JP2828542B2 - Flexible mesh gear meshing structure - Google Patents

Flexible mesh gear meshing structure

Info

Publication number
JP2828542B2
JP2828542B2 JP4142514A JP14251492A JP2828542B2 JP 2828542 B2 JP2828542 B2 JP 2828542B2 JP 4142514 A JP4142514 A JP 4142514A JP 14251492 A JP14251492 A JP 14251492A JP 2828542 B2 JP2828542 B2 JP 2828542B2
Authority
JP
Japan
Prior art keywords
gear
tooth
external gear
meshing
wave generator
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.)
Expired - Fee Related
Application number
JP4142514A
Other languages
Japanese (ja)
Other versions
JPH05332404A (en
Inventor
勇三 小倉
敏浩 石田
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.)
Sumitomo Heavy Industries Ltd
Original Assignee
Sumitomo Heavy Industries 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 Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd
Priority to JP4142514A priority Critical patent/JP2828542B2/en
Publication of JPH05332404A publication Critical patent/JPH05332404A/en
Application granted granted Critical
Publication of JP2828542B2 publication Critical patent/JP2828542B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H55/00Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02Toothed members; Worms
    • F16H55/08Profiling
    • F16H55/0833Flexible toothed member, e.g. harmonic drive

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【産業上の利用分野】本発明は、小型の減速機、あるい
は増速機に適用するのに好適な、撓み噛合い式の歯車噛
合構造の特に歯形の構造に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear meshing structure of a flexible meshing type, particularly a toothed structure suitable for being applied to a small reduction gear or a speed increasing gear.

【0002】[0002]

【従来の技術】従来、図4に示されるような回転原理に
基づく撓み噛合い式の歯車噛合構造が広く知られてい
る。
2. Description of the Related Art A gear meshing structure of a flexible meshing type based on the principle of rotation as shown in FIG. 4 has been widely known.

【0003】図において、符号2が入力軸(第1軸)、
4が該入力軸2の回転によって回転する波動発生器、6
が該波動発生器4の外周に摺動可能に取付けられ該波動
発生器の外周で撓み変形回転が可能とされた外歯歯車、
8が前記外歯歯車6が内接噛合する内歯歯車である。
In the drawing, reference numeral 2 denotes an input shaft (first axis),
4 is a wave generator rotated by the rotation of the input shaft 2;
An external gear that is slidably mounted on the outer periphery of the wave generator 4 and is capable of bending deformation rotation on the outer periphery of the wave generator;
Reference numeral 8 denotes an internal gear in which the external gear 6 meshes internally.

【0004】前記波動発生器4は、入力軸2と一体的に
設けられた楕円形のカム体4Aと、このカム体4Aの外
周に嵌合して楕円形に撓められた可撓性のボールベアリ
ング4Bと、からなる。このボールベアリング4Bの外
環は外歯歯車6に嵌合している。
The wave generator 4 has an elliptical cam body 4A provided integrally with the input shaft 2 and a flexible elliptically bent fitting on the outer periphery of the cam body 4A. And a ball bearing 4B. The outer ring of the ball bearing 4 </ b> B is fitted to the external gear 6.

【0005】外歯歯車6の歯数は内歯歯車2の歯数より
2N(Nは正の整数)だけ少ない歯数とされている。
The number of teeth of the external gear 6 is 2N (N is a positive integer) smaller than the number of teeth of the internal gear 2.

【0006】図4(A)〜(C)に示されるように、
今、入力軸2を回転させると波動発生器4のカム体4A
が回転させられ、このカム体4Aの回転により可撓性の
ボールベアリング4Bを介して外歯歯車6が撓み変形し
ながら内歯歯車8の内側で内接回転する。
As shown in FIGS. 4A to 4C,
Now, when the input shaft 2 is rotated, the cam 4A of the wave generator 4 is rotated.
Is rotated, and the rotation of the cam body 4A causes the external gear 6 to inscribe and rotate inside the internal gear 8 while flexing and deforming via the flexible ball bearing 4B.

