75 meshes with the turning internal gear 77 (which constitutes the inner ring of the yaw bearing 76).
- the entire nacelle can be swung in a horizontal plane via the meshing of the pinion 75 for yaw driving and the swiveling internal gear 77.
- the nacelle can be directed in a desired direction (for example, the windward direction), and the wind pressure can be efficiently received.
- FIG. 6A shows a cross section of the conventional gear device Go of FIG. 12, and FIG. 6B shows a cross section (same as FIG. 2) of the gear device G1 of this embodiment.
- all members other than the rollers 46, 48 (20, 21) and the external gears 50, 52 (16, 17) are the same for convenience.
- the recesses 50C and 52C that respectively accommodate a part of the plurality of rollers 46 and 48 are provided on the inner peripheral surfaces of the shaft insertion holes 50A and 52A of the external gears 50 and 52 in the axial direction. Are formed in the circumferential direction. For this reason, an element of “sliding contact (surface contact)” is provided for the fitting of the eccentric body shaft 14 and the external gears 16 and 17, which has been regarded as “rolling contact (line contact)” by the conventional rollers 20 and 21. Can be added.
- the rollers 46 and 48 rotate, the sliding resistance can be reduced as compared with a simple sliding bearing, and the contact area between the rollers 46 and 48 and the inner wall surfaces 50C1 and 52C1 of the recesses 50C and 52C is remarkably higher than before.
- the load capacity can be increased by that amount (while the size GL1 (GLo) in the radial direction of the gear unit G1 (Go) is kept the same).
- the structure of the present invention is not used for the input side reduction mechanism 40, and the structure of the present invention is used only for the output side reduction mechanism 42.
- the rollers 46 and 48 are in sliding contact with the recesses 50C and 52C, it is preferable to use the rollers 46 and 48 at a low speed portion.
- the rotational speed of the motor is 1200 rpm and the reduction ratio of the input side reduction mechanism 40 is 30, the rotational speed of the eccentric body shaft 44 is 40 rpm.
- the reduction ratio of the output side reduction mechanism 42 in this embodiment is 43 (the number of teeth of the external gears 50 and 52 is 43 and the difference in the number of teeth from the internal gear 54 is 1)
- the rotation speed of the gears 50 and 52 is less than 1 rpm. That is, the relative rotational speed between the external gears 50 and 52 and the eccentric body shaft (shaft member) 44 is about 42 rpm.
- the relative rotational speed of the gear and the shaft member is applied to a location where it is smaller than 100 rpm, the true value can be more effectively exhibited.
- rollers 46 and 48 are accommodated in the recesses 50C and 52C, the retainers 22 and 23, which have been indispensable in the past, are required to define the circumferential position and the axial position of the plurality of rollers 46 and 48. Do not need. Further, the rollers 46 and 48 can be assembled in a state in which a part of the rollers 46 and 48 enters the external gears 50 and 52 because the rollers 46 and 48 are accommodated in the recesses 50C and 52C.
- the space occupied by the retainers 22 and 23 themselves in the circumferential direction is increased by “increasing the diameter of the rollers 46 and 48 ( d0 ⁇ d1) ”, and also in this respect, the load capacity can be surely increased (if the same load capacity is sufficient, the size of the gear device G1 in the radial direction is larger than that of the gear device Go). Can be smaller). Further, in this embodiment, since the recesses 50C and 52C are formed on the external gears 50 and 52 side, the pitch circle d4 of the rollers 46 and 48 can be increased (d3 ⁇ d4).
- the rollers 46 and 48 correspond to the space occupied by the retainers 22 and 23 themselves in the axial direction of the rollers 20 and 21.
- the load capacity can be surely increased (if the same load capacity is sufficient, the axial length (GL1) of the gear device G1 is correspondingly increased). It can be shortened from the axial length GLo of the gear device Go).
- the number of the inner pins 60 is the same as the number of the recesses 50C and 52C, and each of the plurality of recesses 50C and 52C is formed between the inner pin holes 50B and 52B of the external gears 50 and 52. Is formed on the inner peripheral surface on the radially inner side between the rollers 46 and 48, and the concave portion (which tends to become a neck due to the strength of the external gears 50 and 52) even though the diameter of the rollers 46 and 48 and the pitch circle d4 are increased. It is possible to ensure a large distance L1 between 50C and 52C and the inner pin holes 50B and 52B.
