JP3049076B2 - Drive transmission device - Google Patents
Drive transmission deviceInfo
- Publication number
- JP3049076B2 JP3049076B2 JP2116020A JP11602090A JP3049076B2 JP 3049076 B2 JP3049076 B2 JP 3049076B2 JP 2116020 A JP2116020 A JP 2116020A JP 11602090 A JP11602090 A JP 11602090A JP 3049076 B2 JP3049076 B2 JP 3049076B2
- Authority
- JP
- Japan
- Prior art keywords
- roller
- pin
- disk
- axis
- long groove
- 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
Links
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Electrophotography Configuration And Component (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、駆動力を伝達する駆動伝達装置に関する。Description: TECHNICAL FIELD The present invention relates to a drive transmission device for transmitting a driving force.
従来の技術 第４図乃至第７図は、従来からよく使用されている小
型で安価な駆動伝達装置である軸継手の例を示す。2. Description of the Related Art FIGS. 4 to 7 show examples of a shaft coupling which is a small and inexpensive drive transmission device often used in the past.
第４図は古来から使用されているオルダム式軸継手で
ある。この軸継手は、両面に互いに直角の一文字突起を
持つ円板と、この円板の両面側にその一文字突起と嵌合
する一文字形の溝を設けたフランジとを組み合わせて構
成している。この場合、軸に偏心があると突起が溝内で
長手方向に摺動しつつこれを吸収する。従って、中間の
円板と両側のフランジとは互いに摺擦しつつ複雑な運転
をし、ラジアル方向に大きな反力を発生させ、従動側が
大きく振られる要因となり、又高速回転に適しない。更
に各構成体がそれぞれ別個の３種類の円板であるため、
組立及び解体・保守が面倒で部品を紛失するおそれもあ
った。FIG. 4 shows an Oldham type shaft coupling which has been used since ancient times. This shaft coupling is configured by combining a disk having single-letter projections perpendicular to each other on both sides, and a flange having a single-letter groove fitted on the both-sides of the disk to fit the single-letter projection. In this case, if the shaft is eccentric, the protrusion absorbs this while sliding in the longitudinal direction in the groove. Therefore, the intermediate disk and the flanges on both sides perform complicated operations while rubbing each other, generating a large reaction force in the radial direction, causing a large swing on the driven side, and are not suitable for high-speed rotation. Furthermore, since each component is a separate three types of disks,
Assembly, disassembly and maintenance were troublesome, and parts could be lost.
第５図は板ばね式の軸継手である。この構造のもので
は、僅かの偏心、偏角は板ばねの撓みにより吸収するこ
とができるが、板ばねの張力によりオルダム式の軸継手
と同様にラジアル方向の反力が発生する。又駆動側及び
従動側の軸方向距離の自由度が極めて少ないという不具
合もある。FIG. 5 shows a leaf spring type shaft coupling. In this structure, slight eccentricity and declination can be absorbed by bending of the leaf spring, but a radial reaction force is generated by the tension of the leaf spring, similarly to the Oldham type shaft coupling. There is also a disadvantage that the degree of freedom of the axial distance between the driving side and the driven side is extremely small.
第６図はコイルばね式軸継手であるが、この形式のも
のも板ばね式のものと同様の特性のである。FIG. 6 shows a coil spring type shaft coupling, which has the same characteristics as those of the plate spring type.
第７図はタイヤ形のゴム継手を示す。この構造のもの
では、駆動側と従動側の軸方向距離の自由度は比較的多
いが、偏心・偏角の吸収がゴムの弾性率に左右されるた
め、ラジアル方向の反力はかなり発生する。即ち、伝達
トルクが大きい程弾性率を大きく（硬く）しなければな
らないため、反力も伝達トルクに比例して大きくなる。FIG. 7 shows a tire-shaped rubber joint. In this structure, the degree of freedom in the axial distance between the drive side and the driven side is relatively large, but the absorption of eccentricity and declination depends on the elastic modulus of rubber, so that a considerable amount of radial reaction force is generated. . That is, since the elastic modulus must be increased (hardened) as the transmission torque increases, the reaction force also increases in proportion to the transmission torque.
以上の如く従来の軸継手では、大きなラジアル方向の
反力が発生すると共に、駆動側、従動側の軸方向の距離
の自由度が少なく、取付け精度、保持構造に特別の注意
を必要とした。As described above, in the conventional shaft coupling, a large radial reaction force is generated, the degree of freedom in the axial direction on the driving side and the driven side is small, and special attention is required for the mounting accuracy and the holding structure.