【0007】従って、今、内歯歯車8をケーシングに固
定した場合は、外歯歯車6は内歯歯車8に対して入力軸
2の1回転毎に両歯車6、8の歯数差に依存した分だけ
相対回転することになる。その結果、外歯歯車6の撓み
成分を吸収し、自転成分のみを出力として図示しない出
力部材(第2軸)に取出すと、該出力部材は入力軸2に
対して極めてゆっくりと回転することになり、減速比の
大きな減速機が実現できる。
Therefore, when the internal gear 8 is fixed to the casing, the external gear 6 depends on the difference between the internal gear 8 and the number of teeth of the two gears 6 and 8 every one rotation of the input shaft 2. It will rotate relative to that amount. As a result, when the bending component of the external gear 6 is absorbed and only the rotation component is taken out as an output to an output member (second shaft) (not shown), the output member rotates extremely slowly with respect to the input shaft 2. Therefore, a reduction gear having a large reduction ratio can be realized.

【0008】又、外歯歯車6の自転成分の方を固定した
場合は、内歯歯車8を出力部材とする減速機が実現でき
る。更に、ここで入力部材と出力部材を逆転させると増
速比の大きな増速機が実現できる。
When the rotation component of the external gear 6 is fixed, a speed reducer using the internal gear 8 as an output member can be realized. Further, when the input member and the output member are reversed, a gearbox having a large gear ratio can be realized.

【0009】このような撓み噛合い式の歯車噛合構造
は、少ない要素で大きな減速比あるいは増速比を得るこ
とができるため、小型精密機械用の増減速機等に多用さ
れている。
[0009] Such a gear meshing structure of the bending mesh type can obtain a large reduction ratio or a speed increasing ratio with a small number of elements, and is therefore frequently used for a speed increasing and reducing device for small precision machines.

【0010】ところで、従来、上記歯車噛合構造の歯車
の歯形としては、三角歯形あるいはインボリュート歯形
が多く用いられている。しかし、これらの歯形の歯車を
用いた場合、次のような問題がある。
Heretofore, triangular teeth or involute teeth have been widely used as gears of gears having the above-mentioned gear meshing structure. However, when these gears are used, there are the following problems.

【0011】(1)この種の撓み噛合い式歯車噛合構造
では、外歯歯車2と内歯歯車8の噛み合いが楕円の長軸
上の点でのみ行われるが、その際の両歯車の実質的な噛
合本数が少なく(噛合率が小さく)、従って許容伝達ト
ルクが小さい。
(1) In this kind of bending mesh type gear meshing structure, the meshing between the external gear 2 and the internal gear 8 is performed only at a point on the major axis of the ellipse. The actual number of meshes is small (the meshing ratio is small), and therefore the allowable transmission torque is small.

【0012】(2)歯元の厚さが大きく、歯元のアール
(R)部の曲率半径を大きくとれないため、歯元に応力
集中が発生しやすく、疲労強度が小さい。
(2) Since the thickness of the tooth root is large and the radius of curvature of the radius (R) portion of the tooth root cannot be made large, stress concentration tends to occur at the tooth root and fatigue strength is low.

【0013】そこで、前記歯形の噛合率や疲労強度を改
善する目的で、特開昭62−141358号公報には、
図5に示すように、外歯歯車6の歯形曲線を、歯先の半
円部11と歯元の直線部12とで構成し、一方、内歯歯
車8の歯形曲線を、前記外歯歯車6を波動発生器4によ
り内接噛合させた時に外歯歯車6が描く外包絡線により
構成した歯車噛合構造が提示されている。
For the purpose of improving the meshing ratio and fatigue strength of the tooth profile, Japanese Patent Application Laid-Open No. Sho 62-141358 discloses that
As shown in FIG. 5, the tooth profile curve of the external gear 6 is composed of a semicircular portion 11 at the tip and a linear portion 12 at the root, while the tooth profile of the internal gear 8 is defined by the external gear. A gear meshing structure constituted by an external envelope drawn by the external gear 6 when the wave generator 4 is internally meshed by the wave generator 4 is presented.

