WO2013065444A1 - 遊星歯車組のキャリア構造 - Google Patents

遊星歯車組のキャリア構造 Download PDF

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Publication number
WO2013065444A1
WO2013065444A1 PCT/JP2012/075803 JP2012075803W WO2013065444A1 WO 2013065444 A1 WO2013065444 A1 WO 2013065444A1 JP 2012075803 W JP2012075803 W JP 2012075803W WO 2013065444 A1 WO2013065444 A1 WO 2013065444A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
gear set
planetary gear
carrier structure
shaft
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2012/075803
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
崇志 瀬尾
敦史 月崎
整治 神永
靖 鈴村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
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 Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to US14/353,462 priority Critical patent/US20140274550A1/en
Priority to EP12846132.4A priority patent/EP2778468A4/en
Priority to CN201280052141.7A priority patent/CN103906946A/zh
Publication of WO2013065444A1 publication Critical patent/WO2013065444A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output

Definitions

  • the present invention relates to a carrier structure of a planetary gear set, and more particularly to an improvement proposal of a carrier structure related to gear noise, vibration and durability of the planetary gear set.
  • the carrier structure of a planetary gear set is usually a carrier body in which a pair of opposed plates are directly or indirectly coupled to a common shaft portion and integrated with the carrier body, and the facing surface so as to rotate around an axis that is eccentric from the shaft portion. It consists of a planetary pinion supported by bridging between the plates.
  • the planetary gear set is constructed by meshing the planetary pinion of the carrier structure with a sun gear at the center of the carrier structure and a ring gear at the outer periphery of the carrier structure.
  • one of the sun gear, ring gear, and carrier structure (carrier body) is used as an input element, and rotation is input to this, and the other one is fixed as a reaction force element (or arbitrarily rotated).
  • the remaining one function as an output element and take out rotation from this output element.
  • one plate constituting the carrier body is directly coupled to a common shaft portion, and the other plate is connected to the common plate via the one plate by a support straddled between opposing plates.
  • Indirect coupling to the shaft causes the following problems.
  • the one plate is directly coupled to the shaft portion, it is displaced only by an amount corresponding to the relatively large torsional rigidity of the plate, Since the other plate is indirectly coupled to the shaft portion via the one plate by the support straddled between the opposing plates, the displacement according to the torsional rigidity of the one plate and the rigidity of the support Displacement over a large angle corresponding to the sum of the displacement.
  • the other plate is displaced over a larger angle than the one plate by at least a displacement corresponding to the rigidity of the one plate.
  • the opposing plates are displaced relative to each other by at least a displacement angle corresponding to the rigidity of one of the plates, and the rotation axis of the planetary pinion (the planetary pinion supported) is supported by being bridged between the plates and being rotatably supported.
  • the pinion shaft installed between the plates is inclined in the corresponding direction by an angle corresponding to the relative displacement.
  • the present invention arranges the column on the shaft side so that the displacement of the plate coupled to the shaft through the column is not affected by the displacement of the counterpart plate, but is determined only by the displacement according to the rigidity of the column.
  • An object of the present invention is to propose a carrier structure of a planetary gear set which is improved so as to solve all the above problems by devising.
  • the carrier structure of the planetary gear set according to the invention is constructed as follows.
  • One of the opposed plates is coupled to the shaft portion, and the other plate is characterized by being coupled to the shaft portion via a support column extending from a mutual coupling portion between the one plate and the shaft portion.
  • One of the opposing plates is coupled to the shaft portion, and the other plate is coupled to the shaft portion via a post extending from the mutual coupling portion between the one plate and the shaft portion.
  • the other plate coupled to the shaft portion via the support column is not affected at all by the displacement of the one plate, and is displaced only by an angle corresponding to the rigidity of the support column.
  • the relative displacement between the opposing plates during transmission of the planetary gear set is such that the displacement of the one plate according to its torsional rigidity and the displacement of the other plate according to the rigidity of the column.
