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PLANETARY GEAR DEVICE AND PROGRAM FOR DESIGNING PLANETARY GEAR DEVICE 新技術説明会

外国特許コード F180009317
整理番号 (S2016-0784-N0)
掲載日 2018年1月24日
出願国 世界知的所有権機関(WIPO)
国際出願番号 2017JP021022
国際公開番号 WO 2017213151
国際出願日 平成29年6月6日(2017.6.6)
国際公開日 平成29年12月14日(2017.12.14)
優先権データ
  • 特願2016-112434 (2016.6.6) JP
発明の名称 (英語) PLANETARY GEAR DEVICE AND PROGRAM FOR DESIGNING PLANETARY GEAR DEVICE 新技術説明会
発明の概要(英語) This planetary gear device is made by combining a plurality of planetary gear mechanisms, wherein the planetary gear device has first and second planetary gear mechanisms that share a carrier, each planetary gear mechanism is configured from an internal gear (Ik) (k being an integer of 2 or greater) and a planetary gear (Pk) that meshes with the internal gear (Ik) and circumferentially orbits the internal gear, the planetary gear (Pk) of each planetary gear mechanism comprises a spur gear in the form of an external gear, the planetary gears (Pk) of the planetary gear mechanisms either share a center shaft or are linked integrally at the center shafts so as to integrally rotate about a common rotational center axis line, or are integrated together so as to integrally rotate about a common rotational center axis line, and the number of teeth (zp1) of a first planetary gear constituting the first planetary gear mechanism is different from the number of teeth (zp2) of a second planetary gear constituting the second planetary gear mechanism. The number of teeth of the internal gear (I1) is (zi1), the number of teeth of the internal gear (I2) is (zi2), the profile shift coefficient of the first planetary gear is (xp1), the profile shift coefficient of the internal gear that meshes therewith and constitutes the first planetary gear mechanism is (xi1), the profile shift coefficient of the second planetary gear is (xp2), the profile shift coefficient of the internal gear that meshes therewith and that constitutes the second planetary gear mechanism is (xi2), the motive power transmission efficiency of the planetary gear device including the profile shift coefficients (xp1, xi1, xp2, xi2) is (η), the profile shift coefficient of the internal gear (I1) is (xi1), the profile shift coefficient of the internal gear (I2) is (xi2), and the profile shift coefficients have a relationship of a combination of values selected from among a combination of profile shift coefficients in which the motive power transmission efficiency η is maximal or submaximal within an allowable range of design specifications given in advance.
特許請求の範囲(英語) [claim1]
1. A plurality of planetary gear mechanism including a combination of a planetary gear device, sharing the first carrier and the first and second planetary gear mechanism of the 2 and 1, each of the planet gear mechanism includes, and the internal gear Ik(kis an integer of 2 or more) and, said internal gear Ikand engaged with the inner gear of the planet gear to revolve around the circumferential direction Pkcomposed and, through a respective planetary gear of the planetary gear mechanism Pkis, and the spur gear of the gear, the planetary gear mechanism through a respective planetary gear Pkis, the planetary gear apparatus 2 in order to constitute the entire stage gear mechanism has, as a common rotational center axis of the central axis so as to rotate integrally share between central axes or integrally connected to, or, as a common rotational center axis so as to rotate integrally with the integrated with one another and, wherein the first planetary gear mechanism of the 1 to the number of teeth of the first planetary gear 1 (zp1) 、2 constituting the first planetary gear mechanism of the first number of teeth of the planetary gear 2 (zp2) is varied depending on the planetary gear unit and, the internal gear I1z is the number of teeth ofi1and, said internal gear I2z is the number of teeth ofi2and, wherein the first planetary gear butatrienic 1 x coefficientp1、engaged 1 constituting the first planetary gear mechanism of the dislocation of the inner gear-x coefficienti1、2 the first planetary gear butatrienic x coefficientp2、engaged 2 constituting the first planetary gear mechanism of the dislocation of the inner gear-x coefficienti2、dislocations coefficient xp1、xi1、xp2、xi2planetary gears comprising the power transmission efficiency is η and the device, said internal gear I1butatrienic x coefficienti1and, said internal gear I2butatrienic x coefficienti2and, wherein the dislocation coefficient, given in advance within a permissible range of design specifications, η is power transfer efficiency becomes maximum or quasi-maximizing the dislocations in the combination of the coefficients are selected from a combination of the values in a relation of the planetary gear unit.
