WO2012063555A1 - 遊星歯車減速機 - Google Patents
遊星歯車減速機 Download PDFInfo
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- WO2012063555A1 WO2012063555A1 PCT/JP2011/071340 JP2011071340W WO2012063555A1 WO 2012063555 A1 WO2012063555 A1 WO 2012063555A1 JP 2011071340 W JP2011071340 W JP 2011071340W WO 2012063555 A1 WO2012063555 A1 WO 2012063555A1
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- side plate
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- planetary gear
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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
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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
- F16H2001/325—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 comprising a carrier with pins guiding at least one orbital gear with circular holes
Definitions
- the present invention relates to a planetary gear reducer in which the center of revolution of the planetary gear is located inside the planetary gear.
- Japanese Patent Laid-Open No. 2006-263878 discloses that in a planetary gear speed reducer in which the center of revolution of the planetary gear is located inside the planetary gear, a plurality of engagements are made with the planetary gear in order to transmit only the rotation of the planetary gear to the carrier. A mechanism is described in which a hole is formed and a pin inserted into the engagement hole is integrally formed with the carrier.
- the present invention has been made in view of such circumstances, and an object thereof is to provide a planetary gear device that can be manufactured at low cost without integrally forming a carrier and a pin.
- the planetary gear speed reducer according to the present invention is fixed to the planetary gear, the carrier, and the carrier having a plurality of engagement holes in which the revolution center is located inside the planetary gear and penetrates in the axial direction.
- a planetary gear reducer comprising: a plurality of pins that are inserted through the engagement holes and interlock with the rotation of the planetary gear by engagement with the engagement holes.
- the carrier is formed in a disk shape.
- a first side plate that fixes the pin so that the pin protrudes from one end surface in the axial direction, and the outer diameter of the first side plate is a small diameter in the axial direction and a large diameter in the other axial direction.
- the first side plate is formed on a press-fitting hole portion for press-fitting the pin, on one side in the axial direction of the press-fitting hole portion, and opens on one end surface in the axial direction of the first side plate, and at least partially.
- the pin has a non-contact inner peripheral surface And a small-diameter side of the recess.
- the first side plate and the pins constituting the carrier are formed separately, and the pins are fixed to the first side plate by press-fitting, whereby the part manufacturing cost can be reduced.
- the pins are press-fitted into the first side plate, stress is generated in the first side plate, and the first side plate may be deformed.
- the present inventors formed a press-fit hole in the first side plate over the entire axial direction, when the pin is press-fitted into the press-fit hole, the first side plate is deformed by the press-fit, and a plurality of pins are parallel. I found that the degree was worse.
- the parallelism of the plurality of pins is deteriorated as described above, the contact state of the pins with the engagement holes is deteriorated, which causes a reduction in life due to uneven wear of the pins and an increase in transmission torque fluctuation.
- the present inventors conducted extensive research on this cause, and found the cause of the deterioration of the parallelism of the plurality of pins when the pins were press-fitted into the first side plate, leading to the present invention.
- the reason is that if there is a difference in the outer diameter of the first side plate in the axial direction and the pin is press-fit over the entire axial direction of the first side plate, the smaller diameter side of the first side plate is less rigid than the larger diameter side.
- the deformation amount on the small diameter side of the first side plate is increased. Therefore, as in the present invention, a small-diameter recess having an inner peripheral surface that is not in contact with the pin is formed at least partially on the small-diameter side of the first side plate having low rigidity.
- the large-diameter side portion of the first side plate has higher rigidity than the small-diameter side. That is, by pressing the pin into the press-fitting hole portion, the balance between the amount of deformation of the large-diameter side portion of the first side plate in the radial direction and the amount of deformation of the small-diameter side portion of the first side plate in the radial direction is balanced. It is possible to take. As a result, the parallelism of the plurality of pins can be made highly accurate. Therefore, it is possible to extend the service life by suppressing uneven wear of the pins, and to reduce the transmission torque fluctuation.
- the inner peripheral surface of the small-diameter side recess has a portion whose distance from the center of the press-fitting hole portion is longer than the radius of the press-fitting hole portion, and the portion is viewed from the axial direction. And it is good to make it located in the radial direction inner side and radial direction outer side of said 1st side board with respect to the said press-fit hole part.
- the pin in the vicinity of the end surface on the small diameter side of the first side plate, the pin has portions that do not contact the first side plate on the radially inner side and the radially outer side of the first side plate.
- the pin can suppress the stress in the radial direction of the first side plate from acting on the first side plate. Therefore, the parallelism of a plurality of pins can be made highly accurate.
- the inner peripheral surface of the small-diameter side recess may be formed so as to be in non-contact with the pin over the entire circumference.
- the pin does not contact the first side plate over the entire circumference.
- a pin can suppress more reliably that the stress to the radial direction of a 1st side plate acts on a 1st side plate. Therefore, the parallelism of a plurality of pins can be made highly accurate.