- the number of inner pins 60 and the number of recesses 50C and 52C are the same (both are 12), and rollers 46 and 48 are respectively provided corresponding to all of the inner pin holes 50B and 52B.
- the number of rollers 46 and 48 may be smaller than the number of inner pins 60.
- the formation positions of the recesses 50C and 52C are not simply equally distributed in the circumferential direction, but are only radially inward between the inner pin holes 50B and 52B of the external gears 50 and 52. It is good to form it on the inner peripheral surface.
- the number of inner pin holes may be smaller than the number of rollers. In this case, it is preferable to form two or more recesses on the inner peripheral surface on the radially inner side between the inner pin holes.
- the concave portion is formed on the external gear side.
- the concave portion may be formed on the shaft member side.
- FIG. 7 An example is shown in FIG. In the embodiment shown in FIG. 7, a recess 144 ⁇ / b> C is formed in the eccentric body shaft (shaft member) 144.
- the convex portion 144D between the concave portions 144C fulfills the positioning function of the rollers 146 (148).
- no recess is formed in the external gear 150 (152). Even with such a configuration, it is possible to obtain substantially the same operational effects as those described above.
- the roller revolves around the shaft member at the same speed as that of either the shaft member or the gear (the side where the recess is formed). Therefore, it is an important design point to rotate the roller more efficiently.
- the variation in which the concave portion is formed in the shaft member has a tendency that the contact resistance between the roller and the shaft member side becomes larger (relative to the contact resistance between the roller and the gear side). Depending on the speed, it may be easier to find a design point for rotating the roller more efficiently.
- arc-shaped concave portions 50C and 52C having the same diameter (d1) as the diameter d1 of the rollers 46 and 48 are formed, and the entire inner wall surfaces 50C1 and 52C1 of the concave portions 50C and 52C are rollers.
- the formation shape of the recess in the present invention is not limited to this example.
- only a part of the inner wall surface of the recess may be in contact with the roller. An example of this is shown in FIG.
- (A) of FIG. 8 is configured such that the axial cross-sectional shape of the recess C10 of the gear G10 is an ellipse, and is in contact with the roller R10 only at two locations near the openings C11 and C12.
- the contact area between the concave portion C10 and R10 is reduced compared to the configuration according to the previous embodiment of FIGS. 1 to 5, and even if there is a slight manufacturing error, the roller R10 fits into the concave portion C10. More stable.
- FIG. 8 is obtained by further forming a plurality of concave portions C21 and C22 in the concave portion C20 of the gear G20 and intermittently reducing the contact portion with the roller R20.
- An intermediate effect between the configuration according to the embodiment of FIGS. 1 to 5 and the configuration of FIG. 8A is obtained.
- FIG. 8C shows a case where the arc diameter d3 of the recess C30 of the gear G30 is slightly larger than the diameter d4 of the roller R30.
- This configuration can further reduce the contact area between the concave portion C30 and the R30, and can also obtain the self-aligning effect of the shaft member S10 with respect to the gear G30, so that the smoothness of rotation can be further improved.
- the contact with the concave portion C30 and R30 is closer to the line contact than in the examples of FIGS. 8A and 8B (see FIG. 8C).
- the contact with the concave portion changes from “convex-convex contact” to “convex-concave contact” in the axial section, so that it is almost in a state of line contact. Even so, the damage to the contact area is much less (than conventional convex-convex contact).
- the example of FIG. 8C also provides a design advantage that it is easy to find a design point where the rollers can efficiently rotate (adjustment is easy).
- the formation shape of the concave portion of the present invention is appropriately determined in consideration of the use of the gear device, the material and relative rotational speed of the gear and the shaft member, durability to be obtained, smoothness of rotation, and the like. Good.
- the eccentric body shaft has the eccentric oscillating intermeshing planetary gear mechanism in which the eccentric shaft is located at the center in the radial direction of the gear device.
- the gear device to which the present invention is applied has this structure.
- the present invention is not limited to the gear device.
