JPS6246742B2 - - Google Patents
Info
- Publication number
- JPS6246742B2 JPS6246742B2 JP53018359A JP1835978A JPS6246742B2 JP S6246742 B2 JPS6246742 B2 JP S6246742B2 JP 53018359 A JP53018359 A JP 53018359A JP 1835978 A JP1835978 A JP 1835978A JP S6246742 B2 JPS6246742 B2 JP S6246742B2
- Authority
- JP
- Japan
- Prior art keywords
- roller
- pressing force
- thick
- thin
- walled cylindrical
- 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
Links
- 238000003825 pressing Methods 0.000 claims description 71
- 230000013011 mating Effects 0.000 claims description 9
- 230000005540 biological transmission Effects 0.000 claims description 6
- 230000007935 neutral effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000005255 carburizing Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000010791 quenching Methods 0.000 description 1
- 230000000171 quenching effect Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Landscapes
- Friction Gearing (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Description
【発明の詳細な説明】
本発明は相互に接触するローラの摩擦力により
動力を伝達する遊星ローラ式動力伝達装置の改良
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a planetary roller type power transmission device that transmits power by the frictional force of rollers that are in contact with each other.
従来のこの種動力伝達装置として、例えば特開
昭51−148158号の発明及び特開昭47−26563号の
発明が提供されている。 As conventional power transmission devices of this kind, for example, the invention of JP-A-51-148158 and the invention of JP-A-47-26563 have been proposed.
特開昭51−148158号のものには、軸方向に沿う
押付力の変化に従い相手ローラとの当接面におけ
る圧接力が変化する内ローラ１０が示されてい
る。 JP-A-51-148158 discloses an inner roller 10 in which the pressing force on the contact surface with the mating roller changes in accordance with the change in the pressing force along the axial direction.
しかしながら、これの内ローラは、断面の厚さ
が一様のＵ字状ローラであるので、これを軸方向
に押圧したときの中立面（軸方向押付力により半
径方向に移動しない面）が内周寄りに位置する傾
向となる。このため押付力を加えたとき、中立面
よりも外周側の半径方向移動量即ち外径の増加量
が大きくなり、該押付力の相当な部分が外径の増
大に変換され内径の縮小量即ち圧接力に変換され
る量は少ない。 However, since this inner roller is a U-shaped roller with a uniform cross-sectional thickness, when it is pressed in the axial direction, the neutral surface (the surface that does not move in the radial direction due to the axial pressing force) is It tends to be located closer to the inner circumference. Therefore, when a pressing force is applied, the amount of radial movement on the outer circumferential side from the neutral plane, that is, the amount of increase in the outer diameter becomes larger, and a considerable portion of the pressing force is converted into an increase in the outer diameter, resulting in a reduction in the inner diameter. That is, the amount converted into pressure contact force is small.
従つて、内ローラに上記軸方向押付力を加える
と、該ローラの外径増加量が大きいため、内ロー
ラの外周面がハウジングの内周面内にくさび状に
喰い込む（外周端部分が喰い込み）かまたは上記
内ローラの外周面及びハウジングの内周面の両面
が強力に圧接されて過大な摩擦抵抗が発生する。
つまり、押付力はその大部分が上記両面の喰い込
み抵抗または摩擦抵抗に消費され、相手ローラと
の間の圧接力の増加即ち当接部の半径の変化に変
換される量が外径部をフリーにした場合よりも更
に少なくなる。 Therefore, when the above-mentioned axial pressing force is applied to the inner roller, the outer circumferential surface of the inner roller wedges into the inner circumferential surface of the housing (the outer circumferential end part bites) because the increase in the outer diameter of the roller is large. Otherwise, the outer peripheral surface of the inner roller and the inner peripheral surface of the housing are strongly pressed against each other, and excessive frictional resistance is generated.
In other words, most of the pressing force is consumed by the biting resistance or frictional resistance on both sides, and the amount converted into an increase in the pressing force with the mating roller, that is, a change in the radius of the contact part, increases with the outer diameter. It will be even less than if it were made free.
上記により、圧接力Ｐと軸方向押付力Ｔの比
Ｐ／Ｔが小さくなり、内ローラをハウジングの嵌
合孔内に嵌合した場合には上記のような喰い込み
抵抗または摩擦抵抗のために押付力Ｔを減じたと
きの復元が確実に行われず、押付力Ｔに比例した
圧接力Ｐは得られない。 As a result of the above, the ratio P/T of the pressing force P and the axial pressing force T becomes small, and when the inner roller is fitted into the fitting hole of the housing, due to the above-mentioned biting resistance or frictional resistance. Restoration when the pressing force T is reduced is not ensured, and a pressing force P proportional to the pressing force T cannot be obtained.
また、特開昭51−148158号のものにおいては、
内ローラはほぼ均一厚さであるので、側板部が変
形を起し易くクラウニング変形量が格段に少なく
なる。このため圧接面に片当りが発生する恐れが
充分ある。 In addition, in JP-A No. 51-148158,
Since the inner roller has a substantially uniform thickness, the side plate portion is easily deformed, and the amount of crowning deformation is significantly reduced. For this reason, there is a strong possibility that uneven contact will occur on the press-contact surfaces.
次に特開昭47−26563のものは、内ローラを、
比較的長い薄肉円筒部の両端に厚肉円筒部の内周
を接続して構成することにより、該内ローラとケ
ーシングとにより油圧シリンダを形成している。
そして該油圧シリンダ内に作動油を導入して内ロ
ーラの薄肉円筒部を中心に向けて変形せしめるこ
とにより、内ローラと遊星ローラとの間に圧接力
を生成せしめている。 Next, in JP-A No. 47-26563, the inner roller is
By connecting the inner periphery of the thick-walled cylindrical portion to both ends of a relatively long thin-walled cylindrical portion, a hydraulic cylinder is formed by the inner roller and the casing.
