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PLANETARY GEAR DEVICE NEW

外国特許コード F180009521
整理番号 (S2017-0289-N0,S2017-0285-N0)
掲載日 2018年11月2日
出願国 世界知的所有権機関(WIPO)
国際出願番号 2018JP001290
国際公開番号 WO 2018135552
国際出願日 平成30年1月18日(2018.1.18)
国際公開日 平成30年7月26日(2018.7.26)
優先権データ
  • 20170-008496 JP
  • 特願2017-008497 (2017.1.20) JP
発明の名称 (英語) PLANETARY GEAR DEVICE NEW
発明の概要(英語) A planetary gear device (30) equipped with a 3K-type compound planetary gear mechanism. The compound planetary gear mechanism is equipped with a first internal gear (I1), a second internal gear (I2), an external gear (S), a first planetary gear (PI), a second planetary gear (P), and a carrier (H). The first planetary gear (PI) is equipped with an external gear part (PI2) that engages the first internal gear (I1) and has a diameter greater than the radius of the first internal gear (I1), and an internal gear part (PI1) that engages the external gear (S). The second planetary gear (P) engages the second internal gear (I2) and has a diameter greater than the radius of the second internal gear (I2). The first planetary gear (PI) and the second planetary gear (P) are formed so as to synchronize their rotational speeds.
従来技術、競合技術の概要(英語) BACKGROUND ART
Industrial machinery, vehicle, robot, such as OA equipment such as various kinds of drive system or power transmission system (speed increase) constitutes the apparatus, a sun gear, planetary gear, internal gear, and the carrier is comprised of a planetary gear mechanism has been known (Non-Patent Document 1: 'gear applications the design of the mechanism').The planetary gear mechanism, other than the speed of the device, and a relatively high reduction ratio can be realized, compared with the speed reduction ratio and the torque transmission mechanism or the structure is relatively compact.In addition, the planetary gear mechanism, the input shaft and output shaft are arranged coaxially and it is possible, a wide variety of the drive device or a driving system of the power transmission device or the power transmission system has been widely put into practical use.
The planetary gear mechanism, for example, the simple planetary gear mechanism, a Ravigneaux planetary gear mechanism, a complex planetary gear mechanism, such as a strange and known planetary gear mechanism.In general, high efficiency, high torque, and a high reduction ratio gear mechanism, a variety of industrial equipment or the like since there is a demand for many consumer devices, the other of the planetary gear mechanism, the wave motion gear mechanism such as a cycloid gear mechanism (harmonic gear) and the gear mechanism has also been developed, been put into practical use.
The reduction ratio is obtained by the various gear mechanism, is generally believed as follows. (Step 1) the simple planetary gear mechanism: reduction ratio (step 1) about a Ravigneaux planetary gear mechanism 1/4-1/10: reduction ratio of about 1/10 complex planetary gear mechanism: strange about 1/100 reduction ratio of the planetary gear mechanism: reduction ratio of approximately 1/100 the wave motion gear mechanism: reduction ratio of the gear mechanism of a cycloid 1/30-1/200: 1/60-1/200 reduction ratio
In such a wide variety of gear mechanism, a strange planetary gear mechanism, the wave motion gear mechanism, and the cycloid gear mechanism, a special structure using relatively has a gear configuration, and reduction of the productivity, it is difficult to improve the degree of freedom in design of, the difficulty of improving the structural strength, the problem of expensive manufacturing cost or the like is likely to occur.Therefore, a general-purpose using a simple spur gear of the planetary gear mechanism is a planetary gear mechanism and the like, productivity, manufacturing cost, degree of freedom in design, and the like from the viewpoint of the desirable structural strength.In particular, a composite combination of a plurality of planetary gear mechanism is a planetary gear mechanism, as described above, since the reduction ratio of about 1/100 can be realized, requires a high reduction ratio gear of the planetary gear set may be preferably adopted as a mechanism considered.