【0014】これによれば、歯先の半円部11により歯
面の面圧が緩和されると共に、噛合率の増加が達成さ
れ、それにより噛み合う歯の荷重分担が下がって、外歯
歯車6の強度が増加する。
According to this configuration, the semicircular portion 11 at the tooth tip reduces the surface pressure on the tooth surface and achieves an increase in the meshing ratio, whereby the load sharing of the meshing teeth is reduced and the external gear 6 The intensity increases.

【0015】[0015]

【発明が解決しようとする課題】しかし、依然として次
の問題があった。
However, there are still the following problems.

【0016】(1)図6に示すように、カム体(偏心
体)4Aが回転し、歯が外歯歯車6の描く移動軌跡20
に沿って動く時、外歯歯車6と内歯歯車8の噛み合い点
(接触点)はP1→P2→P3と移動する。その際、外
歯歯車6の歯先の半円部11の一部円弧11aのみが内
歯歯車8に噛み合うことになり、残りの円弧11bは、
トルク伝達に寄与する噛み合いには関与しない。ところ
が、従来の歯形は、実際には噛み合いに関与しない部分
をも含めて歯先の歯形曲線を半円状に構成しているた
め、曲率半径が歯厚の半分に限定されることになり、歯
面の面圧の緩和に限界を生じていた。
(1) As shown in FIG. 6, the cam body (eccentric body) 4A rotates, and the teeth move along the movement locus 20 drawn by the external gear 6.
, The mesh point (contact point) between the external gear 6 and the internal gear 8 moves from P1 to P2 to P3. At that time, only a part of the arc 11a of the semicircular portion 11 at the tip of the external gear 6 meshes with the internal gear 8, and the remaining arc 11b is
It does not contribute to the engagement that contributes to torque transmission. However, in the conventional tooth profile, since the tooth profile curve of the tooth tip including the part that does not actually participate in meshing is configured in a semicircular shape, the radius of curvature is limited to half of the tooth thickness, There was a limit to the reduction of the contact pressure on the tooth surface.

【0017】尚、この噛み合いに関与しない円弧11b
をも噛み合わせるようにすることは可能であるが、その
ようにした場合は、出力トルク発生に関与しない半径方
向の荷重が大きくなるだけで、結局、摩擦によるロスの
発生が減速機の効率等を下げることになるので好ましく
ない。
The arc 11b not involved in the engagement
However, in such a case, the load in the radial direction that does not contribute to the output torque generation only increases, and eventually the occurrence of loss due to friction reduces the efficiency of the reduction gear. Is not preferred because it will lower the

【0018】(2)歯面の面圧緩和のため、歯先の曲率
を大きくして歯厚を大きくした場合は、歯元のアール
(R)部の曲率を大きくとれなくなり、当該部分に応力
集中が発生し易い。
(2) In the case where the curvature of the tooth tip is increased to increase the tooth thickness in order to relieve the contact pressure on the tooth surface, the curvature of the radius (R) portion of the root cannot be increased, and the stress is applied to the portion. Concentration easily occurs.

【0019】本発明は、このような従来の問題に鑑みて
なされたものであって、歯面の面圧の緩和と、歯元部の
応力集中の緩和を共に達成し得る撓み噛合い式歯車噛合
構造を提供することを目的とする。
SUMMARY OF THE INVENTION The present invention has been made in view of such a conventional problem, and has been made in consideration of the above circumstances. An object is to provide an engagement structure.