By introducing hydraulic oil into the hydraulic cylinder and deforming the thin cylindrical portion of the inner roller toward the center, a pressing force is generated between the inner roller and the planetary roller.
しかしながら、上記特開昭47−26563号のもの
は、油圧により内ローラを変形させる形式である
ので、油圧導入のための配管やシール手段が必要
となり、装置が複雑化するとともに油洩れ等によ
り圧接力減少の不具合が発生し易い。 However, since the method of JP-A-47-26563 mentioned above uses hydraulic pressure to deform the inner roller, it requires piping and sealing means to introduce hydraulic pressure, which complicates the device and prevents oil leakage. Problems such as force reduction are likely to occur.
また、油圧を薄肉円筒部に半径方向に加えてい
るので、薄肉円筒部はその全長に亘つて変形し、
クラウニング変形（中央部が大きく両端部が小さ
くなるような曲面状の変形）が得られず、内ロー
ラと遊星ローラとの間の片当りが発生し易く充分
な圧接力が得られないことが多い。 In addition, since hydraulic pressure is applied to the thin-walled cylindrical portion in the radial direction, the thin-walled cylindrical portion deforms over its entire length.
Crowning deformation (curved deformation where the center is large and both ends are small) cannot be obtained, and uneven contact between the inner roller and the planetary roller tends to occur, making it difficult to obtain sufficient contact force. .
本発明は上記に鑑みなされたもので、外周部に
厚肉部を設けることにより中立面を外周寄りに位
置せしめて相手ローラとの接触部の変形能を増加
し、小さな軸方向押付力で以つて大きな圧接力を
得るようにするとともに、油圧を使用せず機械的
な加圧手段を使用することにより構造が簡単かつ
低コストの遊星ローラ式動力伝達装置を提供する
ことを目的とする。 The present invention has been developed in view of the above, and by providing a thick wall portion on the outer periphery, the neutral surface is positioned closer to the outer periphery to increase the deformability of the contact portion with the mating roller, and a small axial pressing force can be applied. It is an object of the present invention to provide a planetary roller type power transmission device which has a simple structure and low cost by using a mechanical pressurizing means without using hydraulic pressure, and which can obtain a large pressing force.
このため、本発明に係る遊星ローラ式動力伝達
装置は、回転軸に連結された太陽ローラの外周及
び静止部材に固定された内ローラの内周にそれぞ
れ当接される複数個の遊星ローラを、回転軸に連
結されたキヤリヤにて軸支することにより、上記
２本の回転軸間に動力を伝達するものにおいて、
上記太陽ローラ、遊星ローラ及び内ローラの全部
または一部を、上記回転軸の軸方向に区切つて形
成されると共に押付力が附与される側端面を有す
る複数個の厚肉円筒部と、該厚肉円筒部よりも薄
肉に形成され内外周面の何れか一方が相手ローラ
との当接面とされると共に上記押付力が附与され
たとき該当接面がクラウニング変形可能にされた
薄肉円筒部と、上記厚肉円筒部よりも薄肉に形成
され上記薄肉円筒部の両側端を上記厚肉円筒部に
個別に接続する薄肉円板部とから成り、上記厚肉
円筒部の両側端を押圧したとき上記薄肉円筒部の
直径が変化せしめられる弾性ローラにて構成し、
上記弾性ローラは、静止部材、入力軸等該ローラ
が嵌合される部材上を上記回転軸の軸方向に伸縮
可能に設けられ、かつ上記弾性ローラを回転軸の
軸方向に機械的に押圧する手段を具えてなること
を特徴とする。 Therefore, the planetary roller type power transmission device according to the present invention has a plurality of planetary rollers that are in contact with the outer periphery of the sun roller connected to the rotating shaft and the inner periphery of the inner roller fixed to the stationary member, respectively. In a device that transmits power between the two rotating shafts by being supported by a carrier connected to the rotating shaft,
A plurality of thick-walled cylindrical portions are formed by dividing all or part of the sun roller, planetary roller, and inner roller in the axial direction of the rotating shaft, and have side end surfaces to which a pressing force is applied; A thin-walled cylinder that is thinner than the thick-walled cylindrical portion, and has one of its inner and outer circumferential surfaces as a contact surface with a mating roller, and the contact surface is capable of crowning deformation when the above-mentioned pressing force is applied. and a thin disc part that is thinner than the thick cylindrical part and individually connects both ends of the thin cylindrical part to the thick cylindrical part, and presses both ends of the thick cylindrical part. an elastic roller that changes the diameter of the thin-walled cylindrical portion when
The elastic roller is provided so as to be extendable and retractable in the axial direction of the rotating shaft on a member to which the roller is fitted, such as a stationary member and an input shaft, and mechanically presses the elastic roller in the axial direction of the rotating shaft. It is characterized by being equipped with means.
以下第１図ないし第６図を参照して本発明の１
実施例につき説明する。第１図において、１は太
陽ローラ、２は複数個の遊星ローラ、４はニード
ル軸受、５は遊星ピン、６はキヤリヤ、８は入力
軸、１０はケーシング、１１は出力軸、１３は入
力軸８を支承するための軸受、１４は出力軸１１
を支承するための軸受である。３０はじん性を有
する特殊鋼材等の弾性部材から成る内ローラ即ち
弾性ローラである。上記内ローラ３０は、第２図
に示すように遊星ローラ２との当接面３０ｄを有
する薄肉円筒部３０ａ、入力軸８、出力軸１１等
の回転軸の軸方向に区切つて２個形成された厚肉
円筒部３０ｂ、上記薄肉円筒部３０ａの両側端と
個々の厚肉円筒部３０ｂとを接続する薄肉円板部
３０ｃを結合して成る。上記２個の厚肉円筒部３
０ｂは回転軸の軸方向に比較的厚肉かつその両側
端面が入力軸８等の回転軸の軸心線に略直角な平
面に形成され、上記薄肉円筒部３０ａの肉厚ｔ２
は厚肉円筒部３０ｂの肉厚ｔ１の例えば1/2以下
の薄肉に形成される。また薄肉円板部３０ｃはそ
の肉厚ｔ３を上記ｔ２と同等または若干厚肉に
（円筒部３０ｂよりもはるかに薄肉とされる）さ
れる。 Hereinafter, with reference to FIGS. 1 to 6, 1 of the present invention will be described.
