WO2012104927A1 - 3次元接触のインボリュート正偏位歯形を有する波動歯車装置 - Google Patents
3次元接触のインボリュート正偏位歯形を有する波動歯車装置 Download PDFInfo
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- WO2012104927A1 WO2012104927A1 PCT/JP2011/000644 JP2011000644W WO2012104927A1 WO 2012104927 A1 WO2012104927 A1 WO 2012104927A1 JP 2011000644 W JP2011000644 W JP 2011000644W WO 2012104927 A1 WO2012104927 A1 WO 2012104927A1
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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
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
- F16H1/10—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes one of the members being internally toothed
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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
- F16H49/00—Other gearings
- F16H49/001—Wave gearings, e.g. harmonic drive transmissions
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0833—Flexible toothed member, e.g. harmonic drive
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
Definitions
- the present invention relates to a wave gear device having a positive deviation tooth profile in which a deflection amount is larger than a regular deflection amount. More specifically, in the present invention, the basic tooth profile of the rigid internal gear and the flexible external gear of the wave gear device is an involute tooth profile having a lower pressure angle than the standard, and in the tooth trace direction of the external teeth of the flexible external gear, The present invention relates to a three-dimensional contact involute positive displacement tooth profile obtained by shifting the external tooth so that the straight portions of the involute tooth profile of the cross section perpendicular to the respective axes coincide with each other.
- Wave gear device is the founder C.I. W. Since the invention of Musser (Patent Document 1), various inventions of this apparatus have been made by many researchers including the present inventor to this day. There are various types of inventions related to the tooth profile.
- the present inventor proposed that the basic tooth form of the wave gear device is an involute tooth shape in Patent Document 2, and in Patent Documents 3 and 4, the teeth of the rigid internal gear and the flexible external gear of the wave gear device are proposed.
- the present inventor has proposed a tooth shape of high ratcheting torque capable of continuous meshing in a wave gear device in Patent Document 5.
- a wave gear device has an annular rigid internal gear, a flexible external gear arranged coaxially inside this, and a wave generator fitted inside this.
- the flexible external gear is formed on a flexible cylindrical body, a diaphragm extending in the radial direction from the rear end of the cylindrical body, and an outer peripheral surface portion on the front end opening side of the cylindrical body. With external teeth.
- a flexible external gear formed so that the diaphragm seals the rear end opening of the cylindrical body is called a cup-shaped flexible external gear, and the diaphragm spreads outward from the rear end of the cylindrical body.
- the flexible external gear formed in the state is called a top hat-shaped flexible external gear.
- the flexible external gear of any shape is bent elliptically by a wave generator, and the external teeth formed on the outer peripheral surface portion of the cylindrical body are rigid at both ends of the long axis direction of the ellipse. It meshes with the internal teeth of the internal gear.
- the rim neutral circle of the external teeth of the flexible external gear is also deformed into an elliptical rim neutral curve.
- the amount of deflection in the radial direction relative to the rim neutral circle before deformation at the major axis position of the rim neutral curve is w
- the value obtained by dividing the radius of the rim neutral circle by the reduction ratio of the wave gear device is a normal (standard) deflection amount w. 0 If you have these ratios (w / w 0) is called the deflection coefficient ⁇ .
- a deflection amount ( ⁇ > 1) larger than the normal deflection amount is called a positive deflection
- a deflection amount ( ⁇ ⁇ 1) smaller than the normal deflection amount is called a negative deflection.
- the external teeth of the flexible external gear bent in an elliptical shape are distanced from the diaphragm from the rear end portion on the diaphragm side toward the front end portion on the front end opening side along the tooth trace direction.
- An external tooth profile that is in a positive deflection state over the entire tooth trace direction of the external tooth is called a positive deflection tooth profile, and an external tooth profile that is in a negative displacement deflection state over the entire external tooth trace direction. Is called negative displacement tooth profile.
- one of the requests for wave gear devices is a high reduction ratio ratcheting measure.
- the number of teeth of both gears exceeds 200, it is necessary to increase the tooth depth in order to prevent ratcheting at high load torque.
- the object of the present invention is to maintain a wide range of meshing in the main cross section (axial cross section) set at a predetermined position in the tooth trace direction, and partially in other axial perpendicular sections in the tooth trace direction.