In the planetary gear mechanism, in a plurality of meshing with the gear and sun gear of the planetary gears are arranged in the circumferential direction and therefore, the planetary gear mechanism is the mechanism for establishing the constraints or as design conditions, the coaxial condition, the condition for assembling, and the adjacent condition is generally contemplated that the condition 3.Coaxial conditions, the sun gear, internal gear and the carrier is located coaxially with the axis of the condition.Assembly conditions, a plurality of evenly spaced planet gears meshing with the sun gear and ring gear within the condition.Adjacent condition, the planetary gear does not interfere with each other adjacent the condition.
Fig. 24-is Fig. 27, the sun gear, planetary gear, internal gear, and the carrier of the planetary gear mechanism composed of a conventional conceptual view showing the structure of the present invention.
Fig. 24 is, the configuration of the simple planetary gear mechanism are shown.The number of teeth of sun gear S Zs, Zp the number of teeth of the planetary gear set P, the number of teeth of the gear in the Zi I, N (a natural number) the number of planetary gear P and sets respectively, I is fixed to the gear, the sun gear S is set to the input shaft, output shaft is set to be the carrier H, the reduction ratio of the planetary gear mechanism, the coaxial condition, the condition for assembling, and the adjacent condition is, represented by the following mathematical formula (1).It should be noted that, in Fig. 24, the code K is, the sun gear S and the internal gear in a broad sense means including I and the sun gear, the planetary gear mechanism shown in Fig. 13, the most common 2K-H belonging to the type.
Fig. 25 is, a Ravigneaux type planetary gear mechanism shown in the configuration.The number of teeth of sun gear S Zs, P1 outward in the radial direction of the number of teeth of the planetary gear Zp1, planetary gear P2 radially inward of the number of teeth Zp2, the number of teeth of the internal I Zi, the planetary gear P1, P2 and 2N are set in the number, I is fixed to the gear, the sun gear S is set to the input shaft, output shaft is set to be the carrier H, the reduction ratio of the planetary gear mechanism, the coaxial condition, the condition for assembling, and the adjacent condition, represented by the following mathematical formula (2).In addition, a Ravigneaux type planetary gear mechanism, the first planetary gear P2 of the stage 1 by inverting the rotation direction, and a carrier H as a reference, the sun gear S I and the gear rotates in the same direction so that, in the following equation (2) in the denominator of the reduction ratio, the number of teeth of sun gear S is applied to the Zs to the sign is reversed.In addition, adjacent condition, defined by a plurality of equations, this is, each equation can be adapted to any of the adjacent means that the condition is satisfied.In the equation (2) below, the angle φ is, the sun gear S and the center axis of the planetary gear P1 and a straight line connecting the central axis of, the sun gear S and the center axis of the planetary gear P2 and a straight line connecting the center axis of the angled intersection.
Fig. 24 and the planetary gear train is shown in Fig. 25, in the same plane of the gear train is constituted by, as described above, the rotation axis direction within the plane spaced by a distance from each of the planetary gear mechanism and the planetary gear mechanism is disposed in the composite, the simple planetary gear mechanism and the Ravigneaux planetary gear mechanism as compared to, in order to achieve a high reduction ratio gear mechanism can be used preferably considered.However, in a complex planetary gear mechanism, an epicyclic gear mechanism are arranged in a coaxial condition, the condition for assembling, and each of the adjacent condition satisfied Therefore, the above-described design conditions are satisfied can be realized in a high reduction ratio on the, in practice, very difficult.Therefore, the planetary gear mechanism to reduce the design conditions of the intended configuration of the composite planetary gear mechanism, for example, in JP-1-3 has been proposed.