【0020】[0020]

【課題を解決するための手段】本発明は、第1軸と、該
第1軸の回転に対応するように取付けられた波動発生器
と、該波動発生器の外周に摺動可能に取付けられ該波動
発生器の外周に沿って撓み変形が可能な外歯歯車と、該
外歯歯車が内接噛合する内歯歯車と、前記外歯歯車の自
転成分に対応するように取付けられた第2軸と、を備え
た撓み噛合い式歯車噛合構造において、前記外歯歯車の
歯先の周方向両側部分の歯形曲線を、歯厚の半分より大
きい半径の円弧で構成すると共に、前記内歯歯車の歯形
曲線を、その一部に、前記外歯歯車を前記波動発生器に
より該内歯歯車に内接噛合させたときに、該外歯歯車の
前記円弧が描く外包絡線の形状の部分を含む曲線で構成
したことにより、上記課題を解決したものである。
SUMMARY OF THE INVENTION The present invention provides a first shaft, a wave generator mounted to correspond to the rotation of the first shaft, and a slidably mounted outer periphery of the wave generator. An external gear that can be bent and deformed along the outer periphery of the wave generator, an internal gear in which the external gear meshes internally, and a second gear that is attached to correspond to the rotation component of the external gear. A shaft, and wherein the tooth profile curves of both circumferential portions of the tooth tip of the external gear are formed by arcs having a radius larger than half of the tooth thickness, and the internal gear is provided. Of the tooth profile curve, part of the external gear to the wave generator
When the internal gear meshes with the internal gear, the external gear
The above problem has been solved by forming a curve including a portion of the shape of the outer envelope drawn by the arc .

【0021】[0021]

【作用】上記構成の歯車噛合構造においては、外歯歯車
の歯先の周方向両側部分の歯形曲線が、歯厚の半分より
大きい曲率半径の円弧で構成されているので、例えば歯
厚を略一定にして比較した場合、従来の半円状の歯先よ
りもその歯形曲線の曲率が大きくなり、そのため歯面の
面圧が下がる。
In the gear meshing structure having the above-described structure, the tooth profile curves on both sides in the circumferential direction of the tooth tip of the external gear are constituted by arcs having a radius of curvature larger than half of the tooth thickness. When the comparison is made constant, the curvature of the tooth profile curve becomes larger than that of the conventional semicircular tooth tip, so that the surface pressure of the tooth surface decreases.

【0022】又、歯形曲線の曲率を略一定にして比較し
た場合は、従来より歯厚を小さくすることができ、その
分歯元のアール部の曲率を大きくとることができるよう
になる。この場合、本発明では内歯歯車の歯形曲線を
その一部に、該円弧が描く包絡線の形状の部分を含む
線により構成するようにしたため、外歯歯車の当該円
弧部分を円滑に内歯歯車に内接させることができる。
When the curvature of the tooth profile curve is made substantially constant, the tooth thickness can be made smaller than before, and the curvature of the radius portion at the root of the tooth can be made larger by that amount. In this case, in the present invention the tooth profile of the internal gear,
In part, because it so as to more configured <br/> curve including a portion of the shape of the outer envelope the arc is drawn, it is inscribed the arcuate portion of the external gear to smoothly internal gear be able to.

【0023】なお、外歯歯車の歯元側の歯形曲線は、連
続する複数の円弧で構成するようにすると、滑らかな歯
形曲線とすることができ、又、歯元部分での応力集中を
一層避けることができる。
If the tooth profile curve on the root side of the external gear is constituted by a plurality of continuous arcs, a smooth tooth profile curve can be obtained, and stress concentration at the root portion can be further reduced. Can be avoided.

【0024】[0024]

【実施例】以下、本発明の一実施例を図面を参照しなが
ら説明する。
An embodiment of the present invention will be described below with reference to the drawings.