An example will be explained. In Fig. 1, 1 is a sun roller, 2 is a plurality of planetary rollers, 4 is a needle bearing, 5 is a planetary pin, 6 is a carrier, 8 is an input shaft, 10 is a casing, 11 is an output shaft, and 13 is an input shaft. 8 is a bearing for supporting the output shaft 11; 14 is the output shaft 11;
This is a bearing for supporting. Reference numeral 30 denotes an inner roller, that is, an elastic roller, which is made of an elastic member such as a special steel material having toughness. As shown in FIG. 2, the inner rollers 30 are formed into two thin-walled cylindrical portions 30a having contact surfaces 30d with the planetary rollers 2, separated in the axial direction of the rotational shafts such as the input shaft 8 and the output shaft 11. The thick cylindrical portion 30b is joined to the thin circular plate portion 30c which connects both ends of the thin cylindrical portion 30a and each thick cylindrical portion 30b. The above two thick-walled cylindrical parts 3
0b is relatively thick in the axial direction of the rotating shaft, and both end surfaces thereof are formed into planes substantially perpendicular to the axis of the rotating shaft such as the input shaft 8, and the thin cylindrical portion 30a has a wall thickness t2.
is formed to be thin, for example, 1/2 or less of the wall thickness t1 of the thick-walled cylindrical portion 30b. Further, the thin disk portion 30c has a wall thickness t3 equal to or slightly thicker than the above-mentioned t2 (much thinner than the cylindrical portion 30b).
尚、該薄肉円板部３０ｃには、第２図ａに示す
ようにその両側面にθｉ（０゜＜θｉ10゜が好
適）なる傾斜をもたせてもよい。 Incidentally, the thin disk portion 30c may have an inclination of θi (preferably 0°<θi10°) on both sides thereof, as shown in FIG. 2a.
また自由状態における上記内ローラ３０の内径
Diは、太陽ローラ１の外径Dsと遊星ローラ２の
外径Dpの２倍の和即ち（Ds＋2Dp）よりもわず
かに大きく形成され、遊星ローラ２の組付け、分
解を容易にしている。 Also, the inner diameter of the inner roller 30 in the free state
Di is formed to be slightly larger than the sum of twice the outer diameter Ds of the sun roller 1 and the outer diameter Dp of the planetary roller 2, ie (Ds+2Dp), to facilitate assembly and disassembly of the planetary roller 2.
上記構成を具えた動力伝達装置を組立てる際に
は、ケーシング１０内に太陽ローラ１及び遊星ロ
ーラ２を組み付けた後内ローラ３０を自由状態に
てケース１０の嵌合孔１０ａ内に挿入してピン９
で止める。従つて、内ローラ３０は上記嵌合孔１
０ａ内に入力軸８の軸方向に伸縮自在な状態で嵌
合されることとなる。この場合上記のように内ロ
ーラ３０の内周と遊星ローラ２の外周との間には
わずかな隙間が形成されているので、内ローラ３
０は極めて容易に挿入できる。内ローラ３０の挿
入後該内ローラ３０の厚肉円筒部３０ｂの側面と
ケースカバー１６との間に適当な厚さのジム１５
を敷きボルト１２を締めてケースカバー１６をケ
ーシング１０に固着する。上記締付けにより内ロ
ーラ３０は第２図に示すように軸方向の押付力Ｔ
を受けて自由状態における全幅WiがWtに縮小さ
れる。 When assembling the power transmission device having the above configuration, after assembling the sun roller 1 and planetary roller 2 into the casing 10, the inner roller 30 is inserted into the fitting hole 10a of the case 10 in a free state, and the pin is inserted into the fitting hole 10a of the case 10. 9
Stop with. Therefore, the inner roller 30 is inserted into the fitting hole 1.
It is fitted into the input shaft 8 in an axially expandable state. In this case, since a slight gap is formed between the inner circumference of the inner roller 30 and the outer circumference of the planetary roller 2 as described above, the inner roller 30
0 is very easy to insert. After inserting the inner roller 30, a jim 15 of an appropriate thickness is installed between the side surface of the thick cylindrical portion 30b of the inner roller 30 and the case cover 16.
and tighten the bolts 12 to secure the case cover 16 to the casing 10. Due to the above tightening, the inner roller 30 is applied with an axial pressing force T as shown in FIG.
As a result, the total width Wi in the free state is reduced to Wt.
この全幅Wiの縮小により内径Diも縮小しよう
とするが、当接面３０ｄが遊星ローラ２の外周と
当接した後は半径方向の変形が拘束され、この拘
束分に相当する圧接力Ｐが発生し、該圧接力Ｐに
より内ローラ３０、遊星ローラ２、太陽ローラ１
が圧接される。即ち第２図に示すように内ローラ
３０を自由状態から上記押付力Ｔで圧縮すると、
全幅WiがWtに、当接面３０ｄの幅BiがBtに、傾
斜角θｉがθｔにそれぞれ減少することにより内
径DiがDmに縮小され、当接面３０ｄには第２図
ｂに示すように曲率半径ｒなるクラウニングｃが
形成される。 Due to this reduction in the overall width Wi, the inner diameter Di also tends to be reduced, but after the contact surface 30d contacts the outer periphery of the planetary roller 2, the deformation in the radial direction is restrained, and a pressure contact force P corresponding to this restraint is generated. The pressing force P causes the inner roller 30, the planetary roller 2, and the sun roller 1 to
are pressed together. That is, as shown in FIG. 2, when the inner roller 30 is compressed from the free state with the pressing force T,
By reducing the overall width Wi to Wt, the width Bi of the contact surface 30d to Bt, and the inclination angle θi to θt, the inner diameter Di is reduced to Dm, and the contact surface 30d has a shape as shown in Fig. 2b. A crowning c with a radius of curvature r is formed.