- the press-fitting hole portion may be formed between the axial end of the first side plate on the other axial end side and the small diameter side recess. That is, the pin is press-fitted to the end surface on the large diameter side of the first side plate.
- the pin insertion hole formed in the first side plate is a hole having a diameter corresponding to the press-fitting hole portion and a hole having a shape corresponding to the small-diameter side recess. Accordingly, the pin insertion hole can be formed with a small number of processing steps.
- the first side plate is formed on the other axial side of the press-fitting hole, opens on the other axial end surface of the first side plate, and has a non-contact inner peripheral surface on the pin.
- the pressurizing hole portion may be formed between the small-diameter side recess and the large-diameter side recess in the axial direction.
- a small-diameter side recess is formed on one side in the axial direction of the press-fitting hole portion, and a large-diameter side recess is formed on the other side in the axial direction. That is, no pressure input by the pin is applied to the portion having the large-diameter side recess in the first side plate. Therefore, it acts so that the said site
- the small-diameter side recess is formed in the small-diameter side portion of the first side plate, the small-diameter-side recess acts so that the portion is not deformed.
- the balance between the amount of deformation of the large-diameter side portion of the first side plate in the radial direction and the amount of deformation of the small-diameter side portion of the first side plate in the radial direction is balanced. Easy to take. As a result, the parallelism of the plurality of pins can be made highly accurate.
- the pin includes a press-fit shaft portion and an engaging head having a large circumscribed circle diameter of the press-fit shaft portion at an end of the press-fit shaft portion, and the large-diameter side recess has the engagement portion.
- the stop head may be accommodated and locked in the axial direction with respect to the locking head.
- the pin When the locking head of the pin is locked in the axial direction with respect to the large-diameter side recess, the pin can be restricted from moving to the one side in the axial direction with respect to the first side plate. Thereby, when mounting a pin to a 1st side plate, positioning of a pin can be performed reliably. Further, when the pin has a locking head, the amount by which the locking head of the pin protrudes from the end surface on the large diameter side of the first side plate by accommodating the locking head in the large diameter side recess. Can be reduced. Thus, it can be made to act so that it may have a plurality of functions in the large diameter side recess.
- the carrier may include a second side plate that is disposed to face the first side plate so as to sandwich the planetary gear between the first side plate and fix the pin. That is, the first side plate and the second side plate are arranged so as to sandwich the planetary gear from both sides thereof.
- the transmission of rotational force between the planetary gear and the carrier can be stabilized.
- the pins can be easily and reliably fixed to the second side plate. .
- FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
- FIG. 4 is a view on arrow IV of FIG. 3 (right side view of FIG. 3).
- FIG. 4 is a conceptual diagram which shows the displacement of the pin at the time of pin press-fit when a pin is press-fit in the hole of the axial direction same internal diameter in the disk shaped member from which an outer diameter differs in an axial direction.
- FIG. 5 is a conceptual diagram showing displacement of a pin when a pin is inserted into a hole having a press-fitting hole portion, a small-diameter side recess, and a large-diameter side recess in a disk-shaped member having different outer diameters in the axial direction. It is a graph which shows the relationship between a recess depth ratio and a pin inclination angle.
- FIG. 5 is a conceptual diagram showing displacement of a pin when a pin is inserted into a hole having a press-fitting hole portion, a tapered small-diameter side recess, and a large-diameter side recess in a disk-shaped member having different outer diameters in the axial direction. It is an axial view (figure equivalent to the left view of FIG. 10) of the disk-shaped member which has an elliptical shape small diameter side recess.
- the planetary gear reducer 1 of the present embodiment will be described with reference to FIGS.
- the planetary gear speed reducer 1 according to the present embodiment includes the eccentric cam portions 31 and 32 of the crankshaft 3 as eccentric portions, and planetary gears 5 and 5 that are external gears rotatably supported by the eccentric cam portions 31 and 32. 6 and two planetary gears 5 and 6 are sandwiched between first and second side plates 4 and 8 as carriers.
- the planetary gear reducer 1 is configured in detail as follows.
- the planetary gear reducer 1 mainly includes a housing 2, a crankshaft 3, first and second side plates 4 and 8 as carriers, first and second planetary gears 5 and 6, and a plurality of pins 7. .
- the housing 2 is formed in a cylindrical shape, and an internal gear 21 is formed on the inner peripheral surface of the housing 2.
- Angular rolling bearings 9 and 13 are provided on both outer sides in the axial direction of the internal gear 21 on the inner peripheral surface of the housing 2.
- the crankshaft 3 is inserted into the center of the housing 2 and includes first and second eccentric cam portions 31 and 32 at the center in the axial direction, and cylindrical shaft portions 33 and 34 at both ends.
- Bearings 10 and 14 are provided on the outer peripheral surfaces of the cylindrical shaft portions 33 and 34 of the crankshaft 3. Since the cylindrical shaft portions 33 and 34 of the crankshaft 3 are supported by the housing 2 via the side plates 4 and 8, the crankshaft 3 is supported so as to be rotatable around the input / output axis X with respect to the housing 2. .