- the wave gear device of the present invention employs an involute positive deviation tooth profile having a low pressure angle of less than 20 ° as a basic tooth profile in order to increase the effective tooth depth.
- the rack tooth profile of the involute tooth profile is a straight line, a tooth profile capable of continuous meshing over the entire tooth trace of both gears in consideration of the tooth coning is realized. That is, in the present invention, a standard 2 mn (where m is a module) is a standard axial cross section (hereinafter referred to as a main cross section) set near the center of the tooth trace of the external teeth of the flexible external gear of the wave gear device.
- the rack tooth profile in the cross section perpendicular to each axis in the direction of external teeth was viewed along the direction of the teeth. If you want to match.
- rational tooth meshing over the entire tooth traces of both gears is realized.
- the present invention An annular rigid internal gear, A flexible external gear disposed on the inside; With a wave generator fitted inside,
- the flexible external gear includes a flexible cylindrical body and an annular diaphragm extending in a radial direction from the rear end of the cylindrical body, and includes a front end opening of the cylindrical body.
- the external teeth formed in the region are elliptically formed by the wave generator so as to bend from the rear end portion of the diaphragm side to the front end portion of the opening side to generate a deflection amount substantially proportional to the distance from the diaphragm.
- the rigid internal gear and the flexible external gear are module m spur gears;
- the number of teeth of each of the rigid internal gear and the flexible external gear is at least 200;
- the number of teeth of the flexible external gear is 2n less than the number of teeth of the rigid internal gear, where n is a positive integer;
- the basic tooth profile of the rigid internal gear and the flexible external gear is an involute tooth profile having a pressure angle ⁇ of less than 20 °;
- a cross section perpendicular to the axis set at a midway position between the rear end portion and the front end portion of the flexible external gear in the tooth trace direction of the external teeth is a main cross section, and the movement locus obtained in the main cross section is the first movement.
- the first tangent is defined as a tangent line whose angle with the major axis of the rim neutral curve is the pressure angle ⁇ among the tangent lines drawn on the first movement locus at the top of the loop on the first movement locus.
- the movement trajectories obtained in the cross sections perpendicular to each axis in the tooth trace direction other than the main cross section of the external teeth are called second movement trajectories, and the angle formed by the major axis of the rim neutral curve among the tangent lines drawn to these trajectories.
- second tangents are referred to as second tangents, respectively.
- the tooth profile of the cross section perpendicular to each axis other than the cross section is a dislocation tooth profile obtained by applying a transition to the basic tooth profile consisting of an involute tooth profile;
- the tooth tip of the internal tooth of the rigid internal gear is modified along the tooth trace direction so as not to interfere with the dislocation tooth profile.
- the dislocation amount of the dislocation tooth profile can be a value given by the following equation.
- the dislocation amount curve obtained by the above equation can be approximated by a straight line having a constant gradient. Can also be specified.
- the flexible external gear can be a conical gear with constant teeth.
- the tooth tip of the external tooth of the flexible external gear is the internal tooth of the rigid internal gear.
- the shape of the tooth tip cylindrical surface of the external teeth may be a conical surface whose outer diameter gradually decreases from the rear end portion toward the front end portion in the tooth trace direction so as to be substantially parallel to the tooth bottom.
- the flexible external gear has a positive deflection with a deflection amount larger than the normal deflection amount
- the rigid internal gear and the flexible external gear have an involute tooth profile with a lower pressure angle than the standard.
- the external teeth are displaced so that the straight portions of the involute tooth profile of the cross section perpendicular to each axis of the external teeth coincide with each other.
- the meshing of both teeth can be realized not only on the cross section perpendicular to the axis but also in the direction along the tooth trace perpendicular thereto, so that the desired transmission torque can be maintained even at a high reduction ratio. Yes.
- FIG. 1 It is a schematic front view which shows an example of a general wave gear apparatus. It is explanatory drawing which shows the bending condition of a cup-shaped and a top hat-shaped flexible external gear by an axial section, (a) is a state before a deformation
- FIG. 1 is a front view of a wave gear device that is an object of the present invention.
