JPH0541854B2 - - Google Patents
Info
- Publication number
- JPH0541854B2 JPH0541854B2 JP11286083A JP11286083A JPH0541854B2 JP H0541854 B2 JPH0541854 B2 JP H0541854B2 JP 11286083 A JP11286083 A JP 11286083A JP 11286083 A JP11286083 A JP 11286083A JP H0541854 B2 JPH0541854 B2 JP H0541854B2
- Authority
- JP
- Japan
- Prior art keywords
- disc
- disk
- gear
- rolling elements
- reduction ratio
- 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 - Lifetime
Links
- 238000005096 rolling process Methods 0.000 claims description 16
- 230000000737 periodic effect Effects 0.000 claims 5
- 239000003638 chemical reducing agent Substances 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 5
- LKJPSUCKSLORMF-UHFFFAOYSA-N Monolinuron Chemical compound CON(C)C(=O)NC1=CC=C(Cl)C=C1 LKJPSUCKSLORMF-UHFFFAOYSA-N 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
- F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
-
- 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
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
- F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
- F16H2025/063—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members the intermediate members being balls engaging on opposite cam discs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は、減速機に係り、特に、全体の小型化
を図つた状態で大きな減速比が得られるようにし
た減速機に関する。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a reduction gear, and more particularly to a reduction gear that can obtain a large reduction ratio while reducing the overall size.
〔従来技術とその問題点〕
たとえば、モータを動力源とする装置の中に
は、モータの回転を減速機を介して負荷に伝達す
るようにしたものが多い。[Prior art and its problems] For example, many devices that use a motor as a power source transmit the rotation of the motor to a load via a reduction gear.
ところで、このような用途の減速機としては従
来種々提案されているが、最も一般的には小歯車
と大歯車とを組合せたものが多用されている。す
なわち、入力回転軸で小歯車を回転させ、この小
歯車に噛合した大歯車の回転を出力回転軸に伝え
るようにした歯車式の減速機である。 Incidentally, although various reduction gears have been proposed for such uses, the most commonly used one is a combination of small gears and large gears. That is, it is a gear-type speed reducer in which a small gear is rotated by an input rotating shaft, and the rotation of a large gear meshed with the small gear is transmitted to an output rotating shaft.
しかしながら、歯車式の減速機には次のような
問題点があつた。すなわち、今、小歯車の歯数を
Z1、大歯車の歯数をZ2、小歯車のピツチ円直径を
D1、大歯車のピツチ円直径をD2とすると、この
減速機の減速比Ｘは、
Ｘ＝Z2／Z1＝D2／D1
となる。したがつて、減速比Ｘを大きくするに
は、小歯車のピツチ円直径D1を小さくするか、
大歯車のピツチ円直径D2を大きくする必要があ
る。しかし、歯車の歯数の最小値には限度がある
ので、減速比Ｘを大きく設定するには、必然的に
大歯車のピツチ円直径を大きくせざるを得ず、こ
の結果、減速機全体が大型化するのを免れ得な
い。また、歯車式減速機の場合には、小歯車と大
歯車との歯のうち、互いに接している１〜２枚の
歯を介して動力を伝達する形態となる。このた
め、必要な動力を伝達するには、その力の伝達に
耐え得る大きさに個々の歯を設定する必要があ
る。したがつて、この点からも減速比Ｘを大きく
設定しようとすると全体の大型化を免れ得ない問
題があつた。 However, gear type reducers have the following problems. In other words, now the number of teeth on the pinion is
Z 1 is the number of teeth of the large gear Z 2 is the pitch circle diameter of the small gear
D 1 and the pitch circle diameter of the large gear are D 2 , the reduction ratio X of this reducer is X=Z 2 /Z 1 =D 2 /D 1 . Therefore, in order to increase the reduction ratio X, either reduce the pitch circle diameter D1 of the pinion, or
It is necessary to increase the pitch circle diameter D2 of the large gear. However, since there is a limit to the minimum number of gear teeth, in order to set a large reduction ratio It is inevitable that it will become larger. In the case of a gear type speed reducer, power is transmitted through one or two of the teeth of a small gear and a large gear that are in contact with each other. Therefore, in order to transmit the necessary power, it is necessary to set each tooth to a size that can withstand the transmission of that force. Therefore, from this point of view as well, if an attempt was made to set the reduction ratio X to a large value, there was a problem in that the overall size would inevitably increase.
本発明は、このような事情に鑑みてなされたも
ので、その目的とするところは、小型で、かつ効
率の良い動力伝達特性が得られ、しかも大きな減
速比が得られる減速機を提供することにある。
The present invention has been made in view of the above circumstances, and its purpose is to provide a reduction gear that is compact, provides efficient power transmission characteristics, and provides a large reduction ratio. It is in.
平面の基準円を交錯する正弦波状に曲りくねつ
た溝が第１、第３の円板の片面に、また第２の円
板には両面に備えられている。
A sinusoidal groove that intersects a plane reference circle is provided on one side of the first and third disks, and on both sides of the second disk.
前記第１の円板と第２の円板、そして第２の円
板と第３の円板をそれぞれ平面同士で対向し、第
１の円板と第２の円板の円板間、そして第２の円
板と第３の円板間には転動体を介してあり、この
転動体を保持するための第１、第２の保持器があ
る。第１の保持器と第３の円板は固定されてい
る。 The first disc and the second disc, and the second disc and the third disc, respectively, face each other on their planes, and between the first disc and the second disc, and A rolling element is interposed between the second disc and the third disc, and there are first and second cages for holding the rolling element. The first retainer and the third disc are fixed.