[claim2]
2. The number of teeth (zs1) of the second sun gear S1 and, the planetary gear PkNumRnd, sun gear S1 engaged with, said sun gear S1 butatrienic coefficient xs1and, the power transmission efficiency η is, of the number of teeth (zs1、zp1、zp2、zi1、zi2) and dislocations coefficient (xs1、xp1、xp2、xi1、xi2) combination to the case, the of the number of teeth (zs1、zp1、zp2、zi1、zi2) and dislocations coefficient (xs1、xp1、xp2、xi1、xi2) in the combination of the power transmission efficiency η are selected from a continuous or quasi-maximizing combination of the maximum value, a planetary gear apparatus according to claim 1.
[claim3]
3. In which the power transmission efficiency η is, of the number of teeth (zp1、zp2、zi1、zi2) and dislocations coefficient (xp1、xp2、xi1、xi2) combination to the case, the teeth of said gears number (zp1、zp2、zi1、zi2) and dislocations coefficient (xp1、xp2、xi1、xi2) and the central axis distance coefficient (Xc) in the combination of the draw from the power transmission efficiency η is maximized or near the maximum value of the combination thereof, or, of the number of teeth (zp1、zp2、zi1、zi2) 、dislocations coefficient (xp1、xp2、xi1、xi2) 、and wherein the first 1 view of the planetary gear mechanism with respect to the first 2 view of the planetary gear mechanism a distance between the first transposition amount about a central axis distance coefficient (Xc) combination to the case, the teeth of said gears number (zp1、zp2、zi1、zi2) and dislocations coefficient (xp1、xp2、Xc) from the selected images from among the combination of the power transmitting efficiency η is maximized or a combination of the maximum value of the level, the planetary gear unit according to claim 1.
[claim4]
4. The power transmission efficiency η (xp1, xi1, xp2, xi2, Xc) is, η0=η1, η2and, the number of teeth zikgears of the gear Ikof the power transmission efficiency ηkis, according to the following formula (number 1) represented in,
Formula (number 1) in, the subscript k of each of the planetary gear mechanism is a gear pair, said μksaid inner gear Ikand the planetary gear Pkand coefficient of friction between the, ε The0k2 is one of said inner gear Ikand the planetary gear Pkmeshing rate, as represented by the formula (number 1) in, ε0kCosslett (number 2) represented in,
Formula (number 1) in, ε The1kunapproachable and the engagement rate, wherein the ε2kto keep away from him and is engageable with the ratio, expressed by the formula (number 2) in, ε1k、ε2kCosslett (number 3) represented by,
in formula (number 1), a TheWkmeshing is pressure angle, a Thezpk、a Thezikand tooth tip pressure angle respectively, according to the following equation represented by (number 4),
in formula (number 4), the rcsaid inner gear Ikand planetary gear Pkdenotes a distance between the center axis of the, m Thekand modules, wherein the dislocation is a reference pressure angle and before, wherein the daik、d Theapkrespectively, said internal gear Ikand planetary gear Pkaddendum circle of the diameter, d Thebik、d Thebpkrespectively, said internal gear Ikand the planetary gear Pkreference circle of a diameter, represented by the following formula (5 number),
(number 5) in the formula, wherein the coefficient xinsaid gear pair P1, I1 and the gear pair P2, I2 for adjusting the distance between the axes of the dislocation coefficient and, wherein the coefficient xc1、xc2respectively, wherein the gear pair P1, I1 and the gear pair P2, I2 the distance between the axes of the dislocation quantity Xccaused by changing only each gear pair indicating the impact of dislocation coefficients, wherein the dislocation coefficient xp1、xp2、xi1、xi2in between, the following formula (6 number) and a relation of,
Formula (number 6) in, the inv (a) is, in the involute function, the planetary gear unit according to claim 3.
[claim5]
5. Said planetary gear mechanism has, in a configuration that does not have the sun gear, claim 1, 3, 4 to 1 any one of the planetary gear unit.
[claim6]
6. Said planetary gear mechanism has, configured by including a sun gear, the planetary gear unit according to claim 2 or claim 1.