発明が解決しようとする課題 本発明は従来技術に於ける上記問題を解決し、許容量
が大きく、偏心状態におけるラジアル方向の反力が小さ
く、小型且つ安価であり、しかも着脱及び部品の保守・
管理の容易な駆動伝達装置を提供することを課題とす
る。Problems to be Solved by the Invention The present invention solves the above-mentioned problems in the prior art, has a large allowance, a small radial reaction force in an eccentric state, is small and inexpensive, and has a detachable / maintenance and maintenance of parts.
It is an object to provide a drive transmission device that can be easily managed.
課題を解決するための手段 本発明は上記課題を解決するために、請求項１の発明
は、１軸まわりに回転される第１部材と、第２部材と、
第３部材とを有し、前記第１部材は、前記１軸から半径
方向の互いに正反対方向の離れた位置に、前記１軸に平
行な第１ピンと第２ピンとを備え、該第１ピンと第２ピ
ンとはそれぞれ第１ローラと第２ローラとを回転自在に
軸支し、前記第２部材は、前記１軸から半径方向の互い
に正反対方向の離れた位置に前記１軸に平行な第３ピン
と第４ピンとを備え、該第３ピンと第４ピンとはそれぞ
れ第３ローラと第４ローラとを回転自在に軸支し、更に
前記半径方向に長く切り欠いたそれぞれ前記第１ローラ
及び第２ローラの回転を案内する第１長溝と第２長溝と
を備え、前記第３部材は、半径方向に長く切り欠いたそ
れぞれ前記第１ローラ及び第２ローラの回転を案内する
第３長溝と第４長溝とを備え、前記第１ローラ及び第２
ローラは、前記第１ピン及び第２ピンの自由端側に、前
記第２部材の抜け出しを止める鍔を、前記第３ローラ及
び第４ローラは、前記第３ピン及び第４ピンの自由端側
に、前記第３部材の抜け出しを止める鍔をそれぞれ有
し、前記第１部材と第２部材と第３部材とを順次配列し
該前記第１部材と第３部材との間で駆動力を伝達するこ
とことを特徴とする。Means for Solving the Problems In order to solve the above problems, the present invention provides a first member rotated around one axis, a second member,
A third member, wherein the first member includes a first pin and a second pin parallel to the one axis at positions distant from each other in the radial direction from the one axis in the diametrically opposite directions. The two pins rotatably support the first roller and the second roller, respectively, and the second member includes a third pin parallel to the one axis at a position diametrically opposite to the one axis in a direction opposite to each other. A fourth pin, wherein the third pin and the fourth pin rotatably support the third roller and the fourth roller, respectively, and further include the first roller and the second roller each of which is notched long in the radial direction. A first long groove and a second long groove for guiding rotation, wherein the third member has a third long groove and a fourth long groove for guiding rotation of the first roller and the second roller, respectively, which are notched long in a radial direction; The first roller and the second roller
The roller has a flange on the free end side of the first pin and the second pin for stopping the second member from coming out. The third roller and the fourth roller are free end sides of the third pin and the fourth pin. Each having a flange for stopping the third member from coming off, the first member, the second member, and the third member being sequentially arranged to transmit a driving force between the first member and the third member. It is characterized by doing.
作用 本発明によれば、ローラに鍔を設けて第２部材又は第
３部材の抜け出しを防止することにより、又は第１部材
乃至第３部材に設けた穴に支持軸を通して第１部材及び
第３部材を位置規制し、その間隙を維持することによ
り、第１部材から第３部材までが一体化される。According to the present invention, the first member and the third member are provided by providing the roller with a flange to prevent the second member or the third member from coming off, or by passing the support shaft through the holes provided in the first member to the third member. By regulating the position of the member and maintaining the gap, the first to third members are integrated.
実施例 第１図（ａ）、（ｂ）及び第２図は本発明に係る駆動
伝達装置の前提となる軸継手について説明する。Embodiment FIGS. 1 (a), (b) and FIG. 2 explain a shaft coupling which is a premise of a drive transmission device according to the present invention.