- the first and second eccentric cam portions 31 and 32 are formed in a circular radial cross-sectional shape, and are eccentric with respect to the rotation center axis (input / output axis) X of the crankshaft 3 (shown in FIG. 2). It is eccentric so that That is, the central axis of the first eccentric cam portion 31 is Y1, and the central axis of the second eccentric cam portion 32 is Y2.
- the central axis Y1 of the first eccentric cam portion 31 and the central axis Y2 of the second eccentric cam portion 32 are axially focused around the input / output axis X, that is, the phase is shifted by 180 degrees.
- Bearings 11 and 12 are provided on the outer peripheral surfaces of the first and second eccentric cam portions 31 and 32.
- the first and second planetary gears 5 and 6 are external gears, and have center holes 52 and 62 coaxial with the central axis of the external gear. Bearings 11 and 12 held by first and second eccentric cam portions 31 and 32 are provided on the inner peripheral surfaces of the respective center holes 52 and 62. That is, the first planetary gear 5 is rotatably supported by the first eccentric cam portion 31. The second planetary gear 6 is rotatably supported by the second eccentric cam portion 32. Therefore, the input / output axis X which is the revolution center of the first and second planetary gears 5 and 6 is positioned inside the first and second planetary gears 5 and 6.
- the external gears of the first and second planetary gears 5 and 6 are formed to have a gear pitch circle diameter that meshes with the internal gear 21 at least at one location. Further, the number of teeth of the first and second planetary gears 5 and 6 is different from the number of teeth of the internal gear 21. That is, when the first and second planetary gears 5 and 6 revolve once with respect to the internal gear 21, the phase is shifted by the difference in the number of teeth between the external gear and the internal gear 21. Further, the first and second planetary gears 5 and 6 are formed with a plurality of engagement holes 51 and 61 penetrating in the axial direction at equal intervals in the circumferential direction.
- FIG. 1 the case where eight engagement holes 51 and 61 are formed in the first and second planetary gears 5 and 6 is shown in FIG.
- the inner diameters of the engagement holes 51 and 61 are d (shown in FIG. 2).
- the press-fit shaft portion 71 of the pin 7 is inserted into the engagement holes 51 and 61, and a part of the outer peripheral surface of the press-fit shaft portion 71 of the pin 7 is always in the engagement holes 51 and 61. Inscribed.
- the first and second side plates 4 and 8 constituting the carrier are formed in a disc shape, and are arranged to face each other so as to sandwich the first and second planetary gears 5 and 6 in the axial direction.
- the first side plate 4 and the second side plate 8 are fixed by pins 7. As described above, the pin 7 is inserted through the engagement holes 51 and 61 of the first and second planetary gears 5 and 6. Details of the first and second side plates 4 and 8 and the pin 7 will be described below.
- the outer peripheral surface of the first side plate 4 is formed stepwise in the axial direction.
- the outer diameter of the outer peripheral surface 44 on one axial side (left side in FIG. 1) of the first side plate 4 is made smaller, and the outer diameter of the outer peripheral surface 45 on the other axial side (right side in FIG. 1) is made larger.
- the inner ring of the angular rolling bearing 9 is provided on the outer peripheral surface 44 on the small diameter side of the first side plate 4, and the end surface of the inner ring of the angular rolling bearing 9 is in contact with the step end surface of the outer peripheral surface of the first side plate 4. . That is, the first side plate 4 is supported by the angular rolling bearing 9 so as to be rotatable about the input / output axis X with respect to the housing 2.
- a circular recess 46 centered on the input / output axis X is formed at the radial center of the first side plate 4.
- a bearing 10 that is held by the cylindrical shaft portion 33 of the crankshaft 3 is provided on the inner peripheral surface of the circular recess 46. That is, the first side plate 4 supports the cylindrical shaft portion 33 of the crankshaft 3 so as to be rotatable around the input / output axis X.
- a plurality of holes 41 penetrating in the axial direction are formed in the first side plate 4 at equal intervals in the circumferential direction.
- Each of the holes 41 includes a press-fit hole portion 41a formed in the central portion in the axial direction, a small-diameter side recess 41b formed in one axial direction of the press-fit hole portion 41a (left side in FIG. 1), and a press-fit hole portion 41a.
- a large-diameter side recess 41c formed on the other side in the axial direction (the right side in FIG. 1).
- the press-fitting hole portion 41a, the small-diameter side recess 41b, and the large-diameter side recess 41c have a circular cross-sectional shape and are formed coaxially.
- the press-fitting hole 41a is a part into which the press-fitting shaft 71 of the pin 7 is press-fitted. Therefore, the inner diameter of the press-fitting hole portion 41 a before press-fitting the pin 7 is slightly smaller than the outer diameter of the press-fitting shaft portion 71 of the pin 7.
- the inner diameters of the small-diameter side recess 41b and the large-diameter side recess 41c are formed larger than the press-fit hole 41a.