[claim7]
7. I and the internal gear, the gear meshes with the gear I and said planetary gear revolving movement in the circumferential direction of Pk and, the number of teeth zs1and sun gear S1, a, 1 sharing the first carrier of the planetary gear mechanism and the second planetary gear mechanism 2, 1 of the first planetary gear mechanism 1 z is the number of teeth of the first planetary gearp1、2 of the first planetary gear mechanism 2 z is the number of teeth of the first planetary gearp2、1 x coefficient of the first planetary gear butatrienicp1、1 first engaged gear of the planetary gear mechanism butatrienic coefficient xi1、2 x coefficient of the first planetary gear butatrienicp2、2 first engaged gear of the planetary gear mechanism butatrienic coefficient xi2、dislocations coefficient xp1、xi1、xp2、xi2of the planetary gear unit including a power transmission efficiency is η and, wherein the coefficient of x S1 of the second sun gear butatrienics1of the planetary gear to design the device in the computer, is capable of generating a number of gear (zs1、zp1、zp2、zi1、zi2) generating set, the gear number generated by the (zs1、zp1、zp2、zi1、zi2) from the set of setting a first set of, vector x=(xs1、xp1、xp2、xi1、xi2) and for providing an initial value, the gradient vector v=(∂η / ∂xs1、∂η / ∂xp1、∂η / ∂xp2、∂η / ∂xi1、∂η / ∂xi2) and a step of obtaining, v, q 0 and q satisfy>vector selecting step, the amount of update of the vector x γ q is small enough and determining whether or not, wherein the amount of update γ q has not become sufficiently small when it is determined, adding to the vector x γ q and update step, the amount of update γ q is sufficiently small and if it was determined that is, the number of said gears (zs1、zp1、zp2、zi1、zi2) dislocations and a set of coefficients (xs1、xp1、xp2、xi1、xi2) combination of, wherein the power transmitting efficiency η becomes a maximum or near maximum butatrienic and selects a combination of the coefficients, in which the power transmission efficiency η is the maximum number of said gears is selected (zs1、zp1、zp2、zi1、zi2) dislocations and a set of coefficients (xs1、xp1、xp2、xi1、xi2) and outputting a combination of, executing a design program of the planetary gear unit.
[claim8]
8. I and the internal gear, the gear engaged with the internal gear and said I in the circumferential direction of the planetary gear Pk and revolving movement, which is composed of, 1 sharing the first carrier of the planetary gear mechanism and the planetary gear mechanism of the 2, wherein the first planetary gear mechanism of the 1 to 1 z is the number of teeth of the first planetary gearp1、2 constituting the planetary gear mechanism of the first 2 is the number of teeth of the first planetary gear set zp2、x 1 wherein the first planetary gear butatrienic coefficientp1、engaged planetary gear mechanism of the first gear 1 constituting the x coefficient butatrienici1、x 2 wherein the first planetary gear butatrienic coefficientp2、engaged planetary gear mechanism of the first gear 2 constituting the x coefficient butatrienici2、dislocations coefficient xp1、xi1、xp2、xi2of the planetary gear unit including a power transmission efficiency is η and, wherein the first planetary gear mechanism of the 1 2 and the second distance between the axes of the planetary gear mechanism of dislocation amount coefficient of the distance between the axes central Xcdesign in a computer of the planetary gear device, capable of generating a number of gear (zp1、zp2、zi1、zi2) and generate a set of steps, the number of gears generated (zp1、zp2、zi1、zi2) from the set of setting a first set of, vector x=(xp1、xp2、xi1、xi2) or vector x=(xp1、xp2、Xc) to an appropriate initial value for the step of applying a and, the gradient vector v=(∂η / ∂xp1、∂η / ∂xp2、∂η / ∂xi1、∂η / ∂xi2) or gradient vector v=(∂η / ∂xp1、∂η / ∂xp2、∂η / ∂Xc) and a step of obtaining, v, q > 0 And q satisfy the selected vector, the update amount of said vector x γ q is small enough and determining whether or not, said updating amount γ q has not become sufficiently small when it is determined, the amount of said update vector x γ q and adding the step of updating, by the update amount γ q is small enough if it was determined that, wherein the gear number (zp1、zp2、zi1、zi2) set of dislocations coefficient (xp1、xp2、xi1、xi2) combination, or the gear number (zp1、zp2、zi1、zi2) set of dislocations coefficient (xp1、xp2、Xc) combinations, in which the power transmission efficiency η is the maximum or quasi-maximum transition coefficient to select a combination of a step, in which the power transmission efficiency η becomes the maximum, the selected gear number (zp1、zp2、zi1、zi2) set of dislocations coefficient (xp1、xp2、xi1、xi2) combination, or a selected gear number (zp1、zp2、zi1、zi2) dislocations and a set of coefficients (xp1、xp2、Xc) and the step of outputting the combination of, the design of the planetary gear apparatus to execute the program.
  • 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
  • YOKOHAMA NATIONAL UNIVERSITY
  • 発明者(英語)
  • FUJIMOTO YASUTAKA
  • KOBUSE DAIJI
国際特許分類(IPC)
指定国 (WO2017213151)
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 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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