第１部材の一例である円盤１には、第１ピン及び第２
ピンとしての軸1a及び軸1bがかしめ等により固着されて
いる。軸1a、1bは軸Ｘを中心として互いに正反対方向の
離れた位置にあり、軸Ｘに平行に設けられている。軸1a
及び軸1bは、それぞれ円盤１からスペーサ２、３を介し
て第１ローラ及び第２ローラとしてのローラ４及びロー
ラ５を回転自在に軸支している。ローラ４及びローラ５
はそれぞれＥリング６及びＥリング７により軸1a及び軸
1bから抜けないように位置保持されている。The disk 1 as an example of the first member has a first pin and a second pin.
The shaft 1a and the shaft 1b as pins are fixed by caulking or the like. The shafts 1a and 1b are separated from each other in the diametrically opposite directions about the axis X, and are provided in parallel with the axis X. Axis 1a
The shaft 1b rotatably supports a roller 4 and a roller 5 as first and second rollers from the disk 1 via spacers 2 and 3, respectively. Roller 4 and roller 5
Are the shaft 1a and the shaft by the E-ring 6 and the E-ring 7, respectively.
It is held so that it does not fall out of 1b.
第２部材の一例である円盤８には、円盤１と同様に、
それぞれ第３ピン及び第４ピンとしての軸8a及び8b上に
スペーサ９及びスペーサ10を介して第３ローラ及び第４
ローラとしてのローラ11及びローラ12が回転自在に軸支
され、それぞれＥリング13及びＥリング14で軸方向位置
が規制されている。The disk 8 as an example of the second member has the same structure as the disk 1,
A third roller and a fourth roller are disposed on shafts 8a and 8b as third and fourth pins via spacers 9 and 10, respectively.
Rollers 11 and 12 serving as rollers are rotatably supported, and their axial positions are regulated by E-rings 13 and 14, respectively.
円盤８は更に、半径方向に長いそれぞれ第１長溝及び
第２長溝としての切欠き8c及び切欠き8dを備え、それぞ
れローラ４及びローラ５を嵌入しその回転を案内するよ
うにしている。切欠き8c、8dは、ローラ４、５の外径よ
り僅かに大きい幅で且つある程度平滑に形成され、ロー
ラ４、５が円滑に回転するようにしている。The disk 8 further includes a notch 8c and a notch 8d as a first long groove and a second long groove, respectively, which are long in the radial direction, and the rollers 4 and 5 are fitted therein to guide the rotation thereof. The notches 8c and 8d have a width slightly larger than the outer diameter of the rollers 4 and 5, and are formed to some extent smooth, so that the rollers 4 and 5 rotate smoothly.
第３部材の一例である円盤15には、それぞれ第３長溝
及び第４長溝としての切欠き15a及び切欠き15bが円盤８
と同様に設けられ、それぞれローラ11及びローラ12を間
隙を持って嵌合しこれらを案内している。A notch 15a and a notch 15b as a third long groove and a fourth long groove, respectively, are formed on the disk 15 as an example of the third member.
The roller 11 and the roller 12 are fitted with a gap therebetween to guide them.
このような構成により、円盤１は円盤８に対してロー
ラ４、５の滑らかな回転により１半径方向に自由に動く
ことができ、円盤15も同様に円盤８に対して他の半径方
向（この実施例の場合には円盤１の動く方向と直角の方
向）に自由に動くことができる。従って円盤１と円盤15
とは相対的に一定の面積の範囲で変位することが可能と
なる。本実施例では、第１図（ａ）に示す如くローラ外
径と切欠きとの間隙をδとしているので、δ×δの面積
範囲が変位可能範囲となる。With such a configuration, the disk 1 can freely move in one radial direction with the smooth rotation of the rollers 4 and 5 with respect to the disk 8, and the disk 15 likewise moves in the other radial direction (this In the case of the embodiment, it is possible to freely move in the direction perpendicular to the direction in which the disk 1 moves. Therefore, disk 1 and disk 15
Can be displaced within a relatively constant area. In this embodiment, the gap between the roller outer diameter and the notch is δ as shown in FIG. 1 (a), so that the area range of δ × δ is the displaceable range.