【0025】実施例の歯車噛合構造では、外歯歯車(符
号6Aで示されている)の歯形及び内歯歯車(符号8A
で示されている)の歯形が従来品と異なるだけで、他は
図4に示すものと同じ構成を採用している。よって、以
下においては、主に外歯歯車6Aの歯形及び内歯歯車8
Aの歯形について説明し、他の説明については省略す
る。
In the gear meshing structure of the embodiment, the tooth profile of the external gear (reference numeral 6A) and the internal gear (reference numeral 8A) are used.
) Is the same as that shown in FIG. 4 except that the tooth profile is different from the conventional product. Therefore, in the following, mainly the tooth profile of the external gear 6A and the internal gear 8
The tooth profile of A will be described, and the other description will be omitted.

【0026】図1は、実施例の外歯歯車6Aの歯形を拡
大して示している。この外歯歯車6Aの各歯の周方向両
側部分の歯形曲線は、歯先側から順に第1、第2、第3
の3つの円弧31、32、33を滑らかに連ねた曲線で
構成されている。
FIG. 1 is an enlarged view of the tooth profile of the external gear 6A of the embodiment. The tooth profile curves on both sides in the circumferential direction of each tooth of the external gear 6A are first, second, and third in order from the tooth tip side.
Are smoothly connected to each other.

【0027】各歯の中心点A(歯先と歯元の中間で、歯
厚方向の中央の点)を通る周方向の線を基準線Lとした
場合、第1の円弧31は、半径R1が歯厚Bの半分より
かなり大きく(この例では歯厚Bの約3/2倍)、且つ
その中心C1が基準線L上に位置する凸状の円弧であ
る。
If a circumferential line passing through the center point A of each tooth (the middle point in the tooth thickness direction between the tooth tip and the root) is the reference line L, the first arc 31 has a radius R1 Is a convex arc that is considerably larger than half of the tooth thickness B (about 3/2 times the tooth thickness B in this example) and whose center C1 is located on the reference line L.

【0028】又、第2の円弧32は、半径R2が前記基
準線Lから歯元円Dまでの距離E(歯元の丈)よりかな
り大きく(この例では約2倍)、且つその中心C2が基
準線L上に位置する凹状の円弧である。
The radius R2 of the second arc 32 is considerably larger than the distance E (tooth length) from the reference line L to the root circle D (about twice as long in this example), and the center C2 thereof. Is a concave arc located on the reference line L.

【0029】又、第3の円弧33は、その中心C3が、
隣接する歯との中間線CL2より僅かに自歯寄りに位置
し、且つ歯元円Dと第2の円弧32とに接する半径R3
の凹状の円弧である。つまり、1歯ピッチ角Gの1/2
にあたる半歯ピッチ角1/2Gより、歯の中心線CL1
寄りの位置に、中心C3を位置させた円弧であり、歯元
円Dと第2の円弧32とに滑らかに接する半径のもので
ある。
The third arc 33 has a center C3,
Radius R3 which is located slightly closer to its own tooth than intermediate line CL2 between adjacent teeth and which is in contact with root circle D and second arc 32
Is a concave arc. That is, 1/2 of the pitch angle G of one tooth
From the half tooth pitch angle 1 / 2G
It is an arc with the center C3 positioned closer to it, and has a radius that smoothly touches the root circle D and the second arc 32.

【0030】尚、各歯の歯先は、外歯歯車6Aの中心よ
り、1歯の中心Aまでの長さに歯先のたけFを加えた長
さに等しい半径を持つ歯先円により構成されている。
The tip of each tooth is constituted by a tip circle having a radius equal to the length from the center of the external gear 6A to the center A of one tooth plus the length F of the tip. Have been.

【0031】又、このように外歯歯車6Aの歯形を構成
した関係から、内歯歯車8A(図3参照)の歯形曲線
は、その一部に、外歯歯車6Aを波動発生器4により内
接噛合させた時に該外歯歯車6Aの前記第1円弧31が
描く外包絡線の形状の部分Xを含む曲線で形成されてい
る。
Further, the tooth profile of the external gear 6A is configured as described above.
From the relationship described above, the tooth profile of the internal gear 8A (see FIG. 3)curve
IsSome of them,The external gear 6A is moved inside by the wave generator 4.
When the first arc 31 of the external gear 6A is brought into contact with the external gear 6A,
Outer envelope to drawIn the curve containing the part X of the shapeIs formed
You.