- the present invention can also be applied to a gear device G ⁇ b> 2 configured such that a plurality of eccentric body shafts (shaft members) pass through external gears (gears).
- the four eccentric body shafts 84 rotate at the same time through the transmission gears 82 and 83.
- the eccentric bodies 84 ⁇ / b> A and 84 ⁇ / b> B that are integrally attached to the eccentric body shafts 84 rotate in the same phase, and the external gears 90 and 92 are connected to the internal gear 94 via the rollers 86 and 88. Oscillates and rotates while inscribed inside. Since the internal gear 94 is integrated with the casing 96 and is fixed, when the external gears 90 and 92 swing and rotate, pins that are internal teeth of the external gears 90 and 92 and the internal gear 94 are provided. A phenomenon occurs in which the meshing position with 94P sequentially moves.
- the eccentric body shaft 84 revolves around the shaft center of the gear device G2 at a speed corresponding to the rotation component, and the first and second carriers 96 and 98 supporting the eccentric body shaft 84 are integrated. It rotates at a speed corresponding to the revolution speed.
- the external gears 90 and 92 as gears, the eccentric body shaft 84 as a shaft member, and the eccentric bodies 84A and 84B of the external gears 90 and 92 and the eccentric body shaft 84 are provided.
- the plurality of rollers 86 and 88 disposed in the circumferential direction along the axial direction therebetween external gears 90 and 92 (inner circumference of the shaft insertion hole formed and fitted with the eccentric body shaft 84)
- the recesses 90C and 92C By forming the recesses 90C and 92C, the same configuration as that of the previous embodiment can be taken, and the same effect can be obtained.
- the present invention includes a planetary gear 100 as a gear of the present invention, a carrier pin 102 as a shaft member that rotatably supports the planetary gear 100, and the planetary gear 100 and the carrier pin. And a plurality of rollers 104 arranged in the circumferential direction along the axial direction between the planetary gear 102 and the sun gear and an internal gear (both not shown). , And a gear unit G3 that constitutes a simple planetary gear mechanism with internal gears. Since the simple planetary gear mechanism itself is known, detailed description is omitted.
- each of the concave portions 100A of the planetary gear 100 (formed on the inner peripheral surface of the shaft insertion hole into which the carrier pin 102 formed is fitted) is a radius of the tooth portion 100B of the planetary gear 100. It is good to comprise so that it may be formed inside a direction. More preferably, as shown in FIG. 11, the tooth portion 100 ⁇ / b> B may be formed radially inward of the circumferential center position (near). As a result, a large distance L2 between the recess 100A and the tooth bottom 100C of the planetary gear 100 can be secured, and a larger roller 104 (or a larger pitch circle) can be incorporated.
- the present invention can be applied to various gear devices.
- the use may be for pitch driving of a wind power generation system, and further, it is not limited to the use of a gear device of a wind power generation system.
- the method for forming the concave portion according to the present invention is not limited to this.
- a plurality of circular holes holes that will later become part of the recesses
- the circular holes are polished, and then a part of each circular hole is cut.
- the part which a part of circular hole was notched by the shaft insertion hole and remained can be utilized as a recessed part.
- the pitch circle diameter of the recess (50C) (the pitch circle diameter of the roller) was smaller than the diameter of the projection (50D).
- the pitch circle diameter of the recesses (the pitch circle diameter of the rollers) is larger than the diameter of the projections.
- rolling elements of the present invention are not necessarily “rollers”, and may be rolling elements such as “balls”.
- the configuration of the “gear” to be applied is not particularly limited, and may be a swinging intermeshing external gear, an involute gear of a simple planetary gear mechanism, or a gear device having another configuration. It can also be applied to other gears.
- the swinging internal meshing gear device of the type in which the internal gear swings can be applied to the internal gear.