- the inner peripheral surfaces of the small-diameter side recess 41 b and the large-diameter side recess 41 c are formed so as not to contact the press-fit shaft portion 71 of the pin 7.
- the small-diameter side recess 41b and the large-diameter side recess 41c are formed in a circular radial cross-sectional shape.
- the large diameter side recess 41 c accommodates the locking head 72 of the pin 7.
- the inner peripheral surface of the large-diameter side recess 41 c is formed so as not to contact the locking head 72 of the pin 7.
- the inner diameter and axial depth of the small-diameter recess 41b and the inner diameter and axial depth of the large-diameter recess 41c can be adjusted as appropriate.
- the pin 7 is formed integrally with a press-fit shaft portion 71 having the same outer diameter D (shown in FIG. 2) in the axial direction and the other axial end of the press-fit shaft portion 71 (on the right side in FIG. 1). And a locking head 72 having a large circumscribed circle diameter.
- the outer diameter D of the press-fit shaft portion 71 is formed smaller than the inner diameter d of the engagement holes 51 and 61 of the first and second planetary gears 5 and 6.
- the pin 7 is inserted from the large-diameter side recess 41c side of the hole 41 of the first side plate 4 and protrudes from one end face in the axial direction of the first side plate 4.
- the press-fit shaft portion 71 of the pin 7 is press-fitted into the press-fit hole portion 41 a of the first side plate 4 and is inserted through the engagement holes 51 and 61 of the first and second planetary gears 5 and 6.
- the press-fitting shaft portion 71 of the pin 7 always rotates in contact with the inner peripheral surfaces of the engagement holes 51 and 61.
- the locking head 72 is locked in the axial direction with respect to the end surface of the large-diameter recess 41c.
- an internal thread 73 is formed at one end (left end in FIG. 1) of the press-fit shaft portion 71 in the axial direction.
- the press-fit shaft portion 71 is press-fitted into the press-fit hole portion 41a, whereby the pin 7 is fixed to the first side plate 4 and the locking head 72 is locked to the large-diameter side recess 41c.
- the pin 7 acts to press the first side plate 4 toward one side in the axial direction (left side in FIG. 1) to apply a preload to the angular rolling bearing 9.
- the outer peripheral surface of the second side plate 8 is formed in a step shape in the axial direction.
- An angular rolling bearing 13 is provided on the outer peripheral surface of the second side plate 8 on the small diameter side, and the second side plate 8 is supported by the angular rolling bearing 13 so as to be rotatable about the input / output axis X with respect to the housing 2.
- a circular hole 81 is formed at the radial center of the second side plate 8.
- a bearing 14 held by the cylindrical shaft portion 34 of the crankshaft 3 is provided on the inner peripheral surface of the circular hole 81. That is, the second side plate 8 supports the cylindrical shaft portion 34 of the crankshaft 3 so as to be rotatable around the input / output axis X.
- a plurality of holes 82 penetrating in the axial direction are formed in the second side plate 8 at equal intervals in the circumferential direction.
- Each hole 82 is formed coaxially with the hole 41 of the first side plate 4.
- Bolts 15 are inserted into the holes 82 from the left side of FIG.
- the bolt 15 is screwed into the female screw 73 of the press-fit shaft portion 71 of the pin 7.
- the 1st side plate 4, the 2nd side plate 8, and the pin 7 are fixed integrally.
- the operation of the planetary gear reducer 1 will be described.
- the crankshaft 3 as an input shaft rotates around the input / output axis X
- the first and second eccentric cam portions 31 and 32 revolve around the input / output axis X.
- the first and second planetary gears 5 and 6 revolve around the input / output axis X.
- the external gears of the first and second planetary gears 5 and 6 mesh with the internal gear 21. Therefore, the first and second planetary gears 5 and 6 rotate around the central axes Y1 and Y2 while revolving around the input / output axis X.
- the first and second planetary gears 5 and 6 are The crankshaft 3 rotates relative to the number of teeth per rotation (Z2-Z1). That is, the first and second planetary gears 5 and 6 make one revolution revolution with the eccentricity e as a radius and ⁇ (Z2 ⁇ Z1) / Z2 ⁇ revolution rotation with respect to the housing 2. This rotation motion is transmitted to the first and second side plates 4 and 8 as output shafts through the engagement holes 51 and 61 of the first and second planetary gears 5 and 6 and the press-fit shaft portion 71 of the pin 7. .
- the output shaft is the first and second side plates 4 and 8, but the first and second side plates 4 and 8 are fixed, and the housing 2 is rotatably provided. Can be used as an output shaft.
- the crankshaft 3 as the input shaft rotates
- the first and second planetary gears 5 and 6 revolve, but the rotation is restricted.
- the housing 2 as the output shaft rotates.