- 2 (a) to 2 (c) are cross-sectional views showing a state in which the opening of the flexible external gear is bent into an elliptical shape in a cross section including an axis, (a) is a state before deformation, (b) Is a cross section including the major axis of the ellipse after deformation, and (c) is a cross section including the minor axis of the ellipse after deformation.
- 2A to 2C a solid line indicates a cup-shaped flexible external gear, and a broken line indicates a top hat-shaped flexible external gear.
- a wave gear device 1 includes an annular rigid internal gear 2, a flexible external gear 3 disposed on the inner side thereof, and a wave generator having an elliptical profile fitted on the inner side. 4.
- the rigid internal gear 2 and the flexible external gear 3 are spur gears of the module m, and the number of teeth is 200 or more.
- the flexible external gear 3 of the wave gear device 1 is bent into an ellipse by a wave generator 4 having an elliptical contour, and the external teeth 11 are in the vicinity of both ends of the elliptical long axis L1. It meshes with the internal teeth 12 of the gear 2.
- the flexible external gear 3 includes a flexible cylindrical body 13, a diaphragm 15 that extends continuously in the radial direction from the rear end 14, and a boss 16 that continues to the diaphragm 15.
- External teeth 11 are formed on the outer peripheral surface portion of the cylindrical body 13 on the opening end 17 side.
- the cylindrical body portion 13 is directed from the diaphragm-side rear end 114 toward the opening end 17 by the wave generator 4 having an elliptical contour that is fitted into the inner peripheral surface portion of the outer tooth forming portion of the cylindrical body portion 13.
- the amount of bending outward or inward in the radial direction is gradually increased.
- FIG. 2B in the cross section including the elliptical long axis L1, the amount of outward deflection gradually increases in proportion to the distance from the rear end 14 to the open end 17, and is shown in FIG.
- the amount of inward bending gradually increases in proportion to the distance from the rear end 14 to the opening end 17.
- the external teeth 11 formed on the outer peripheral surface portion on the opening end 17 side also move from the rear end portion 18 on the diaphragm side toward the front end portion 19 on the opening end side in the tooth trace direction, with the rear end 14 (diaphragm 15
- the amount of deflection gradually increases in proportion to the distance from
- FIG. 3 shows an elliptical rim of the external teeth 11 of the flexible external gear 3 with respect to the internal teeth 12 of the rigid internal gear 2 obtained by approximating the relative motion of both the gears 2 and 3 of the wave gear device 1 with a rack. It is a figure which shows the movement locus
- the x-axis indicates the direction of translation of the rack, and the y-axis indicates the direction perpendicular to the rack.
- the origin of the y axis is the average position of the amplitude of the movement trajectory.
- Equation 1A the movement trajectory is as shown in Equation 1A.
- FIG. 3 shows the movement locus in this case.
- x 0.5 ( ⁇ sin ⁇ ) (Formula 1A)
- y ⁇ cos ⁇
- FIG. 4 shows a rack tooth profile of an involute tooth profile having a low pressure angle ⁇ ( ⁇ 20 °) set in the main section 20 of the deflection coefficient ⁇ 0 of the flexible external gear 3. High teeth are used to prevent ratcheting.
- the total amplitude of the movement locus drawn by a point on the elliptical rim neutral curve of the flexible external gear 3 with respect to the rigid internal gear 2 in the main cross section 20 is expressed as 2 ⁇ 0 mn (positive deviation of ⁇ 0 > 1).
- the total amplitude of the movement locus drawn by the points on the elliptical rim neutral curve at the front end portion 19 of the external teeth 11 in the direction of the tooth traces is 2 ( ⁇ 0 + a) mn, and the rear end portion 18 of the external teeth 11 in the direction of the tooth traces.
- the total amplitude of the movement locus drawn by the points on the elliptical rim neutral curve at 2 is 2 ( ⁇ 0 -b) mn.
- the angle formed by the major axis of the rim neutral curve (y axis in FIG. 3) with respect to the movement trajectory I 0 is the pressure angle ⁇ .
- a tangent line ( ⁇ 20 °) is drawn and is defined as a first tangent line T1.
- a tangent line whose angle with the major axis of the rim neutral curve is a pressure angle ⁇ with respect to the loop-shaped top portion of the movement locus obtained in the cross-section perpendicular to each axis in the tooth trace direction other than the main cross section 20 in the external tooth 11 This is referred to as a second tangent line T2.