  • the amount of displacement corresponds to the difference from the amount. Therefore, the difference between these displacement amounts (relative displacement between the opposing plates) is not affected by the displacement of the one plate. Therefore, the difference between the displacement amounts (opposing plates) without increasing the rigidity of the column. Relative displacement between them) can be reduced.
  • FIG. 1 is a side view showing the overall carrier structure of a planetary gear set according to a first embodiment of the present invention.
  • FIG. 1 shows an outline of the carrier structure in FIG. 1.
  • (a) is a schematic side view of the carrier structure
  • (b) is a cross section of the carrier structure on line BB of (a), and is viewed in the direction of the arrow.
  • FIG. FIG. 5 is a front view of one planetary pinion support plate showing a carrier structure of a planetary gear set according to a second embodiment of the present invention.
  • FIG. 5 is a side view similar to FIG. 1, showing the overall structure of a planetary gear set carrier according to a third embodiment of the present invention.
  • FIG. 5 is a side view similar to FIG. 1, showing the overall structure of a planetary gear set carrier according to a fourth embodiment of the present invention.
  • FIG. 6 is a schematic side view similar to FIG. 2 (a), schematically showing the carrier structure in FIG.
  • FIG. 1 and 2 show a carrier structure of a planetary gear set according to a first embodiment of the present invention
  • FIG. 1 is an overall side view of the carrier structure
  • FIG. 2 is an explanatory diagram showing an outline of the carrier structure. It is a drawing.
  • reference numeral 1 denotes a carrier body.
  • the carrier body 1 is a pair of plates 2 and 3 arranged coaxially and opposed to each other, and the other of the plates 2 and 3 opposite to each other.
  • the plate 3 is composed of support columns 4 for supporting the plate 3 as described later.
  • One of the opposing plates 2 and 3 is directly coupled to the vicinity of the shaft end of the shaft portion 5 common to both opposing plates 2 and 3, that is, the outer periphery near the shaft end on the left side of FIGS. To do.
  • the other plate 3 is connected via a column 4 extending from the shaft end indicated by “5a” in FIG. 2 (b) in the mutual coupling portion between the one plate 2 and the vicinity of the shaft end of the shaft portion 5. Connected to the shaft 5.
  • each column 4 is inclined and extended as clearly shown in FIG. 2 (a) so as to converge toward the shaft end 5a of the shaft portion 5, and finally the free end of each column 4 far from the plate 3 is moved. It merges into the common annular body 4a and integrates it.
  • the plate 3 can be coupled to the shaft portion 5 via the support column 4 extending from the shaft end 5a.
  • the carrier body 1 has a configuration in which the coaxial opposing plates 2 and 3 are individually coupled and integrated with the common shaft portion 5 without using the counterpart plates 3 and 4 respectively.
  • the carrier body 1 as described above is configured so that the planetary pinion 6 as illustrated in FIG. 1 is rotatably supported between the opposing plates 2 and 3 so that the planetary pinion 6 can rotate around the axis eccentric from the shaft portion 5. It is what constitutes.
  • the planetary pinion 6 is a stepped pinion that integrally includes a large-diameter pinion portion 7 and a small-diameter pinion portion 8.
  • each planetary pinion 6 extends in the axial direction between the peripheral portions of the opposing plates 2 and 3, and is supported rotatably between the peripheral portions of the opposing plates 2 and 3.
  • the opposing plates 2 and 3 are respectively provided with the same number of through holes 2a and 3a as the planetary pinions 6, and the pair of through holes 2a and 3a are aligned with each other in the axial direction. 3 is arranged between the columns 4 adjacent in the circumferential direction.
  • a pair of through holes 2a and 3a aligned with each other in the axial direction are provided by inserting pinion shafts (not shown), and the planetary pinions 6 are rotatably supported on the pinion shafts, respectively.
  • the planetary pinion 6 is supported on the (opposite plates 2 and 3).
  • the carrier structure composed of the carrier body 1 and the planetary pinion 6 for the planetary gear set, for example,
  • the large-diameter pinion portion 7 of the planetary pinion 6 is engaged with a sun gear (not shown) at the center of the carrier structure, and the small-diameter pinion portion 8 is engaged with an inner peripheral tooth of a ring gear (not shown) at the outer periphery of the carrier structure.
  • one of the sun gear, ring gear, and carrier structure (carrier body 1) is used as an input element, and rotation is input thereto, and the other one is fixed as a reaction force element (or optional).
  • the remaining one functions as an output element, and the rotation is extracted from this output element.