- the pin 7 is fixed to the first side plate 4 by being press-fitted into the press-fitting hole portion 41 a of the first side plate 4. Since the pins 7 are inscribed in the engagement holes 51 and 61, it is desirable that the central axes of the plurality of pins 7 are parallel to the input / output axis X. That is, it is desired that the parallelism of the plurality of pins 7 matches with high accuracy.
- the end of the press-fit shaft portion 71 of the pin 7 is fastened to the second side plate 8 by a bolt 15. Therefore, it is desirable that the parallelism of the plurality of pins 7 also matches from the viewpoint of assembly. In the above embodiment, the parallelism of the plurality of pins 7 can be matched with very high accuracy. The reason for this will be described in detail below.
- the hole 141 is enlarged, and a tensile stress is generated on the outer periphery of the hole 141. Since the radial thickness of the portion of the disk-shaped member 140 radially outside the hole 141 is thinner than the radial thickness of the radially inner portion, the central axis of the pin 107 is thinner than the central axis of the hole 141. Displaces almost parallel to the outside in the radial direction.
- the outer diameter of the disc-like member 140 is the same in the axial direction, but as shown in the present embodiment, the outer diameter of the first side plate 4 is different in the axial direction. Therefore, as shown in FIG. 5, in the disk-like member 240 having the outer diameter different in the axial direction like the first side plate 4, the hole 241 (shown by a two-dot chain line) having the same inner diameter in the axial direction is used.
- the pin 107 is press-fitted.
- the radially outer portion of the hole 241 has a different radial thickness in the axial direction. That is, in the portion of the disk-like member 240 on the radially outer side of the hole 241, the portion on the large diameter side has higher rigidity than the small diameter side. Therefore, the center position of the pin 107 is displaced more radially outward on the smaller diameter side with a smaller radial thickness than on the larger diameter side with a larger radial thickness. Therefore, the central axis of the pin 107 is inclined with respect to the central axis of the hole 241. Therefore, if the holes 41 of the first side plate 4 have the same inner diameter in the axial direction as shown in FIG.
- each pin 7 (the left side in FIG. 1) Compared to the other axial end portion (the right side in FIG. 1), it is displaced radially outward. Then, as shown in the CAE analysis result of FIG. 6, the central axis of the pin 7 is relative to the central axis of the first side plate 4 so that one axial end portion (left side in FIG. 5) of the pin 7 opens relatively. Inclined.
- the CAE analysis result shown in FIG. 6 is an enlarged display of the displacement amount.
- a press-fitting hole 341 (with a two-dot chain line having the same inner diameter in the axial direction).
- the disk-shaped member 340 includes a small diameter side recess 342 corresponding to the small diameter side recess 41b in the present embodiment.
- the disk-shaped member 340 does not include a recess corresponding to the large-diameter side recess 41c. That is, the press-fitting hole portion 341 is formed between the axial end of the other axial end (the right side in FIGS. 7 and 8) of the disk-like member 340 and the small-diameter side recess 342.
- the radially outer portion of the press-fitting hole portion 341 has a different radial thickness in the axial direction. For this reason, the center position of the pin 107 tends to be displaced more radially outward on the small-diameter side where the radial thickness is thinner than on the large-diameter side where the radial thickness is thick.
- the small-diameter side recess 342 is not in contact with the outer peripheral surface of the pin 107, pressure input by the pin 107 does not act directly. Therefore, the portion of the small diameter side recess 342 is not easily deformed.
- the small-diameter recess 342 causes the small-diameter portion of the disk-like member 340 to prevent the central position of the pin 107 from being displaced radially outward. That is, when the pin 107 is press-fitted into the press-fitting hole portion 341, the amount of deformation of the large-diameter portion of the disk-shaped member 340 in the radial direction and the amount of deformation of the small-diameter side portion of the disk-shaped member 340 in the radial direction. Can be balanced. Therefore, the central axis of the pin 107 can be prevented from being inclined with respect to the central axis of the press-fitting hole portion 341.
- the hole 41 of the first side plate 4 is only the press-fit hole portion 341 and the small-diameter side recess 342 as shown in FIGS. 7 and 8, that is, the hole 41 of the first side plate 4 is the press-fit hole portion 41a and the small-diameter side.
- the central axis of the pin 7 is displaced substantially parallel to the central axis of the press-fit hole 41a. That is, as shown in the CAE analysis result of FIG. 9, the parallelism of the plurality of pins 7 is the same.
- the small diameter side recess 41b the parallelism can be matched with high accuracy without the plurality of pins 7 being relatively inclined. Therefore, it is possible to extend the life by suppressing the uneven wear of the pin 7 and to reduce the transmission torque fluctuation.
- the disk-shaped member 440 has the same shape as the first side plate 4 of the present embodiment. That is, the outer diameter of the disk-shaped member 440 differs in the axial direction, and the disk-shaped member 440 includes a press-fit hole portion 441 corresponding to the press-fit hole portion 41a, a small-diameter side recess 442 corresponding to the small-diameter side recess 41b, and It is assumed that a large-diameter recess 443 corresponding to the large-diameter recess 41c is provided.