この結果、例えば第２図で破線に示す如く、円盤１及
び円盤15に駆動軸又は従動軸となる回転軸30及び31が結
合された場合において、回転軸30と31との間に偏心が生
じたときには、中間の円盤８が円盤１と円盤15との間で
滑らかに動いて円盤１及び円盤15に大きなラジアル方向
の力を作用させず、円盤１と円盤15とはそれぞれ偏心し
たその位置で互いに振り回されたり振動したりすること
なく円滑に回転する。As a result, when the rotating shafts 30 and 31 serving as drive shafts or driven shafts are coupled to the disk 1 and the disk 15 as shown by broken lines in FIG. 2, for example, eccentricity occurs between the rotating shafts 30 and 31. In this case, the intermediate disk 8 moves smoothly between the disk 1 and the disk 15 without exerting a large radial force on the disk 1 and the disk 15, and the disk 1 and the disk 15 are respectively eccentric at the respective positions. They rotate smoothly without being swung or shaken by each other.
そして、請求項１の発明では第３図に示すように構成
している。In the invention of claim 1, the configuration is as shown in FIG.
ローラ４、５はそれぞれ鍔4a、4bを有し、ローラ11、
12も同様に鍔11a、12aを有する。このように鍔を設ける
ことにより、円盤８及び円盤15は、それぞれスペーサ
２、３と鍔4a、4bの間及びスペーサ９、10と鍔11a、12a
との間に挟まれて、それぞれ軸方向位置が規制され、円
盤８、円盤15を一体化することができる。The rollers 4 and 5 have flanges 4a and 4b, respectively.
12 also has flanges 11a and 12a. By providing the flanges in this manner, the disks 8 and 15 can be moved between the spacers 2 and 3 and the flanges 4a and 4b and between the spacers 9 and 10 and the flanges 11a and 12a, respectively.
, The axial position of each is regulated, and the disk 8 and the disk 15 can be integrated.
なお以上実施例でば、第１部材乃至第３部材を円盤状
部材として示したが、これらの部材を他の適当な形状に
することができるのは勿論である。In the above embodiment, the first to third members are shown as disc-shaped members. However, it is needless to say that these members can be formed into other appropriate shapes.
効果 以上の如く本発明によれば、第１部材乃至第３部材が
一体化されるので組立の自動化が可能となり、又着脱及
び部品の保守・管理が容易になり部品の紛失等を防止す
ることができる。Effects As described above, according to the present invention, the first member to the third member are integrated, so that the assembling can be automated, the attachment / detachment and maintenance / management of the parts are facilitated, and the parts are prevented from being lost. Can be.
第１図（ａ）は本発明の実施例の駆動伝達装置の正面
図、同図（ｂ）はその（ｂ）−（ｂ）線断面図、第２図
はその分解斜視図、第３図は他の実施例の側断面図、第
４図乃至第７図は従来の軸継手の説明図である。 １、８、15…円盤（それぞれ第１乃至第３部材） 1a、1b、8a、8b…軸（それぞれ第１乃至第４ピン） ４、５、11、12…ローラ（それぞれ第１乃至第４ロー
ラ） 8c、8d、15a、15b…切欠き（それぞれ第１乃至第４長
溝） 4a、5a、11a、12a…鍔 16…支持軸 1c、8c、15c…穴 Ｘ…軸（１軸）1 (a) is a front view of a drive transmission device according to an embodiment of the present invention, FIG. 1 (b) is a sectional view taken along the line (b)-(b), FIG. 2 is an exploded perspective view thereof, and FIG. Is a side sectional view of another embodiment, and FIGS. 4 to 7 are explanatory views of a conventional shaft coupling. 1, 8, 15 ... disks (first to third members, respectively) 1a, 1b, 8a, 8b ... shafts (first to fourth pins) 4, 5, 11, 12 ... rollers (first to fourth, respectively) Rollers) 8c, 8d, 15a, 15b ... Notches (first to fourth long grooves, respectively) 4a, 5a, 11a, 12a ... Flange 16 ... Support shafts 1c, 8c, 15c ... Holes X ... Shafts (one shaft)
フロントページの続き (56)参考文献 特開 昭60−146919（ＪＰ，Ａ) 特開 平２−240411（ＪＰ，Ａ) 実開 平１−146015（ＪＰ，Ｕ) 実開 昭49−131438（ＪＰ，Ｕ) 実開 昭64−38904（ＪＰ，Ｕ) 実開 昭51−153356（ＪＰ，Ｕ) 実開 平２−83886（ＪＰ，Ｕ) 実公 昭40−9608（ＪＰ，Ｙ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F16D 3/04 Continuation of the front page (56) References JP-A-60-146919 (JP, A) JP-A-2-240411 (JP, A) JP-A-1-146015 (JP, U) JP-A-49-131438 (JP) , U) Japanese Utility Model Showa 64-38904 (JP, U) Japanese Utility Model Showa 51-153356 (JP, U) Japanese Utility Model Utility Model Hei 2-83886 (JP, U) Japanese Utility Model Showa 40-9608 (JP, Y1) (58) Field surveyed (Int.Cl. 7 , DB name) F16D 3/04