  • the relative displacement between the opposing plates 2 and 3 during transmission of the planetary gear set is such that the displacement of one plate 2 according to its torsional rigidity and the other plate 3 according to the rigidity of the column 4
  • the displacement amount corresponds to the difference from the displacement amount to be displaced. Therefore, the difference between these displacement amounts (relative displacement between the opposing plates 2 and 3) will not be affected by the displacement of one plate 2, and therefore, between the displacement amounts without increasing the rigidity of the column 4.
  • the difference (relative displacement between the opposing plates 2 and 3) can be reduced.
  • the rotation axis of the planetary pinion 6 supported by the bridge between the opposed plates 2 and 3 so as to be rotatable is directed in the corresponding direction according to the relative displacement between the opposed plates 2 and 3 during transmission of the planetary gear set. Tilt is suppressed. Moreover, this effect can be achieved almost without relying on the increase in the rigidity of the support column 4, and without increasing the weight and cost due to the increase in the rigidity of the support column 4, and without reducing the transmission efficiency (increasing energy loss). The effect of can be produced.
  • the planetary pinion 6 has a small inclination due to the relative displacement between the opposing plates 2 and 3, and in this embodiment, the planetary pinion 6 and the gear meshing with the planetary pinion 6 (usually as described above, the sun gear and the ring gear). ) Without causing a gear meshing failure, It is possible to solve the above-mentioned problems that the planetary gear set generates a large gear noise and vibration, and the transmission efficiency and durability are lowered due to a poor tooth contact.
  • the processing of the support column end part is within a small diameter range.
  • the time required for manufacturing the carrier body (carrier structure) can be shortened and the cost can be reduced.
  • one plate 2 is directly coupled to the vicinity of the shaft end (5a) of the shaft portion 5, and the other plate 3 is connected to the shaft at the mutual coupling portion between the one plate 2 and the vicinity of the shaft end (5a).
  • the shaft portion 5 is coupled to the shaft portion 5 via the support column 4 extending from the end 5a.
  • FIG. 2 (a) it is possible to make the structure in which the shaft portion 5 hardly extends in the carrier body 1, as in the conventional structure.
  • the installation space of the gear accommodated in the carrier body 1 is easily secured as before, and thus the various functions and effects described above are made without deteriorating the ease of designing the carrier structure and the assembling workability. Can be achieved.
  • the support column 4 is provided integrally with the other plate 3, and the free end far from the other plate 3 is provided at the position of the shaft portion 5 in the mutual coupling portion between the one plate 2 and the shaft portion 5.
  • FIG. 3 shows a carrier structure according to a second embodiment of the present invention.
  • the configuration is basically the same as that of the first embodiment described above with reference to FIGS. 1 and 2, but the plate 2 directly coupled to the shaft portion 5 is arranged between the support through holes 2 a of the planetary pinion 6.
  • the region 2b has a shape cut out in a fan shape.
  • the notch 2b is not limited to the above fan shape and size, and can be arbitrarily selected as long as the planetary pinion 6 can be supported.
  • the notch 2b reduces the torsional rigidity of the plate 2, that is, the circumferential rigidity of the plate portion 2c in which the planetary pinion support through-hole 2a is formed, and can have the following effects.
  • the relative displacement of the opposing plates 2 and 3 during the transmission of the planetary gear set is the same as the displacement of the plate 2 depending on its torsional rigidity as described in the first embodiment, and the plate 3 Is determined by the difference from the displacement amount that is displaced according to the rigidity of the column 4.
  • the torsional rigidity of the plate 2 is usually higher than the rigidity of the column 4, and if the design is not devised, the relative displacement of the opposing plates 2 and 3 (the inclination of the planetary pinion 6) according to the difference in rigidity is Even if it can be suppressed within the allowable range, it is difficult to obtain a minute value near 0 or 0.
  • the torsional rigidity of the plate 2 is lowered by setting the notch 2b, so that the torsional rigidity of the plate 2 can be close to or the same as the rigidity of the column 4. Therefore, the difference between the displacement amount at which the plate 2 is displaced according to its torsional rigidity and the displacement amount at which the plate 3 is displaced according to the rigidity of the support column 4 can be made as close to 0 as possible.