【0032】図3に、外歯歯車6Aと内歯歯車8Aの噛
み合い状態を拡大して示す。この図から外歯歯車6Aと
内歯歯車8Aの噛み合いが連続的に行われているのが分
かる。
FIG. 3 is an enlarged view showing the meshing state between the external gear 6A and the internal gear 8A. From this figure, it can be seen that the meshing between the external gear 6A and the internal gear 8A is continuously performed.

【0033】この実施例ではこのように外歯歯車6Aの
歯先の周方向両側の歯形曲線を、歯厚の半分よりかなり
大きい曲率半径R1の円弧で構成したので、従来の半円
状の歯先よりも歯面の面圧が下がる。
In this embodiment, since the tooth profile curves on both sides in the circumferential direction of the tooth tip of the external gear 6A are constituted by arcs having a radius of curvature R1 which is considerably larger than half of the tooth thickness, a conventional semicircular tooth is formed. The surface pressure on the tooth surface is lower than before.

【0034】又、歯形曲線の曲率とは関係なく歯厚を小
さくすることができるようになるので、図2に示すよう
に歯厚Bを小さくして、従来の歯よりも歯元のアール部
35の曲率を大きくすることができる。この場合、歯元
側の歯形曲線は、連続する2つの円弧で構成されている
ので、曲率の大きな滑らかな歯形曲線とすることがで
き、歯元部分での応力集中を避けることができる。
Since the tooth thickness can be reduced irrespective of the curvature of the tooth profile curve, the tooth thickness B is reduced as shown in FIG. 35 can be increased. In this case, since the tooth profile curve on the root side is composed of two continuous arcs, a smooth tooth profile curve having a large curvature can be obtained, and stress concentration at the root portion can be avoided.

【0035】更に、歯先の先端の噛み合いに不要な部分
をカットしたので、不必要な噛み合いにより生じる歯面
間の摩擦ロスをなくすことができる。
Further, since an unnecessary portion for the meshing of the tip of the tooth tip is cut, a friction loss between tooth surfaces caused by unnecessary meshing can be eliminated.

【0036】[0036]

【発明の効果】以上説明したように、本発明によれば、
歯車の歯面の面圧の緩和と、歯元の応力集中の緩和とを
共に達成することができ、歯車の強度アップを図ること
ができる。従って、容量に対してコンパクトな減速機あ
るいは増速機を提供することができるようになる。
As described above, according to the present invention,
It is possible to achieve both the reduction of the surface pressure on the tooth surface of the gear and the reduction of the stress concentration at the root of the gear, and the strength of the gear can be increased. Therefore, it is possible to provide a speed reducer or a speed-increasing gear with a smaller capacity.

【図面の簡単な説明】[Brief description of the drawings]

【図1】本発明の一実施例における外歯歯車の歯形の拡
大図
FIG. 1 is an enlarged view of a tooth profile of an external gear according to an embodiment of the present invention.

【図2】本発明の一実施例における外歯歯車の歯形と従
来の外歯歯車の歯形を比較して示す図
FIG. 2 is a diagram showing a comparison between a tooth profile of an external gear in an embodiment of the present invention and a tooth profile of a conventional external gear;

【図3】本発明の一実施例における外歯歯車と内歯歯車
の噛合図
FIG. 3 is an engagement diagram of an external gear and an internal gear in one embodiment of the present invention.

【図4】(A)〜(C)は、撓み噛合い式歯車噛合構造
の回転原理を説明するためのスケルトン図
FIGS. 4A to 4C are skeleton diagrams for explaining the principle of rotation of a flexion meshing gear meshing structure;

【図5】従来の撓み噛合い式歯車噛合構造において用い
られている外歯歯車の歯形の一例を示す図
FIG. 5 is a diagram showing an example of a tooth profile of an external gear used in a conventional flexible meshing gear meshing structure.