Claims (1)
部材と、第３部材とを有し、 前記第１部材は、前記１軸から半径方向の互いに正反対
方向の離れた位置に、前記１軸に平行な第１ピンと第２
ピンとを備え、該第１ピンと第２ピンとはそれぞれ第１
ローラと第２ローラとを回転自在に軸支し、 前記第２部材は、前記１軸から半径方向の互いに正反対
方向の離れた位置に前記１軸に平行な第３ピンと第４ピ
ンとを備え、該第３ピンと第４ピンとはそれぞれ第３ロ
ーラと第４ローラとを回転自在に軸支し、更に前記半径
方向に長く切り欠いたそれぞれ前記第１ローラ及び第２
ローラの回転を案内する第１長溝と第２長溝とを備え、 前記第３部材は、半径方向に長く切り欠いたそれぞれ前
記第１ローラ及び第２ローラの回転を案内する第３長溝
と第４長溝とを備え、 前記第１ローラ及び第２ローラは、前記第１ピン及び第
２ピンの自由端側に、前記第２部材の抜け出しを止める
鍔を、前記第３ローラ及び第４ローラは、前記第３ピン
及び第４ピンの自由端側に、前記第３部材の抜け出しを
止める鍔をそれぞれ有し、 前記第１部材と第２部材と第３部材とを順次配列し該前
記第１部材と第３部材との間で駆動力を伝達することを
特徴とする駆動伝達装置。A first member rotated about one axis;
A first pin parallel to the one axis and a second pin at a position apart from the one axis in diametrically opposite directions.
And a first pin and a second pin, each of which is a first pin.
The roller and the second roller are rotatably supported, and the second member includes a third pin and a fourth pin that are parallel to the one axis at positions separated from each other in the radial direction from the one axis, The third pin and the fourth pin rotatably support a third roller and a fourth roller, respectively, and further include the first roller and the second roller which are notched long in the radial direction.
A first long groove for guiding rotation of the roller and a second long groove for guiding rotation of the roller, wherein the third member includes a third long groove and a fourth groove for guiding rotation of the first roller and the second roller, respectively, which are long and notched in a radial direction. A long groove, the first roller and the second roller are provided with a flange on a free end side of the first pin and the second pin to prevent the second member from coming out, and the third roller and the fourth roller are The third pin and the fourth pin each have a flange on a free end side thereof for stopping the third member from coming off. The first member, the second member, and the third member are sequentially arranged, and the first member is provided. A drive transmission device for transmitting a drive force between a first member and a third member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2116020A JP3049076B2 (en) | 1990-05-02 | 1990-05-02 | Drive transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2116020A JP3049076B2 (en) | 1990-05-02 | 1990-05-02 | Drive transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0415314A JPH0415314A (en) | 1992-01-20 |
| JP3049076B2 true JP3049076B2 (en) | 2000-06-05 |
Family
ID=14676803
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2116020A Expired - Fee Related JP3049076B2 (en) | 1990-05-02 | 1990-05-02 | Drive transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3049076B2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06332285A (en) * | 1993-05-25 | 1994-12-02 | Ricoh Co Ltd | Rotary developing device |
| JP5939715B2 (en) * | 2013-09-11 | 2016-06-22 | 京セラドキュメントソリューションズ株式会社 | Fixing apparatus and image forming apparatus |
| DE102014211272B4 (en) * | 2014-06-12 | 2022-11-24 | Schaeffler Technologies AG & Co. KG | shaft coupling |
| DE102015212435A1 (en) * | 2015-07-02 | 2017-01-05 | Schaeffler Technologies AG & Co. KG | Oldham |
| JP2018096387A (en) * | 2016-12-08 | 2018-06-21 | アイシン精機株式会社 | Gear transmission mechanism |
-
1990
- 1990-05-02 JP JP2116020A patent/JP3049076B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0415314A (en) | 1992-01-20 |
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