  • the relative displacement (the inclination of the planetary pinion 6) can be almost eliminated.
  • the effect of the first embodiment of preventing the occurrence of gear meshing failure can be further ensured, and the planetary gear set generates a large gear noise and vibration, or the tooth contact. It is possible to almost completely avoid the problem that the transmission efficiency and durability are lowered due to the failure of the above.
  • FIG. 4 shows a carrier structure according to a third embodiment of the present invention.
  • the configuration is basically the same as that of the first embodiment described above with reference to FIGS. 1 and 2 except that the plate 2 directly coupled to the shaft portion 5 is joined to the free end of each column 4 far from the plate 3.
  • the stay 9 extending between the common annular body 4a and the outer peripheral portion of the plate 2 is also coupled to a location on the shaft portion 5 in the mutual coupling portion between the plate 2 and the shaft portion 5.
  • the number of stays 9 is the same as that of the columns 4 and is arranged at the same position in the circumferential direction as these columns 4. Then, the free end of each stay 9 far from the plate 2 is extended toward the free end of the support column 4 at the same position in the circumferential direction and is brought into contact with the free end of the support column 4.
  • the free ends of the stays 9 are coupled to locations on the shaft portion 5 in the mutual coupling portion between the plate 2 and the shaft portion 5, respectively. Further, the end portions of the stay 9 close to the plate 2 are respectively coupled to or integrated with the outer peripheral portion of the plate 2.
  • the plate 5 directly coupled to the shaft portion 5 is connected via the stay 9 extending from the mutual coupling portion (annular body 4a) between the plate 2 and the shaft portion 5. But because it is connected to the shaft part 5, The torsional rigidity of the opposing plates 2 and 3 during transmission of the planetary gear set can be made closer to that of the first embodiment, and the relative displacement between the opposing plates 2 and 3 can be further reduced. Therefore, the inclination of the rotation axis of the planetary pinion 6 that is supported by the bridge between the opposing plates 2 and 3 so as to be rotatable can be further effectively suppressed, and the above-described operational effects of the first embodiment become more remarkable. .
  • the end portion of the stay 9 on the plate 2 side is coupled to or integrated with the outer peripheral portion of the plate 2, and the free end of each stay 9 is extended toward the free end of the column 4.
  • the arrangement of the stay 9 is the same as the arrangement of the support 4, and the rigidity of the stay 9 against the torsional reaction force received during transmission of the planetary gear set is the same as that of the support 4, and the above-mentioned effects are more remarkable. Can be.
  • ⁇ Configuration> 5 and 6 show a carrier structure according to a fourth embodiment of the present invention.
  • this embodiment it is basically configured in the same manner as the third embodiment described above with reference to FIG. 4, but the free end of the stay 9 and the free end of the column 4 are coupled at an intermediate position between the plates 2 and 3, Accordingly, the length of the stay 9 and the length of the support column 4 are configured to be substantially the same.
  • the length of the stay 9 and the length of the support 4 are substantially the same, so that the rigidity of the stay 9 against the torsional reaction force received during transmission of the planetary gear set is the same as that of the support 4. It will be something. Therefore, the inclination of the rotation axis of the planetary pinion 6 that is supported by the bridge between the opposing plates 2 and 3 so as to be rotatable can be suppressed more effectively than in the third embodiment, and the above-described effects can be made more remarkable. obtain.
  • the other plate 3 is coupled to the shaft portion 5 with a support column 4 extending from a location on the shaft portion 5 in the mutual coupling portion between the one plate 2 and the shaft portion 5.
  • the other plate 3 may be coupled to the shaft portion 5 with a support column 4 extending from a position on the plate 2 in the mutual coupling portion between the one plate 2 and the shaft portion 5.
  • the same effect can be achieved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
PCT/JP2012/075803 2011-11-01 2012-10-04 遊星歯車組のキャリア構造 Ceased WO2013065444A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US14/353,462 US20140274550A1 (en) 2011-11-01 2012-10-04 Carrier structure for planetary gear set
EP12846132.4A EP2778468A4 (en) 2011-11-01 2012-10-04 CARRIER STRUCTURE FOR PLANETARY GEARBOX
CN201280052141.7A CN103906946A (zh) 2011-11-01 2012-10-04 行星齿轮组的齿轮架构造