- Gear device 44 Eccentric body shaft (shaft member) 44A, 44B ... Eccentric body 46, 48 ... Roller (rolling element) 50, 52 ... External gears 50A, 52A ... Shaft insertion holes 50B, 52B ... Inner pin holes 50C, 52C ... Recesses 50C1, 52C1 ... Inner wall surfaces 50D, 52D ... Protrusions 54 ... Internal gears 60 ... Inner pins
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Abstract
Description
前記軸挿入孔に嵌合された軸部材と、前記歯車と軸部材の間に配置された複数の転動体と、を備え、且つ前記歯車の前記軸挿入孔が形成されている内周面または前記軸部材の外周面に、前記複数の転動体を収容する凹部が、円周方向に複数形成されている構成とすることにより、上記課題を解決したものである。
44…偏心体軸(軸部材)
44A、44B…偏心体
46、48…ころ(転動体)
50、52…外歯歯車
50A、52A…軸挿入孔
50B、52B…内ピン孔
50C、52C…凹部
50C1、52C1…内壁面
50D、52D…凸部
54…内歯歯車
60…内ピン
Claims (11)
- 歯車装置において、
軸方向に形成された軸挿入孔を備えた歯車と、
前記軸挿入孔に嵌合された軸部材と、
前記歯車と軸部材の間に配置された複数の転動体と、を備え、且つ
前記歯車の前記軸挿入孔が形成されている内周面または前記軸部材の外周面に、前記複数の転動体を収容する凹部が、円周方向に複数形成されている
ことを特徴とする歯車装置。 - 請求項1において、
前記凹部が、前記歯車の前記軸挿入孔が形成されている内周面に形成されている
ことを特徴とする歯車装置。 - 請求項2において、
前記歯車としての外歯歯車と、偏心体を備えた前記軸部材としての偏心体軸と、前記外歯歯車と前記偏心体軸の偏心体との間に配置された複数の転動体と、更に、前記外歯歯車が内接噛合する内歯歯車と、を備え、
前記偏心体軸の偏心体、転動体、及び凹部を介して前記外歯歯車を偏心揺動させながら前記内歯歯車に内接噛合させる偏心揺動内接噛合型の遊星歯車機構を構成した
ことを特徴とする歯車装置。 - 請求項3において、
更に、前記外歯歯車を貫通する複数の内ピンを備えると共に、前記外歯歯車が該複数の内ピンがそれぞれ挿入される複数の内ピン孔を該外歯歯車の中心からオフセットした位置に備え、
前記偏心体軸が、当該歯車装置の半径方向中央に配置され、且つ、前記軸挿入孔が前記外歯歯車の半径方向中央に形成され、
前記複数の凹部の各々が、前記内ピン孔と内ピン孔との間の半径方向内側において前記歯車の前記軸挿入孔の形成されている内周面に形成されている
ことを特徴とする歯車装置。 - 請求項4において、
前記内ピンの数と前記凹部の数が同数である
ことを特徴とする歯車装置。 - 請求項1において、
前記歯車としての遊星歯車と、該遊星歯車を回転自在に支持する前記軸部材としてのキャリヤピンと、前記遊星歯車と前記キャリヤピンとの間に配置された複数の転動体と、を備えると共に、更に前記遊星歯車と噛合する太陽歯車及び内歯歯車と、を備え、
前記遊星歯車、太陽歯車、及び内歯歯車とで単純遊星歯車機構を構成した
ことを特徴とする歯車装置。 - 請求項6において、
前記凹部の各々が、前記遊星歯車の歯部の半径方向内側に形成されている
ことを特徴とする歯車装置。 - 請求項1~7のいずれかにおいて、
前記凹部の内壁面の一部のみが前記転動体と接触している
ことを特徴とする歯車装置。 - 請求項1~8のいずれかにおいて、
前記凹部と凹部の間の凸部が前記転動体の円周方向の位置決め機能を備えている
ことを特徴とする歯車装置。 - 請求項1~9のいずれかにおいて、
前記歯車と、前記軸部材とが、前記凹部及び転動体を介して締まり嵌めにて嵌合している
ことを特徴とする歯車装置。 - 請求項3において、
前記揺動内接噛合歯車機構を構成する前記偏心体軸、外歯歯車、及び内歯歯車が、前記外歯歯車の凹部及び転動体の接触部分を含めて、締まり嵌めにて組み込まれている自然エネルギの回収装置の駆動部用の歯車装置。
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Cited By (2)
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CN106090186B (zh) * | 2016-06-13 | 2018-10-02 | 中航工业哈尔滨轴承有限公司 | 用于端面研磨机上的行星轮及该行星轮内孔的设计方法 |
CN110005759A (zh) * | 2017-11-15 | 2019-07-12 | 住友重机械工业株式会社 | 偏心摆动型齿轮装置 |
Families Citing this family (5)
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JP2013096550A (ja) * | 2011-11-04 | 2013-05-20 | Nabtesco Corp | 歯車伝動装置 |