【図6】上記従来の歯車噛合構造における歯車噛合図FIG. 6 is a gear mesh diagram in the conventional gear mesh structure.

【符号の説明】[Explanation of symbols]

2…入力軸(第1軸) 4…波動発生器 6…外歯歯車 8…内歯歯車 31…第1の円弧 32…第2の円弧 33…第3の円弧 B…歯厚 R1…第1の円弧の半径 R2…第2の円弧の半径 R3…第3の円弧の半径 2 ... input shaft (first shaft) 4 ... wave generator 6 ... external gear 8 ... internal gear 31 ... first circular arc 32 ... second circular arc 33 ... third circular arc B ... tooth thickness R1 ... first Radius of the arc R2 ... radius of the second arc R3 ... radius of the third arc

フロントページの続き (58)調査した分野(Int.Cl.6,DB名) F16H 1/32Continuation of front page (58) Field surveyed (Int.Cl. 6 , DB name) F16H 1/32

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項1】第1軸と、該第1軸の回転に対応するよう
に取付けられた波動発生器と、該波動発生器の外周に摺
動可能に取付けられ該波動発生器の外周に沿って撓み変
形が可能な外歯歯車と、該外歯歯車が内接噛合する内歯
歯車と、前記外歯歯車の自転成分に対応するように取付
けられた第2軸と、を備えた撓み噛合い式歯車噛合構造
において、 前記外歯歯車の歯先の周方向両側部分の歯形曲線を、歯
厚の半分より大きい半径の円弧で構成すると共に、 前記内歯歯車の歯形曲線を、その一部に、前記外歯歯車
を前記波動発生器により該内歯歯車に内接噛合させたと
きに、該外歯歯車の前記円弧が描く外包絡線の形状の部
分を含む曲線で構成したことを特徴とする撓み噛合い式
歯車噛合構造。
1. A first shaft, a wave generator mounted to correspond to rotation of the first shaft, and slidably mounted on an outer periphery of the wave generator along an outer periphery of the wave generator. A bendable external gear that can be bent and deformed, an internal gear that the internal gear meshes with the external gear, and a second shaft mounted so as to correspond to the rotation component of the external gear. In the toothed gear meshing structure, the tooth profile curves of both sides in the circumferential direction of the tooth tip of the external gear are configured by an arc having a radius larger than half of the tooth thickness, and the tooth profile curve of the internal gear is partially formed. The external gear
Is internally meshed with the internal gear by the wave generator.
Part of the shape of the outer envelope drawn by the arc of the external gear
A flex meshing type gear meshing structure characterized by being constituted by a curve including a minute .
JP4142514A 1992-06-03 1992-06-03 Flexible mesh gear meshing structure Expired - Fee Related JP2828542B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP4142514A JP2828542B2 (en) 1992-06-03 1992-06-03 Flexible mesh gear meshing structure

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP4142514A JP2828542B2 (en) 1992-06-03 1992-06-03 Flexible mesh gear meshing structure

Publications (2)

Publication Number Publication Date
JPH05332404A JPH05332404A (en) 1993-12-14
JP2828542B2 true JP2828542B2 (en) 1998-11-25

Family

ID=15317129

Family Applications (1)

Application Number Title Priority Date Filing Date
JP4142514A Expired - Fee Related JP2828542B2 (en) 1992-06-03 1992-06-03 Flexible mesh gear meshing structure

Country Status (1)

Country Link
JP (1) JP2828542B2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4357054B2 (en) 1999-11-22 2009-11-04 株式会社ハーモニック・ドライブ・システムズ Negative displacement flexure meshing gear system having overtake type maximum tooth profile
CN105605196B (en) * 2016-03-24 2018-02-02 江苏理工学院 High intensity low vibration low noise spiral gear drive mechanism

Also Published As

Publication number Publication date
JPH05332404A (en) 1993-12-14

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