従つて例えば自由状態における内径Di＝Ds＋
2Dpに形成された上記内ローラ３０をケーシング
１０内に組み込んだ状態で上記押付力Ｔにて圧縮
すると先ずクラウニングＣ（第２図のＣ）が圧縮
された後有効変形量ｅが圧縮され、結局内ローラ
３０の圧縮量は（Ｃ＋ｅ）となり、（Ｃ＋ｅ）に
相当する量の圧接力Ｐが発生することとなる。第
３図に押付力Ｔと内ローラ３０の半径方向変形量
Ｅとの関係を示す。第３図から明らかなように上
記変形量Ｅは押付力Ｔに比例し、従つて上記圧接
力Ｐも押付力Ｔに、更にはシム１５の厚さに比例
することになるので、シム１５の厚さを変化させ
て内ローラ３０の全幅Wtを変化させる即ちクラ
ウニング量Ｃ及び有効変形量ｅを変化させること
により圧接力Ｐを容易に調整することができる。 Therefore, for example, the inner diameter Di=Ds+ in the free state
When the inner roller 30 formed to 2Dp is assembled in the casing 10 and compressed by the pressing force T, the crowning C (C in Fig. 2) is first compressed, and then the effective deformation amount e is compressed, and eventually The amount of compression of the inner roller 30 is (C+e), and a pressing force P corresponding to (C+e) is generated. FIG. 3 shows the relationship between the pressing force T and the amount of radial deformation E of the inner roller 30. As is clear from FIG. 3, the amount of deformation E is proportional to the pressing force T, and therefore the pressing force P is also proportional to the pressing force T, and furthermore, to the thickness of the shim 15. By changing the thickness and changing the total width Wt of the inner roller 30, that is, by changing the crowning amount C and the effective deformation amount e, the pressing force P can be easily adjusted.
上記内ローラ３０は、剛性の大なる厚肉円筒部
３０ｂの側端面に押付力Ｔが附与されると共に変
形能の大きい薄肉円筒部３０ａに当接面３０ｄが
形成されているので、該内ローラ３０を回転軸の
軸方向に押圧したときの中立面（半径方向に移動
しない面）が外周寄りに位置せしめられることと
なる。このため、押圧力Ｔによる厚肉円筒部３０
ｂの外径の増大は殆んどなく、該押付力Ｔの殆ん
ど全てが当接面３０ｄの直径の縮小即ち圧接力Ｐ
の増加に変換される。また、上記のように、押付
力Ｔによる内ローラ３０の外径の増加がないので
かかる外径の増大により該内ローラ３０の外周３
０ｅとこれが嵌合するケーシング１０の嵌合孔の
内周とが接触して両者間に摩擦を生じ、押付力Ｔ
が摩擦で吸収されるようなことはなく、内ローラ
３０は嵌合孔１０ａ内で抵抗なく伸縮できる。こ
のため押付力Ｔは全て圧接力Ｐに変換され、また
押付力Ｔを減じたときの復元も円滑に行われるの
で押付力Ｔに比例した圧接力Ｐを得ることができ
る。 In the inner roller 30, the pressing force T is applied to the side end face of the thick cylindrical part 30b with high rigidity, and the contact surface 30d is formed on the thin cylindrical part 30a with high deformability. When the roller 30 is pressed in the axial direction of the rotating shaft, the neutral surface (the surface that does not move in the radial direction) is positioned closer to the outer periphery. Therefore, the thick cylindrical portion 30 due to the pressing force T
There is almost no increase in the outer diameter of b, and almost all of the pressing force T is reduced by the diameter of the contact surface 30d, that is, the pressing force P
is converted into an increase in Further, as described above, since the outer diameter of the inner roller 30 does not increase due to the pressing force T, the outer circumference 3 of the inner roller 30 is
0e and the inner periphery of the fitting hole of the casing 10 into which it is fitted come into contact and create friction between them, resulting in a pressing force T
is not absorbed by friction, and the inner roller 30 can expand and contract within the fitting hole 10a without resistance. Therefore, all the pressing force T is converted into the pressing force P, and the restoration when the pressing force T is reduced is also performed smoothly, so that the pressing force P proportional to the pressing force T can be obtained.
上記の事項を第４図及び第５図を参照して更に
詳しく説明する。第４図及び第５図は本発明に係
る内ローラ３０と特開昭51−148158号に示される
従来例の内ローラ１０とを比較したものである。 The above matters will be explained in more detail with reference to FIGS. 4 and 5. 4 and 5 are comparisons between the inner roller 30 according to the present invention and the conventional inner roller 10 shown in Japanese Patent Application Laid-Open No. 148158/1983.
本発明に係る内ローラは、相手ローラとの当接
部即ち内周側に薄肉で変形能の大きい薄肉円筒部
が、該当接部から半径方向に離隔した部位即ち外
周側に剛性の大きい厚肉円筒部が夫々形成されて
いるので、第４図ａに示すように、該内ローラ３
０を軸方向に押圧したときの中立面Ａ１が外周寄
りに位置する。このため第５図ａに鎖線で示すよ
うに、押付力Ｔを加えたときの中立面Ａ１よりも
外周側の半径方向移動量即ち外径の増加量は殆ん
どなく、押付力Ｔはその殆んどが内径の縮小量ｅ
即ち圧接力Ｐの増加に変換される。 The inner roller according to the present invention has a thin cylindrical portion having a thin wall and high deformability at the contact portion with the mating roller, that is, the inner circumference side, and a thick wall portion having high rigidity at a portion radially distant from the contact portion, that is, the outer circumference side. Since the cylindrical portions are respectively formed, as shown in FIG. 4a, the inner roller 3
0 is pressed in the axial direction, the neutral plane A1 is located near the outer periphery. Therefore, as shown by the chain line in Fig. 5a, when the pressing force T is applied, there is almost no radial movement on the outer circumference side of the neutral plane A1, that is, an increase in the outer diameter, and the pressing force T is Most of this is the reduction in inner diameter e
That is, this is converted into an increase in the pressure contact force P.