JP6310764B2 (ja) * | 2014-04-30 | 2018-04-11 | ナブテスコ株式会社 | 歯車伝動装置 |
JP6378110B2 (ja) * | 2015-02-19 | 2018-08-22 | 日本電産コパル株式会社 | 遊星歯車伝動装置 |
KR101955790B1 (ko) * | 2017-03-27 | 2019-03-07 | 유경복 | 심플렉스 드라이브 |
JP7047301B2 (ja) * | 2017-09-22 | 2022-04-05 | 日本電産株式会社 | 変速機 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0618724U (ja) * | 1992-08-11 | 1994-03-11 | 株式会社鈴木鉄工所 | 溶融金属浴用軸受 |
JPH0669495U (ja) * | 1993-03-16 | 1994-09-30 | 帝人製機株式会社 | 偏心差動式減速機 |
JPH07317756A (ja) * | 1994-05-23 | 1995-12-08 | Sando Iron Works Co Ltd | 液中ベアリング |
JP2007024072A (ja) * | 2005-07-12 | 2007-02-01 | Koekkusu:Kk | 内接式遊星歯車機構(インボリュート型減速機構) |
JP2008038941A (ja) * | 2006-08-02 | 2008-02-21 | Sumitomo Heavy Ind Ltd | 偏心揺動歯車装置 |
JP2009047242A (ja) * | 2007-08-20 | 2009-03-05 | Sumitomo Heavy Ind Ltd | 出力ギヤ付減速装置及びその組み付け方法 |
JP2009144533A (ja) * | 2007-12-11 | 2009-07-02 | Mitsubishi Heavy Ind Ltd | 風力発電装置 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5551875B2 (ja) * | 2007-02-05 | 2014-07-16 | 住友重機械工業株式会社 | 動力伝達装置及びその製造方法 |
-
2009
- 2009-12-02 JP JP2009274773A patent/JP5256181B2/ja active Active
-
2010
- 2010-12-02 CN CN201080051092.6A patent/CN102667238B/zh not_active Expired - Fee Related
- 2010-12-02 WO PCT/JP2010/071588 patent/WO2011068160A1/ja active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0618724U (ja) * | 1992-08-11 | 1994-03-11 | 株式会社鈴木鉄工所 | 溶融金属浴用軸受 |
JPH0669495U (ja) * | 1993-03-16 | 1994-09-30 | 帝人製機株式会社 | 偏心差動式減速機 |
JPH07317756A (ja) * | 1994-05-23 | 1995-12-08 | Sando Iron Works Co Ltd | 液中ベアリング |
JP2007024072A (ja) * | 2005-07-12 | 2007-02-01 | Koekkusu:Kk | 内接式遊星歯車機構(インボリュート型減速機構) |
JP2008038941A (ja) * | 2006-08-02 | 2008-02-21 | Sumitomo Heavy Ind Ltd | 偏心揺動歯車装置 |
JP2009047242A (ja) * | 2007-08-20 | 2009-03-05 | Sumitomo Heavy Ind Ltd | 出力ギヤ付減速装置及びその組み付け方法 |
JP2009144533A (ja) * | 2007-12-11 | 2009-07-02 | Mitsubishi Heavy Ind Ltd | 風力発電装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106090186B (zh) * | 2016-06-13 | 2018-10-02 | 中航工业哈尔滨轴承有限公司 | 用于端面研磨机上的行星轮及该行星轮内孔的设计方法 |
CN110005759A (zh) * | 2017-11-15 | 2019-07-12 | 住友重机械工业株式会社 | 偏心摆动型齿轮装置 |
CN110005759B (zh) * | 2017-11-15 | 2022-05-17 | 住友重机械工业株式会社 | 偏心摆动型齿轮装置 |
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JP2011117521A (ja) | 2011-06-16 |
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