- a second tangent line T2 For example, in FIG.
- the second tangent line T2a is obtained at the loop-shaped top portion of the movement locus Ia of the front end portion 19
- the second tangent line T2b is obtained at the loop-shaped top portion of the movement locus Ib of the rear end portion 18.
- each of the external teeth 11 other than the main cross section 20 other than the main cross section 20 is a dislocation tooth profile obtained by transferring the basic tooth profile composed of the rack tooth profile of the involute tooth profile.
- FIG. 5 is a graph showing the amount of dislocation at each position of the tooth trace of the flexible external gear, and shows an example of the above formula 2.
- the horizontal axis indicates the value (deviation coefficient ⁇ ) obtained by dividing the radial deflection w of the cross section perpendicular to each axis of the external teeth 11 of the flexible external gear 3 by mn
- the vertical axis indicates the displacement y. Show. Practically, since this curve is close to a straight line, the amount of dislocation may be defined by a straight line approximating this curve.
- 6 (A), 6 (B) and 6 (C) show meshing with the internal teeth 12 of the rigid internal gear 2 at the front end 19, the main cross section 20 and the rear end 18 of the external teeth 11 thus obtained. Is shown.
- the tooth profiles of the two gears 2 and 3 share the tooth profile of the straight portion.
- FIG. 7 shows an example of the shapes of the teeth of the flexible external gear 3 and the rigid internal gear 2 having the tooth shapes formed as described above, and the center axis 1a and the elliptical shape of these both gears. It is a longitudinal cross-sectional view at the time of cut
- the tooth tips of the internal teeth 12 of the rigid internal gear 2 are modified so as not to interfere with the dislocation tooth profile of the external teeth 11 along the tooth trace direction. That is, in the tooth tip of the inner tooth 12, the toothpaste gradually decreases from the position corresponding to the main cross section 20 of the outer tooth 11 toward the end on the rear end portion 18 side of the outer tooth in the tooth trace direction. It has been modified.
- the flexible external gear 3 be a conical gear having a constant height.
- the tip of the external tooth 11 of the flexible external gear 3 is the internal tooth of the rigid internal gear 2 on the axial cross section including the long axis when the flexible external gear 3 is deformed in an elliptical shape.