- the radially outer portion of the press-fitting hole portion 441 has a different radial thickness in the axial direction. For this reason, the center position of the pin 107 tends to be displaced more radially outward on the small-diameter side where the radial thickness is thinner than on the large-diameter side where the radial thickness is thick.
- the small diameter side recess 442 and the large diameter side recess 443 are not in contact with the outer peripheral surface of the pin 107, the pressure input by the pin 107 does not act directly. Therefore, the small diameter side recess 442 and the large diameter side recess 443 are not easily deformed.
- the small-diameter side recess 442 and the large-diameter side recess 443 act so as to prevent the center position of the pin 107 from being displaced outward in the radial direction. That is, when the pin 107 is press-fitted into the press-fitting hole portion 441, an amount by which the large-diameter side portion of the disk-like member 440 is deformed in the radial direction, and an amount by which the small-diameter side recess 442 portion restricts deformation in the radial direction. Thus, it is possible to balance the amount of the large-diameter side recess 443 with respect to the amount of deformation in the radial direction. Accordingly, the central axis of the pin 107 can be prevented from being inclined with respect to the central axis of the press-fit hole portion 441. When CAE analysis was performed in this case, the same results as in FIG. 9 could be obtained.
- the inclination angle of the pin 107 was analyzed when the depth F5 of the small-diameter side recess 442 and the depth F4 of the large-diameter side recess 443 were changed.
- the horizontal axis represents the ratio (F5 / F4) of the depth F5 of the small diameter side recess 442 to the depth F4 of the large diameter side recess 443, and the vertical axis represents the inclination angle of the pin 107.
- the depth ratio and the inclination angle have a substantially linear relationship such that the inclination angle decreases as the depth ratio increases.
- the depth ratio is around 1.6 and the inclination angle is zero.
- the inclination angle also changes depending on the inner diameters of the small diameter side recess 442 and the large diameter side recess 443. Therefore, by appropriately adjusting the depth and the inner diameter of the small diameter side recess 442 and the large diameter side recess 443, the inclination angle can be made zero.
- the disk-shaped member 540 has a case where the small-diameter side recess 542 is tapered with respect to the disk-shaped member 440 shown in FIG. Also in this case, similarly to FIG. 10, the central axis of the pin 107 can be prevented from being inclined with respect to the central axis of the press-fitting hole portion 441. However, it is necessary to appropriately adjust the depth and the inner diameter of the small diameter side recess 542 and the large diameter side recess 443.
- the disc-like member 640 is elliptical when the small-diameter side recess 642 is viewed from the axial direction with respect to the disc-like member 440 shown in FIG.
- the elliptical long diameter of the small-diameter side recess 642 before the pin 107 is press-fitted is made to coincide with the radial direction of the disk-shaped member 640.
- the short diameter of the elliptical shape of the small diameter side recess 642 before the pin 107 is press-fitted is smaller than the outer diameter of the pin 107.
- the inner peripheral surface of the small-diameter-side recess 642 has a portion where the distance from the center of the press-fit hole portion 441 is longer than the radius of the press-fit hole portion 441, and when the portion is viewed from the axial direction, It is located at least on the radially inner side and the radially outer side of the disk-shaped member 640 with respect to the press-fitting hole portion 441.
- the short diameter part of the small diameter side recess 642 is deformed by press-fitting the pin 107, but the long diameter part of the small diameter side recess 642 is hardly deformed even if the pin 107 is press-fitted. Therefore, as in FIG.
- the central axis of the pin 107 can be prevented from being inclined with respect to the central axis of the press-fit hole portion 441.
- the parallelism can be matched with high accuracy without the plurality of pins 7 being relatively inclined. Therefore, it is possible to extend the life by suppressing the uneven wear of the pin 7 and to reduce the transmission torque fluctuation.
- the first side plate 4 can be a disc-shaped member as shown in FIGS. 7, 12 and 13. Moreover, in this embodiment, although it was set as the structure provided with two planetary gears, it is applicable even if it is 1 piece or 3 or more pieces.
- As the tooth profile of the planetary gear various tooth shapes such as an involute tooth profile and a trochoid tooth profile can be applied, as long as the internal gear and the planetary gear as the external gear can mesh and rotate.
- the end surface of the pin 7 is in contact with the second side plate 8. However, a counterbore hole may be provided in the second side plate 8 and a part of the pin 7 may be inserted.