つまり、本発明においては、変形態の大きい薄
肉円筒部３０ａを内周側に、変形能が小さく剛性
の大きい厚肉円筒部３０ｂを外周側に位置せしめ
た弾性ローラとなしているので、単位押付力Ｔ当
りの圧接力Ｐ即ちＰ／Ｔが第４図ｂ及び第５図ｂ
に示す特開昭51−148158号の発明のような従来の
ものよりも格段に大きくなり、小さな押付力で以
つて大きな圧接力を得ることができる。 In other words, in the present invention, since the elastic roller is configured such that the thin cylindrical portion 30a with large deformation is located on the inner periphery side and the thick cylindrical portion 30b with low deformability and high rigidity is located on the outer periphery side, the unit pressing The pressure contact force P per force T, that is, P/T, is as shown in Fig. 4b and Fig. 5b.
It is much larger than conventional ones such as the invention of JP-A No. 51-148158 shown in 1988, and a large pressing force can be obtained with a small pressing force.
更に本発明においては、押付力Ｔを減ずる際の
復元も円滑に行われるので押付力Ｔに比例した圧
接力Ｐを得ることができ、負荷の大きさに対応し
て圧接力を調整するトルクカム装置との結合が極
めて容易にできる。 Furthermore, in the present invention, since the restoration is performed smoothly when the pressing force T is reduced, it is possible to obtain the pressing force P proportional to the pressing force T, and the torque cam device adjusts the pressing force in accordance with the magnitude of the load. It is extremely easy to combine with
対して、第４図ｂ及び第５図ｂに示すような従
来のものは、内ローラ１０が略均一な厚さに形成
されているので、第４図ｂに示すように、これを
軸方向に押圧したときの中立面Ａ２（軸方向押付
力Ｔにより半径方向に移動しない面）が本発明の
ものよりもはるかに内周寄りに位置する。このた
め押付力Ｔを加えたときの、中立面Ａ２よりも外
周側の半径方向移動量即ち外径の増加量が大き
く、該押付力Ｔの相当な部分が外径の増大に変換
され内径の縮小量ｅ即ち圧接力Ｐに変換される量
は少ない。 On the other hand, in the conventional rollers shown in FIGS. 4b and 5b, the inner roller 10 is formed to have a substantially uniform thickness, so that the inner roller 10 is axially rotated as shown in FIG. The neutral surface A2 (the surface that does not move in the radial direction due to the axial pressing force T) when pressed is located much closer to the inner circumference than that of the present invention. Therefore, when the pressing force T is applied, the amount of radial movement on the outer peripheral side, that is, the amount of increase in the outer diameter is larger than the neutral plane A2, and a considerable portion of the pressing force T is converted into an increase in the outer diameter, and the inner diameter The reduction amount e, that is, the amount converted into the pressure contact force P is small.
従つて、上記従来例において、たとえ内ローラ
１０が、ハウジング９の嵌合孔内に嵌合されてい
るとしても、該ローラ１０に上記軸方向押付力Ｔ
を加えると、これの外径増加量が大きいため、第
５図ｂに鎖線で示すように、内ローラ１０の外周
１０ａがハウジング９の内周面９ａ内にくさび状
に喰い込む（長さｌの部分が喰い込む）かまたは
両面１０ａ，９ａが強力に圧接されて過大な摩擦
抵抗が発生する。つまり、押付力T0はその大部
分が上記両面１０ａ，９ａの喰い込み抵抗または
摩擦抵抗に消費され、相手ローラとの間の圧接力
の増加即ち当接部の半径の変化ｅに変換される量
が外径部をフリーにした場合よりも更に少なくな
る。 Therefore, in the conventional example, even if the inner roller 10 is fitted into the fitting hole of the housing 9, the axial pressing force T is applied to the roller 10.
, the increase in the outer diameter is large, so the outer circumference 10a of the inner roller 10 wedges into the inner circumferential surface 9a of the housing 9 (length l), as shown by the chain line in FIG. ), or both surfaces 10a and 9a are strongly pressed together, resulting in excessive frictional resistance. In other words, most of the pressing force T 0 is consumed by the biting resistance or frictional resistance of both surfaces 10a and 9a, and is converted into an increase in the pressing force with the mating roller, that is, a change in the radius of the contact part e. The amount is even smaller than when the outer diameter portion is left free.
このため、上記従来のものは上記Ｐ／Ｔが本発
明よりも格段に小さいばかりか、内ローラをハウ
ジングの嵌合孔内に嵌合した場合は上記のような
喰い込み抵抗または摩擦抵抗のために押付力Ｔを
減じたときの復元が確実に行われず、本発明のよ
うに押付力Ｔに比例した圧接力Ｐは得られなくな
る傾向にある。 For this reason, not only is the P/T of the conventional roller much smaller than that of the present invention, but also the above-mentioned biting resistance or frictional resistance occurs when the inner roller is fitted into the fitting hole of the housing. When the pressing force T is reduced, the restoration is not reliably performed, and there is a tendency that the pressing force P proportional to the pressing force T cannot be obtained as in the present invention.