- the shape of the tooth tip cylindrical surface of the external tooth 11 is a conical surface whose outer diameter gradually decreases from the rear end portion 18 toward the front end portion 19 in the tooth trace direction so as to be substantially parallel to the 12 tooth bottom. Is desirable.
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Abstract
Description
円環状の剛性内歯車と、
この内側に配置された可撓性外歯車と、
この内側に嵌めた波動発生器とを有し、
前記可撓性外歯車は、可撓性の円筒状胴部と、この円筒状胴部の後端から半径方向に延びている円環状のダイヤフラムを備え、前記円筒状胴部の前端開口部の部位に形成されている外歯が、前記波動発生器によって、そのダイヤフラム側の後端部からその開口側の前端部に掛けて、前記ダイヤフラムからの距離にほぼ比例した撓み量が生ずるように楕円状に撓められる波動歯車装置において:
前記剛性内歯車および前記可撓性外歯車はモジュールmの平歯車であり;
前記剛性内歯車および可撓性外歯車のそれぞれの歯数は、少なくとも200枚であり;
前記可撓性外歯車の歯数は、nを正の整数とすると、前記剛性内歯車の歯数より2n枚少なく;
前記剛性内歯車および前記可撓性外歯車の基本歯形は、圧力角αが20°未満のインボリュート歯形であり;
前記可撓性外歯車が前記波動発生器によって楕円状に変形することにより、前記可撓性外歯車の外歯のリム中立円は楕円状のリム中立曲線に変形しており、当該リム中立曲線の長軸位置における前記リム中立円に対する半径方向の撓み量は、κを1より大きな値の偏位係数とすると、κmnであり;
前記可撓性外歯車の外歯の歯筋方向の各位置における軸直角断面において、歯の噛み合いをラック噛み合いで近似したときに得られる前記可撓性外歯車の外歯の前記剛性内歯車の内歯に対する各移動軌跡を求め、
前記可撓性外歯車の外歯の歯筋方向における後端部から前端部までの間の途中位置に設定した軸直角断面を主断面とし、この主断面において得られる前記移動軌跡を第1移動軌跡と呼び、この第1移動軌跡上のループ状頂部において、当該第1移動軌跡に引いた接線のうち、リム中立曲線の長軸とのなす角が前記圧力角αとなる接線を第1接線と呼び、
前記外歯における前記主断面以外の歯筋方向の各軸直角断面において得られる前記移動軌跡をそれぞれ第2移動軌跡と呼び、これらに引いた接線のうち、リム中立曲線の長軸とのなす角が前記圧力角αとなる接線をそれぞれ第2接線と呼ぶものとすると、
前記外歯の歯筋方向に沿って見た場合に、各軸直角断面における各第2移動軌跡を遷移させて各第2接線が前記第1接線に一致するように、前記外歯における前記主断面以外の各軸直角断面の歯形が、インボリュート歯形からなる前記基本歯形に転移を施した転位歯形となっており;
前記剛性内歯車の内歯の歯先には、その歯筋方向に沿って、前記転位歯形に干渉しないように修正が施されていることを特徴としている。
図1は本発明の対象である波動歯車装置の正面図である。図2(a)~(c)はその可撓性外歯車の開口部を楕円状に撓ませた状況を含軸断面で示す断面図であり、(a)は変形前の状態、(b)は変形後における楕円形の長軸を含む断面、(c)は変形後における楕円の短軸を含む断面をそれぞれ示してある。なお、図2(a)~(c)において実線はコップ状の可撓性外歯車を示し、破線はシルクハット状の可撓性外歯車を示す。
x=0.5mn(θ-κsinθ) (式1)
y=κmncosθ
x=0.5(θ-κsinθ) (式1A)
y=κcosθ
次に、本発明による外歯11、内歯12の歯形設定方法を説明する。まず、可撓性外歯車3の軸直角断面で歯筋方向の中央付近に設定した断面を主断面20とする。図4は、可撓性外歯車3の偏位係数κ0の主断面20に設定した低圧力角α(<20°)のインボリュート歯形のラック歯形形状である。ラチェティングを防止するために高歯を採用している。すなわち、主断面20で歯たけを標準の2mn(mはモジュール、nは正の整数であり、通常はn=1)より大きくした2κ0mn=2(1+c)mn(偏位係数κ0=1+c、0<c<0.5)としている。このように、外歯11および内歯12の基本歯形として、低圧力角αのインボリュート歯形のラック歯形形状を採用する。
a=κ0(la-l0)/l0
b=κ0(l0-lb)/l0
1a 中心軸線
2 剛性内歯車
3 可撓性外歯車
4 波動発生器
11 外歯
12 内歯
13 円筒状胴部
14 後端
15 ダイヤフラム
16 ボス
17 開口端
18 後端部
19 前端部
20 主断面
I 標準偏位撓みの移動軌跡
I0 主断面の正偏位撓みの移動軌跡
Ia 前端部の正偏位撓みの移動軌跡
Ib 後端部の正偏位撓みの移動軌跡
T1 第1接線
T2a、T2b 第2接線
Claims (4)
- 円環状の剛性内歯車と、この内側に配置された可撓性外歯車と、この内側に嵌めた波動発生器とを有し、
前記可撓性外歯車は、可撓性の円筒状胴部と、この円筒状胴部の後端から半径方向に延びている円環状のダイヤフラムを備え、前記円筒状胴部の前端開口部の部位に形成されている外歯が、前記波動発生器によって、そのダイヤフラム側の後端部からその開口側の前端部に掛けて、前記ダイヤフラムからの距離にほぼ比例した撓み量が生ずるように楕円状に撓められる波動歯車装置において:
前記剛性内歯車および前記可撓性外歯車はモジュールmの平歯車であり;
前記剛性内歯車および可撓性外歯車の歯数は、少なくとも200枚であり;
前記可撓性外歯車の歯数は、nを正の整数とすると、前記剛性内歯車の歯数より2n枚少なく;
前記剛性内歯車および前記可撓性外歯車の基本歯形は、圧力角αが20°未満のインボリュート歯形であり;
前記可撓性外歯車が前記波動発生器によって楕円状に変形することにより、前記可撓性外歯車の外歯のリム中立円は楕円状のリム中立曲線に変形しており、当該リム中立曲線の長軸位置における前記リム中立円に対する半径方向の撓み量は、κを1より大きな値の偏位係数とすると、κmnであり;
前記可撓性外歯車の外歯の歯筋方向の各位置における軸直角断面において、歯の噛み合いをラック噛み合いで近似したときに得られる前記可撓性外歯車の外歯の前記剛性内歯車の内歯に対する各移動軌跡を求め、
前記可撓性外歯車の外歯の歯筋方向における後端部から前端部までの間の途中位置に設定した軸直角断面を主断面とし、この主断面において得られる前記移動軌跡を第1移動軌跡と呼び、この第1移動軌跡上のループ状頂部において、当該第1移動軌跡に引いた接線のうち、リム中立曲線の長軸とのなす角が前記圧力角αとなる接線を第1接線と呼び、
前記外歯における前記主断面以外の歯筋方向の各軸直角断面において得られる前記移動軌跡をそれぞれ第2移動軌跡と呼び、これらに引いた接線のうち、リム中立曲線の長軸とのなす角が前記圧力角αとなる接線をそれぞれ第2接線と呼ぶものとすると、
前記外歯の歯筋方向に沿って見た場合に、各軸直角断面における各第2移動軌跡を遷移させて各第2接線が前記第1接線に一致するように、前記外歯における前記主断面以外の各軸直角断面の歯形が、インボリュート歯形からなる前記基本歯形に転移を施した転位歯形となっており;
前記剛性内歯車の内歯の歯先には、その歯筋方向に沿って、前記転位歯形に干渉しないように修正が施されていることを特徴とする波動歯車装置。 - 請求項1において、
前記外歯における前記主断面での歯たけは、当該主断面での偏位係数κをκ0とすると、2κ0mnであり、
偏位係数κ0は1+c(0<c<0.5)であることを特徴とする波動歯車装置。 - 請求項1ないし3のうちのいずれかの項において、
前記可撓性外歯車は等高歯の円錐歯車であり、
当該可撓性外歯車が楕円状に変形した状態での長軸を含む軸断面上において、当該可撓性外歯車の外歯の歯先が前記剛性内歯車の内歯の歯底にほぼ平行になるように、当該外歯の歯先円筒面の形状は、歯筋方向の後端部から前端部に向けて外径が漸減する円錐面となっていることを特徴とする波動歯車装置。
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US13/701,336 US9057421B2 (en) | 2011-02-04 | 2011-02-04 | Wave gear device having three-dimensional contacting involute positive deflection tooth profile |
JP2012555571A JP5390028B2 (ja) | 2011-02-04 | 2011-02-04 | 3次元接触のインボリュート正偏位歯形を有する波動歯車装置 |
PCT/JP2011/000644 WO2012104927A1 (ja) | 2011-02-04 | 2011-02-04 | 3次元接触のインボリュート正偏位歯形を有する波動歯車装置 |
KR1020137001544A KR101411588B1 (ko) | 2011-02-04 | 2011-02-04 | 3차원 접촉의 인볼류트 양편위 치형을 가지는 파동기어장치 |
CN201180030454.8A CN102959275B (zh) | 2011-02-04 | 2011-02-04 | 具有三维接触渐开线正偏位齿形的波动齿轮装置 |
DE112011103908T DE112011103908T5 (de) | 2011-02-04 | 2011-02-04 | Wellgetriebe mit einem Evolventen-Zahnprofil mit positiver Verbiegung, das dreidimensional im Kontakt steht |
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WO2013046274A1 (ja) * | 2011-09-29 | 2013-04-04 | 株式会社ハーモニック・ドライブ・システムズ | テーパー型可撓性外歯車を有する波動歯車装置 |
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KR20130031348A (ko) | 2013-03-28 |
CN102959275A (zh) | 2013-03-06 |
US9057421B2 (en) | 2015-06-16 |
CN102959275B (zh) | 2015-09-02 |
JPWO2012104927A1 (ja) | 2014-07-03 |
JP5390028B2 (ja) | 2014-01-15 |
KR101411588B1 (ko) | 2014-06-25 |
DE112011103908T5 (de) | 2013-09-19 |
US20130081496A1 (en) | 2013-04-04 |
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