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011-239923 2011-11-01
JP2011239923 2011-11-01
JP2012164700A JP5936472B2 (ja) 2011-11-01 2012-07-25 遊星歯車組のキャリア構造
JP2012-164700 2012-07-25

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WO2013065444A1 true WO2013065444A1 (ja) 2013-05-10

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PCT/JP2012/075803 Ceased WO2013065444A1 (ja) 2011-11-01 2012-10-04 遊星歯車組のキャリア構造

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US (1) US20140274550A1 (enExample)
EP (1) EP2778468A4 (enExample)
JP (1) JP5936472B2 (enExample)
CN (1) CN103906946A (enExample)
WO (1) WO2013065444A1 (enExample)

Families Citing this family (7)

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Publication number Priority date Publication date Assignee Title
US9410611B2 (en) * 2014-01-06 2016-08-09 Hamilton Sundstrand Corporation Carrier shaft set
FR3068303A1 (fr) * 2017-06-29 2019-01-04 Valeo Systemes Thermiques Actionneur pour un dispositif de regulation d'entree d'air pour vehicule automobile
US10760677B2 (en) * 2018-01-31 2020-09-01 Pratt & Whitney Canada Corp. Epicyclic gear train with balanced carrier stiffness
CN108190743B (zh) * 2018-02-11 2023-12-26 上海振华重工(集团)股份有限公司 一种滑轮支座
JP7145194B2 (ja) * 2020-12-14 2022-09-30 川崎重工業株式会社 遊星歯車減速装置
DE102022109201A1 (de) * 2022-04-14 2023-10-19 Neugart Gmbh Umlaufgetriebe
JP2025011755A (ja) * 2023-07-11 2025-01-24 ナブテスコ株式会社 減速機

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JPS61161453U (enExample) * 1985-03-29 1986-10-06
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JP2001200897A (ja) * 1999-11-12 2001-07-27 Otics Corp プラネタリギヤ装置
JP2002364740A (ja) * 2001-06-08 2002-12-18 Hino Motors Ltd プラネタリキャリヤ及びその製造方法
JP2005048950A (ja) * 2003-07-29 2005-02-24 Zahnradfab Friedrichshafen Ag 遊星歯車装置用遊星キャリヤの案内プレート結合体

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JPS61161453U (enExample) * 1985-03-29 1986-10-06
JPH07208585A (ja) 1994-01-12 1995-08-11 Jatco Corp 遊星歯車装置のキャリヤ装置
JP2001200897A (ja) * 1999-11-12 2001-07-27 Otics Corp プラネタリギヤ装置
JP2002364740A (ja) * 2001-06-08 2002-12-18 Hino Motors Ltd プラネタリキャリヤ及びその製造方法
JP2005048950A (ja) * 2003-07-29 2005-02-24 Zahnradfab Friedrichshafen Ag 遊星歯車装置用遊星キャリヤの案内プレート結合体

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Title
See also references of EP2778468A4 *

Also Published As

Publication number Publication date
US20140274550A1 (en) 2014-09-18
EP2778468A1 (en) 2014-09-17
JP2013117303A (ja) 2013-06-13
CN103906946A (zh) 2014-07-02
JP5936472B2 (ja) 2016-06-22
EP2778468A4 (en) 2015-07-22

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