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Abstract
Description
Claims (7)
- 公転中心が遊星歯車の内側に位置し、軸方向に貫通する複数の係合穴を備える前記遊星歯車と、
キャリアと、
前記キャリアに固定され、前記係合穴に挿通され、前記係合穴との係合により前記キャリアを前記遊星歯車の自転運動に連動させる複数のピンと、
を備える遊星歯車減速機において、
前記キャリアは、円盤板状に形成され、軸方向一方の端面から前記ピンを突出させるように前記ピンを固定した第一側板を備え、
前記第一側板の外径は、前記軸方向一方を小径とし且つ軸方向他方を大径とし、
前記第一側板は、
前記ピンを圧入する圧入穴部と、
前記圧入穴部の前記軸方向一方側に形成され、前記第一側板の前記軸方向一方の端面に開口し、少なくとも一部に前記ピンに非接触の内周面を有する小径側凹所とを備える遊星歯車減速機。 - 請求項1において、
前記小径側凹所の内周面は、前記圧入穴部の中心からの距離が前記圧入穴部の半径より長い部位を有し、
当該部位は、軸方向から見た場合に、前記圧入穴部に対して少なくとも前記第一側板の径方向内側および径方向外側に位置する遊星歯車減速機。 - 請求項2において、
前記小径側凹所の内周面は、全周に亘って前記ピンに非接触となるように形成される遊星歯車減速機。 - 請求項1~3の何れか一項において、
前記圧入穴部は、前記第一側板の前記軸方向他方の端面と前記小径側凹所との軸方向間に形成される遊星歯車減速機。 - 請求項1~3の何れか一項において、
前記第一側板は、
前記圧入穴部の前記軸方向他方側に形成され、前記第一側板の前記軸方向他方の端面に開口し、前記ピンに非接触の内周面を有する大径側凹所を備え、
前記圧入穴部は、前記小径側凹所と前記大径側凹所との軸方向間に形成される遊星歯車減速機。 - 請求項5において、
前記ピンは、圧入軸部と、前記圧入軸部の端部に前記圧入軸部の外接円直径の大きな係止頭部とを備え、
前記大径側凹所は、前記係止頭部を収容すると共に前記係止頭部に対して軸方向に係止する遊星歯車減速機。 - 請求項1~6の何れか一項において、
前記キャリアは、前記第一側板との間に前記遊星歯車を挟むようにして前記第一側板に対向して配置され、前記ピンを固定する第二側板を備える遊星歯車減速機。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180053641.8A CN103201535B (zh) | 2010-11-10 | 2011-09-20 | 行星齿轮减速器 |
JP2012542841A JP5817735B2 (ja) | 2010-11-10 | 2011-09-20 | 遊星歯車減速機 |
EP11840280.9A EP2639477B1 (en) | 2010-11-10 | 2011-09-20 | Planetary gear reducer |
US13/883,064 US8651997B2 (en) | 2010-11-10 | 2011-09-20 | Planetary gear reducer |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010251621 | 2010-11-10 | ||
JP2010-251621 | 2010-11-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012063555A1 true WO2012063555A1 (ja) | 2012-05-18 |
Family
ID=46050710
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/071340 WO2012063555A1 (ja) | 2010-11-10 | 2011-09-20 | 遊星歯車減速機 |
Country Status (5)
Country | Link |
---|---|
US (1) | US8651997B2 (ja) |
EP (1) | EP2639477B1 (ja) |
JP (1) | JP5817735B2 (ja) |
CN (1) | CN103201535B (ja) |
WO (1) | WO2012063555A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014001816A (ja) * | 2012-06-19 | 2014-01-09 | Sumitomo Heavy Ind Ltd | 遊星歯車装置 |
JP2016023695A (ja) * | 2014-07-18 | 2016-02-08 | 日本電産シンポ株式会社 | 減速機 |
CN109477552A (zh) * | 2016-07-30 | 2019-03-15 | 谐波传动***有限公司 | 波动发生器以及波动齿轮装置 |
JP2021028501A (ja) * | 2019-08-09 | 2021-02-25 | 株式会社ニッセイ | 差動減速機及び差動減速機の製造方法 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6723652B2 (ja) * | 2016-09-21 | 2020-07-15 | 住友重機械工業株式会社 | 歯車装置 |
RU180912U1 (ru) * | 2017-07-24 | 2018-06-29 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Чувашский государственный университет имени И.Н. Ульянова" | Редуктор одноступенчатый планетарный |
US10619706B2 (en) * | 2017-08-21 | 2020-04-14 | Shinano Kenshi Kabushiki Kaisha | Speed reducer and motor with speed reducer |
JP7222289B2 (ja) * | 2019-03-29 | 2023-02-15 | 株式会社豊田自動織機 | 軸部材の結合構造及び流体機械 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0560184A (ja) * | 1991-03-19 | 1993-03-09 | Sumitomo Heavy Ind Ltd | トロコイド系歯形内接式遊星歯車構造 |
JPH06241283A (ja) * | 1993-02-12 | 1994-08-30 | Sumitomo Heavy Ind Ltd | 内接噛合遊星歯車構造の角度伝達誤差の低減方法及び内接噛合遊星歯車変速機 |