Patent Document 1 (PCT International Application Publication Nos WO2007-017935) composite planetary gear mechanism is described, the sun gear, planetary gear, and the internal gear having a set of the planetary gear mechanism 2 is provided.This composite planetary gear mechanism is, each of the planetary gear mechanism and the planetary gear are integrally and coaxially, the dislocation of the use by a structure in which design conditions are relaxed.Patent Document 2 (Japanese Patent Application JP-2008-275112) composite planetary gear mechanism is described, the sun gear, planetary gear, and the internal gear having a set of the planetary gear mechanism 2 and connected to, the planetary gears can be disposed on the non-axisymmetric having a configuration in which the design condition may be alleviated.
Fig. 26 is, in Patent Document 3 (PCT International Application Publication Nos WO2012-060137) composite planetary gear mechanism as described in the conceptual view of the configuration.Patent Document 3 is a complex planetary gear mechanism, as shown in Fig. 26, the sun gear of the planetary gear mechanism S1 a set of 2, and S2 are interconnected, each planetary gear P1 by a common carrier H, the spindle and the bearing P2 is supported by the bearing or independently, to improve the degree of freedom in the design and configuration.
The above-described various forms of the planetary gear mechanism, may be any, typically with a gear in the planetary gear mechanism has a structure, as other configurations of the planetary gear mechanism, as shown in Fig. 26, an inner gear of the planetary gear mechanism is not provided in the form of complex has been known.
Composite planetary gear mechanism is shown in Fig. 27, Ravigneaux type planetary gear mechanism shown in Fig. 25 the internal gear S2 (Fig. 25) sun gear I (Fig. 27) is replaced by a planetary gear mechanism may be regarded as.In the planetary gear mechanism shown in Fig. 27, the sun gear S1, is S2, the carrier rotates in the opposite direction H as a reference.
Zs1 The number of teeth of sun gear S1, the number of teeth of sun gear S2 Zs2, Zp1 the number of teeth of the planetary gear P1, the number of teeth of the planetary gear P2 Zp2, the planetary gear P1, the number of set 2N and P2, fixed to the sun gear S2, sun gear S1 is set to the input shaft, output shaft is set to be the carrier H, the reduction ratio of the planetary gear mechanism, the coaxial condition, the condition for assembling, and the adjacent condition, represented by the following mathematical formula (3).In addition, adjacent condition, as described below is defined by a plurality of equations, this is, for each expression should be adapted to any of the means.In the equation (3) below, the angle φ is, the sun gear S1, planetary gear S2 and the center axis of the straight line connecting the center axis of the P1, the sun gear S1, planetary gear S2 and the center axis of the central axis P2 intersects a straight line connecting the angle.
In addition, a modification of the planetary gear mechanism shown in Fig. 27, the shared central axis 2 and two planet gears has a different number of teeth of the planetary gear mechanism including a, Patent Document 4 (Japanese Patent Application Laid-Open 7-301288) and the like are described.
  • 出願人(英語)
  • ※2012年7月以前掲載分については米国以外のすべての指定国
  • NATIONAL UNIVERSITY CORPORATION YOKOHAMA NATIONAL UNIVERSITY
  • 発明者(英語)
  • Yasutaka Fujimoto
国際特許分類(IPC)
指定国 National States: AE AG AL AM AO AT AU AZ BA BB BG BH BN BR BW BY BZ CA CH CL CN CO CR CU CZ DE DJ DK DM DO DZ EC EE EG ES FI GB GD GE GH GM GT HN HR HU ID IL IN IR IS JO JP KE KG KH KN KP KR KW KZ LA LC LK LR LS LU LY MA MD ME MG MK MN MW MX MY MZ NA NG NI NO NZ OM PA PE PG PH PL PT QA RO RS RU RW SA SC SD SE SG SK SL SM ST SV SY TH TJ TM TN TR TT TZ UA UG US UZ VC VN ZA ZM ZW
ARIPO: BW GH GM KE LR LS MW MZ NA RW SD SL SZ TZ UG ZM ZW
EAPO: AM AZ BY KG KZ RU TJ TM
EPO: AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
OAPI: BF BJ CF CG CI CM GA GN GQ GW KM ML MR NE SN ST TD TG
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