また、本発明は、変形能の大きい薄肉円筒部に
相手ローラとの当接面を形成し、該薄肉円筒部
を、薄肉円板部を介して剛性の大きい厚肉円筒部
に連結しているので、薄肉円筒部が確実にクラウ
ニング変形することによりクラウニング変形量Ｃ
が大きくなる。 Further, in the present invention, a contact surface with a mating roller is formed on a thin cylindrical portion having a large deformability, and the thin cylindrical portion is connected to a thick cylindrical portion having a high rigidity via a thin disk portion. Therefore, the amount of crowning deformation C is reduced by ensuring the crowning deformation of the thin-walled cylindrical part.
becomes larger.
このため相手ローラの間に片当りが発生するこ
とはない。一方上記従来のものにおいては、内ロ
ーラはほぼ均一厚さであるので、側板部が変形を
起し易く当然本発明のものよりもクラウニング変
形量Ｃが格段に少なくなる。このため圧接面に片
当りが発生する恐れがある。 Therefore, uneven contact will not occur between the mating rollers. On the other hand, in the above-mentioned conventional roller, since the inner roller has a substantially uniform thickness, the side plate portion is easily deformed, and the amount of crowning deformation C is naturally much smaller than that of the roller of the present invention. For this reason, there is a possibility that uneven contact will occur on the pressure contact surface.
第６図に、軸方向押付力Ｔと半径方向変形量
（Ｃ＋ｅ）との関係を、厚肉円筒部３０ｂの厚さ
t1と薄肉円筒部３０ａの厚さt2をパラメータにし
て示す。 FIG. 6 shows the relationship between the axial pressing force T and the amount of radial deformation (C+e) depending on the thickness of the thick cylindrical portion 30b.
t 1 and the thickness t 2 of the thin cylindrical portion 30a are shown as parameters.
図から明らかなように、本発明においては、
t1／t2が大きくなるに従い半径方向変形量が増大
し大きな圧接力を得ることができる。対して第４
図ｂ及び第５図ｂに示す従来例は、t1／t2≒１で
あるために半径方向変形量が小さく、一定の押付
力T1以上になると内ローラの外周がハウジング
と接触し摩擦抵抗が増加して、半径方向変形量が
減少する。 As is clear from the figure, in the present invention,
As t 1 /t 2 becomes larger, the amount of radial deformation increases and a larger pressing force can be obtained. against the fourth
In the conventional example shown in Fig. b and Fig. 5b, since t 1 /t 2 ≒ 1, the amount of radial deformation is small, and when the pressing force exceeds a certain value T 1 , the outer periphery of the inner roller comes into contact with the housing, causing friction. The resistance increases and the amount of radial deformation decreases.
第７図は本発明の他の実施例を示し、この場合
は、太陽ローラ１００を第２図のものと同様な弾
性ローラにて形成して、その内周スプライン部１
００ａを入力軸８０のスプライン８０ａに該入力
軸８０の軸方向に伸縮可能にして嵌合し、ナツト
１９の締め込み量により太陽ローラ１００の全幅
Wtを変化させ押付力Ｔを調整している。３はケ
ーシング１０に固着された内ローラ、８０は入力
軸であり、太陽ローラ１００は該入力軸８０に固
着されている。その他の構成は上記第１実施例の
場合と同様である。この実施例の場合はナツト１
９を締め込み全幅Wtを縮小せしめると太陽ロー
ラ１００の外径Dsが増加しようとするが遊星ロ
ーラ２により外径Dsの増加が拘束され、この拘
束分に見合う量の圧接力Ｐが発生する。 FIG. 7 shows another embodiment of the present invention, in which the sun roller 100 is formed of an elastic roller similar to that of FIG.
00a is fitted to the spline 80a of the input shaft 80 so that it can expand and contract in the axial direction of the input shaft 80, and the total width of the sun roller 100 is adjusted by the tightening amount of the nut 19.
The pressing force T is adjusted by changing Wt. 3 is an inner roller fixed to the casing 10, 80 is an input shaft, and the sun roller 100 is fixed to the input shaft 80. The other configurations are the same as in the first embodiment. In this example, nut 1
9 to reduce the full width Wt, the outer diameter Ds of the sun roller 100 tends to increase, but the increase in the outer diameter Ds is restrained by the planetary roller 2, and a pressing force P corresponding to this restraint is generated.
該圧接力Ｐはナツト１９の締め込み量に比例す
る。 The pressing force P is proportional to the amount by which the nut 19 is tightened.
第８図は本発明の更に他の実施例を示し、この
場合は遊星ローラ２００を第２図のものと同様な
弾性ローラにて形成して遊星ピン５に軸受４を介
して該ピン５の軸方向に伸縮可能にして支承せし
め、遊星ローラ２００の厚肉円筒部に円周方向に
等分に締付けボルト１８を設け、ナツト１７の締
め込み量を変化させることにより押付力Ｔを調整
している。 FIG. 8 shows still another embodiment of the present invention, in which the planetary roller 200 is formed of an elastic roller similar to that in FIG. The planetary roller 200 is supported by being extendable and contractible in the axial direction, and tightening bolts 18 are provided equally in the circumferential direction on the thick cylindrical portion of the planetary roller 200, and the pressing force T is adjusted by changing the tightening amount of the nut 17. There is.
即ちナツト１７を締め込み遊星ローラ２００の
全幅Wtを縮小せしめると直径Dpの膨張が拘束さ
れこの拘束分に見合う圧接力Ｐが発生する。１は
入力軸８に固定された太陽ローラ、３はケーシン
グ１０に固定された内ローラである。その他の構
成は第１実施例の場合と同様である。 That is, when the nut 17 is tightened to reduce the total width Wt of the planetary roller 200, the expansion of the diameter Dp is restrained, and a pressing force P corresponding to this restraint is generated. 1 is a sun roller fixed to the input shaft 8, and 3 is an inner roller fixed to the casing 10. The other configurations are the same as in the first embodiment.