JP2006263878A (ja) | 2005-03-24 | 2006-10-05 | Sumitomo Heavy Ind Ltd | ロボット手首駆動用動力伝達装置及び動力伝達装置 |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3206992A1 (de) * | 1982-02-26 | 1983-09-08 | Rudolf Braren | Zykloidengetriebe |
SK277969B6 (en) * | 1992-12-31 | 1995-09-13 | Jozef Herstek | Multisatelit gearbox |
JP3634897B2 (ja) * | 1995-07-19 | 2005-03-30 | トヨタ自動車株式会社 | ボルトの嵌合部構造 |
CN2242368Y (zh) * | 1995-12-12 | 1996-12-11 | 北京理工大学 | 内平动齿轮减速器 |
JP4201448B2 (ja) * | 1999-12-28 | 2008-12-24 | 住友重機械工業株式会社 | 内接噛合遊星歯車構造を採用した変速機のシリーズ |
JP3896751B2 (ja) * | 2000-02-23 | 2007-03-22 | 日本精工株式会社 | 車輪用軸受ユニットの製造方法 |
JP2003262256A (ja) * | 2002-03-08 | 2003-09-19 | Sumitomo Heavy Ind Ltd | 揺動内接噛合遊星歯車装置及びその外歯歯車の組込み方法 |
US6851759B2 (en) * | 2002-08-29 | 2005-02-08 | Delphi Technologies, Inc. | Retaining a brake rotor in an vehicle corner apparatus |
US7044563B2 (en) * | 2003-11-07 | 2006-05-16 | Nsk Corporation | Wheel supporting roller bearing unit and manufacturing method of the same |
JP2006038108A (ja) * | 2004-07-27 | 2006-02-09 | Sumitomo Heavy Ind Ltd | 内接噛合遊星歯車減速機及び内接噛合遊星歯車減速装置 |
JP4947884B2 (ja) * | 2004-08-20 | 2012-06-06 | 住友重機械工業株式会社 | 遊星減速機構の遊星回転部材のピンの製造方法 |
JP4818787B2 (ja) * | 2006-04-17 | 2011-11-16 | 住友重機械工業株式会社 | 揺動内接噛合遊星歯車装置 |
US20070269155A1 (en) * | 2006-05-22 | 2007-11-22 | Jtekt Corporation | Rolling bearing device for wheels |
JP4847892B2 (ja) * | 2007-02-22 | 2011-12-28 | 住友重機械工業株式会社 | 揺動内接噛合遊星歯車装置及びその偏心体軸の製造方法 |
JP5440326B2 (ja) * | 2010-03-30 | 2014-03-12 | 株式会社ジェイテクト | 変速歯車装置およびその製造方法 |
-
2011
- 2011-09-20 US US13/883,064 patent/US8651997B2/en not_active Expired - Fee Related
- 2011-09-20 CN CN201180053641.8A patent/CN103201535B/zh not_active Expired - Fee Related
- 2011-09-20 EP EP11840280.9A patent/EP2639477B1/en not_active Not-in-force
- 2011-09-20 WO PCT/JP2011/071340 patent/WO2012063555A1/ja active Application Filing
- 2011-09-20 JP JP2012542841A patent/JP5817735B2/ja not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0560184A (ja) * | 1991-03-19 | 1993-03-09 | Sumitomo Heavy Ind Ltd | トロコイド系歯形内接式遊星歯車構造 |
JPH06241283A (ja) * | 1993-02-12 | 1994-08-30 | Sumitomo Heavy Ind Ltd | 内接噛合遊星歯車構造の角度伝達誤差の低減方法及び内接噛合遊星歯車変速機 |
JP2006263878A (ja) | 2005-03-24 | 2006-10-05 | Sumitomo Heavy Ind Ltd | ロボット手首駆動用動力伝達装置及び動力伝達装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2639477A4 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014001816A (ja) * | 2012-06-19 | 2014-01-09 | Sumitomo Heavy Ind Ltd | 遊星歯車装置 |
JP2016023695A (ja) * | 2014-07-18 | 2016-02-08 | 日本電産シンポ株式会社 | 減速機 |
CN109477552A (zh) * | 2016-07-30 | 2019-03-15 | 谐波传动***有限公司 | 波动发生器以及波动齿轮装置 |
CN109477552B (zh) * | 2016-07-30 | 2021-10-08 | 谐波传动***有限公司 | 波动发生器以及波动齿轮装置 |
JP2021028501A (ja) * | 2019-08-09 | 2021-02-25 | 株式会社ニッセイ | 差動減速機及び差動減速機の製造方法 |
JP7266492B2 (ja) | 2019-08-09 | 2023-04-28 | 株式会社ニッセイ | 差動減速機及び差動減速機の製造方法 |
Also Published As
Publication number | Publication date |
---|---|
JP5817735B2 (ja) | 2015-11-18 |
EP2639477A4 (en) | 2014-11-05 |
EP2639477B1 (en) | 2017-01-04 |
JPWO2012063555A1 (ja) | 2014-05-12 |
CN103201535B (zh) | 2016-09-21 |
EP2639477A1 (en) | 2013-09-18 |
US20130225354A1 (en) | 2013-08-29 |
US8651997B2 (en) | 2014-02-18 |
CN103201535A (zh) | 2013-07-10 |
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