第９図は弾性部材から成る内ローラ３０を複列
型（この実施例では２列）に形成した場合を示
し、薄肉円筒部３０ａ、厚肉円筒部３０ｂ、薄肉
円板部３０ｃの形状及びこれらの結合態様は第２
図の場合と同様である。同図において２は遊星ロ
ーラを示す。 FIG. 9 shows a case in which the inner roller 30 made of an elastic member is formed in a double row type (two rows in this embodiment), and shows the shapes of the thin cylindrical portion 30a, the thick cylindrical portion 30b, and the thin disk portion 30c, and the shapes thereof. The binding mode is the second
This is the same as the case shown in the figure. In the figure, 2 indicates a planetary roller.
第１０図は太陽ローラ１００を複列型の弾性ロ
ーラとした場合を示し、１００ａは薄肉円筒部、
１００ｂは厚肉円筒部、１００ｃは薄肉円板部で
ありこれら要素の形状及び結合態様は第６図の場
合と同様である。１００ｄは遊星ローラ２との当
接面である。 FIG. 10 shows a case where the sun roller 100 is a double-row type elastic roller, and 100a is a thin cylindrical portion;
100b is a thick cylindrical part, 100c is a thin disc part, and the shape and manner of connection of these elements are the same as in the case of FIG. 100d is a contact surface with the planetary roller 2.
尚、図示を省略したが遊星ローラを第１０図と
同様に複列型に形成することも勿論可能である。
また上記の各実施例においては、太陽ローラ、遊
星ローラ、内ローラの内、何れか１つを弾性ロー
ラとしたが、上記各ローラの一部または全部を弾
性ローラとしてもよい。 Incidentally, although not shown, it is of course possible to form the planetary rollers in a double-row type as in FIG. 10.
Further, in each of the above embodiments, any one of the sun roller, planetary roller, and inner roller is an elastic roller, but a part or all of the rollers may be an elastic roller.
本発明は以上のように構成されており、本発明
によれば次の効果がある。 The present invention is configured as described above, and the present invention has the following effects.
(1) 厚肉円筒部を外周側に薄肉円筒部を内周側に
夫々形成し（太陽ローラ及び遊星ローラの場合
は（厚肉円筒部を内周側に薄肉円筒部を外周側
に夫々形成）、両者を薄肉円板部で結合する構
造としたので、均一厚さのローラを備えた従来
のものに較べクラウニング変形量を大きくとる
ことができ、小さな軸方向押付力で以つて大き
な圧接力を得ることができる。(1) A thick cylindrical part is formed on the outer periphery and a thin cylindrical part is formed on the inner periphery (in the case of sun rollers and planetary rollers (a thick cylindrical part is formed on the inner periphery and a thin cylindrical part is formed on the outer periphery). ), the structure is such that the two are connected by a thin disc part, so the amount of crowning deformation can be larger than that of conventional rollers with uniform thickness, and a large pressing force can be achieved with a small axial pressing force. can be obtained.
(2) 厚肉円筒部の側端に機械的に軸方向押付力を
附与して薄肉円板部を介して薄肉円筒部に伝達
し、薄肉円筒部にクラウニング変形を生起させ
るものであるので、装置が簡単かつ低コストで
あり油洩れ等の不具合の発生がないことから信
頼性が高い。(2) Since an axial pressing force is mechanically applied to the side end of the thick-walled cylindrical portion and transmitted to the thin-walled cylindrical portion via the thin-walled disk portion, crowning deformation is caused in the thin-walled cylindrical portion. The device is simple and low cost, and is highly reliable as it does not cause problems such as oil leakage.
(3) 弾性ローラの他のローラへの当接部が薄肉に
形成されているため、この部分の変形態が大き
くケーシング等の加工誤差により各ローラ間が
片当りしようとしても薄肉部で強い当りを吸収
することにより片当りの発生を防止することが
できる。従つて装置の耐久性が向上する。(3) Since the contact part of the elastic roller with other rollers is formed with a thin wall, this part is highly deformed and even if the rollers try to contact unevenly due to machining errors in the casing, etc., there will be strong contact in the thin part. By absorbing this, uneven hitting can be prevented. Therefore, the durability of the device is improved.
(4) この種ローラは転動面の高硬度が要求される
ので、通常、焼入れ、浸炭等の熱処理が施され
るが、本発明は剛性の高い厚肉円筒部を有する
ので、熱処理時においてはこれが熱変形の拘束
部材として作用することにより、熱変形は極め
て小さくなる。また厚肉円筒部を有するのでロ
ーラの断面係数が大きく、このため機械加工に
おけるローラの変形がなく加工が容易で加工精
度も高い。(4) Since this type of roller requires high hardness of the rolling surface, it is usually subjected to heat treatment such as quenching and carburizing, but since the present invention has a thick cylindrical portion with high rigidity, Since this acts as a restraining member for thermal deformation, thermal deformation becomes extremely small. Furthermore, since the roller has a thick cylindrical portion, the section modulus of the roller is large, and therefore the roller does not deform during machining, making it easy to process and providing high processing accuracy.
第１図ないし第６図は本発明の１実施例を示
し、第１図は回転軸の軸線に沿う断面図、第２図
は弾性ローラの形状を示す断面図、第３図は押付
力の変化を示す線図、第４図、第５図、第６図は
作用を示す線図である。第７図ないし第１０図は
本発明の他の実施例を示し、第７図及び第８図は
第１図に応当する図、第９図、第１０図は弾性ロ
ーラの１例を示す断面図である。
１，１００……太陽ローラ、２，２００……遊
星ローラ、３，３０……内ローラ、６……キヤリ
ヤ、８，８０……入力軸、１０……ケーシング、
１１……出力軸、１５……シム。
1 to 6 show one embodiment of the present invention, FIG. 1 is a sectional view along the axis of the rotating shaft, FIG. 2 is a sectional view showing the shape of the elastic roller, and FIG. 3 is a sectional view of the pressing force. Diagrams showing changes, FIGS. 4, 5, and 6 are diagrams showing effects. 7 to 10 show other embodiments of the present invention, FIGS. 7 and 8 are views corresponding to FIG. 1, and FIGS. 9 and 10 are cross sections showing one example of the elastic roller. It is a diagram. 1,100...Sun roller, 2,200...Planet roller, 3,30...Inner roller, 6...Carrier, 8,80...Input shaft, 10...Casing,
11...Output shaft, 15...Shim.
Claims (1)
止部材に固定された内ローラの内周にそれぞれ当
接される複数個の遊星ローラを、回転軸に連結さ
れたキヤリヤにて軸支することにより、上記２本
の回転軸間に動力を伝達するものにおいて、上記
太陽ローラ、遊星ローラ及び内ローラの全部また
は一部を、上記回転軸の軸方向に区切つて形成さ
れると共に押付力が附与される側端面を有する複
数個の厚肉円筒部と、該厚肉円筒部よりも薄肉に
形成され内外周面の何れか一方が相手ローラとの
当接面とされると共に上記押付力が附与されたと
き該当接面がクラウニング変形可能にされた薄肉
円筒部と、上記厚肉円筒部よりも薄肉に形成され
上記薄肉円筒部の両側端を上記厚肉円筒部に個別
に接続する薄肉円板部とから成り、上記厚肉円筒
部の両側端を押圧したとき上記薄肉円筒部の直径
が変化せしめられる弾性ローラにて構成し、上記
弾性ローラは、静止部材、入力軸等該ローラが嵌
合される部材上を上記回転軸の軸方向に伸縮可能
に設けられ、かつ上記弾性ローラを回転軸の軸方
向に機械的に押圧する手段を具えてなることを特
徴とする遊星ローラ式動力伝達装置。1. By pivotally supporting a plurality of planetary rollers that are in contact with the outer periphery of a sun roller connected to a rotating shaft and the inner periphery of an inner roller fixed to a stationary member, respectively, with a carrier connected to a rotating shaft. , in which power is transmitted between the two rotating shafts, all or part of the sun roller, planetary roller, and inner roller are divided in the axial direction of the rotating shaft, and a pressing force is applied. a plurality of thick-walled cylindrical portions having side end surfaces that are shaped like a roller, and one of the inner and outer circumferential surfaces of the thick-walled cylindrical portions, which are formed thinner than the thick-walled cylindrical portions, as a contact surface with the mating roller, and the pressing force is applied. a thin-walled cylindrical portion whose contact surface is capable of crowning deformation when a given contact surface is given; and a thin-walled circle formed thinner than the thick-walled cylindrical portion and individually connects both ends of the thin-walled cylindrical portion to the thick-walled cylindrical portion. It consists of an elastic roller that changes the diameter of the thin-walled cylindrical section when both ends of the thick-walled cylindrical section are pressed. A planetary roller type power transmission characterized by comprising a means that is extendable and retractable in the axial direction of the rotating shaft on the members to be joined, and that mechanically presses the elastic roller in the axial direction of the rotating shaft. Device.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1835978A JPS54111049A (en) | 1978-02-20 | 1978-02-20 | Planetary roller type power transmission device with elastic roller |
| US06/010,255 US4483216A (en) | 1978-02-20 | 1979-02-07 | Planetary-roller transmission with elastic roller or ring |
| DE7979100418T DE2967254D1 (en) | 1978-02-20 | 1979-02-13 | Planetary-roller transmission with elastic roller or ring |
| EP79100418A EP0003793B1 (en) | 1978-02-20 | 1979-02-13 | Planetary-roller transmission with elastic roller or ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1835978A JPS54111049A (en) | 1978-02-20 | 1978-02-20 | Planetary roller type power transmission device with elastic roller |
Related Child Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6175381A Division JPS57200754A (en) | 1981-04-23 | 1981-04-23 | Planetary roller type power transmission provided with elastic roller |
| JP13939181A Division JPS57200755A (en) | 1981-09-04 | 1981-09-04 | Planetary roller type power transmission provided with elastic roller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS54111049A JPS54111049A (en) | 1979-08-31 |
| JPS6246742B2 true JPS6246742B2 (en) | 1987-10-05 |
Family
ID=11969490
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1835978A Granted JPS54111049A (en) | 1978-02-20 | 1978-02-20 | Planetary roller type power transmission device with elastic roller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS54111049A (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6336202Y2 (en) * | 1979-03-16 | 1988-09-26 | ||
| JPS5659054A (en) * | 1979-10-18 | 1981-05-22 | Mitsubishi Heavy Ind Ltd | Rolling transmission type planetary roller device |
| JPS5793073U (en) * | 1980-11-28 | 1982-06-08 | ||
| JPS5818149U (en) * | 1981-07-28 | 1983-02-04 | 三菱重工業株式会社 | Planetary roller type power transmission device |
| JPS58145064U (en) * | 1982-03-24 | 1983-09-29 | 三菱重工業株式会社 | Servo motor device for position control |
| JPS60150354U (en) * | 1984-03-17 | 1985-10-05 | 三菱重工業株式会社 | reduction gear |
| JPH0214685Y2 (en) * | 1985-02-15 | 1990-04-20 | ||
| JPS6250366U (en) * | 1986-09-04 | 1987-03-28 |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51148158A (en) * | 1975-06-04 | 1976-12-20 | Skf Nova Ab | Planetary toothed wheel gearing |
-
1978
- 1978-02-20 JP JP1835978A patent/JPS54111049A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51148158A (en) * | 1975-06-04 | 1976-12-20 | Skf Nova Ab | Planetary toothed wheel gearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS54111049A (en) | 1979-08-31 |
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