ここで第１の円板を入力軸として回転させる
と、第２の円板と第２の保持器は第１の円板とは
反対方向に回転する。そして第２の保持器は出力
として取り出される。 Here, when the first disc is rotated using the input shaft, the second disc and the second retainer are rotated in the opposite direction to that of the first disc. The second holder is then taken out as an output.
従来の減速機のように１〜２枚の歯にのみ伝達
動力（負荷）が作用してしまうことがなく、ほぼ
全ての転動体が動力伝達を行なうため、小型の減
速機が可能である。また減速比は、円板に設けら
れた正弦波状の溝の波数によつて決定するため大
きな減速比が得られる。したがつて、本発明は小
型・大減速・高伝達動力が得られる。
Unlike conventional speed reducers, the transmitted power (load) does not act on only one or two teeth, and almost all rolling elements transmit power, making it possible to create a small speed reducer. Furthermore, since the reduction ratio is determined by the wave number of the sinusoidal grooves provided in the disk, a large reduction ratio can be obtained. Therefore, according to the present invention, it is possible to obtain a small size, large deceleration, and high power transmission.
第１図に本発明の実施例を示す。 FIG. 1 shows an embodiment of the present invention.
第１・第２・第３の円板１，２，３の平面４，
５，６，７にはそれぞれ正弦波状の溝８，９，１
０，１１があり、平面４と平面５は転動体１２を
介して対向している。転動体１２は第１の保持器
１３にて保持されている。また、平面６と平面７
も転動体１４を介して対向しており、転動体１４
は保持器１５に保持されている。 The planes 4 of the first, second and third disks 1, 2, 3,
5, 6, and 7 have sinusoidal grooves 8, 9, and 1, respectively.
0 and 11, and plane 4 and plane 5 face each other with rolling elements 12 in between. The rolling elements 12 are held by a first cage 13. Also, plane 6 and plane 7
are also opposed to each other via the rolling elements 14, and the rolling elements 14
is held in a holder 15.
第１の円板１は軸受１６により回転自在にハウ
ジング１７に支持されている。第２の円板２は軸
受１８により回転自在に第２の保持器１５に支持
されている。第３の円板３はハウジング１７に固
定されている。また第１の保持器１３はハウジン
グ１７に固定されており、第２の保持器１５は軸
受１９によつて回転自在に第３の円板３に支持さ
れている。 The first disc 1 is rotatably supported by a housing 17 by a bearing 16. The second disc 2 is rotatably supported by the second retainer 15 by a bearing 18. The third disc 3 is fixed to the housing 17. Further, the first cage 13 is fixed to the housing 17, and the second cage 15 is rotatably supported by the third disk 3 by a bearing 19.
第１〜第３の円板１，２，３の平面４，５，
６，７上に構成された正弦波状の（周期的に）曲
りくねつた溝の形状を第２図に示す。２１が円
板、２２が溝である。 Planes 4, 5 of the first to third disks 1, 2, 3,
FIG. 2 shows the shape of the sinusoidal (periodically) winding groove formed on the grooves 6 and 7. 21 is a disk, and 22 is a groove.
第１・第２の保持器１３，１５の形状を第３図
に示す。３１が保持器であり、長穴３２がある。
これら長穴３２によつて転動体１２，４１は一定
間隔に保持される。 The shapes of the first and second cages 13 and 15 are shown in FIG. 31 is a retainer, which has an elongated hole 32.
These elongated holes 32 hold the rolling elements 12 and 41 at a constant interval.
第１図にて、円板１が入力側であり、第２の保
持器１５が出力側である。また転動体は正弦波状
の溝８と９、そして１０と１１のそれぞれの交点
に存在する。 In FIG. 1, the disk 1 is on the input side, and the second holder 15 is on the output side. Further, rolling elements are present at the intersections of sinusoidal grooves 8 and 9 and 10 and 11, respectively.
次に本実施例の原理を第４図にて説明する。正
弦波状の溝８，９，１０，１１の中心線をSINカ
ーブ４１，４２，４３，４４とする。そしてSIN
カーブ４１と４２の交点をＡ、SINカーブ４３と
４４の交点をＢとすると交点Ａ，Ｂには転動体１
２，１４が存在する。 Next, the principle of this embodiment will be explained with reference to FIG. The center lines of the sinusoidal grooves 8, 9, 10, 11 are SIN curves 41, 42, 43, 44. and SIN
If the intersection of curves 41 and 42 is A, and the intersection of SIN curves 43 and 44 is B, rolling elements 1 are located at intersections A and B.
2,14 exist.
ここで交点Ａの転動体を固定し（図中上下方向
の移動は可）、SINカーブ４１を反時計方向にθ1
回転したときSINカーブ４２は時計方向へθ2回転
すると、次式が成立する。 Here, fix the rolling element at intersection A (it is possible to move it up and down in the figure), and move the SIN curve 41 counterclockwise by θ 1
When the SIN curve 42 rotates clockwise by θ 2 , the following equation holds true.
CφSZ1・θ1＝CφSZ2・θ2 (1)
ここでZ1，Z2はSINカーブ４１，４２の山数で
ある。 CφSZ 1 ·θ 1 =CφSZ 2 ·θ 2 (1) Here, Z 1 and Z 2 are the numbers of peaks of the SIN curves 41 and 42.
またSINカーブ４２の回転角とSINカーブ４３
の回転角は同値であり、SINカーブ４４は固定さ
れているため、SINカーブ４２がθ2回転した時、
交点Ｂの回転角θとし、SINカーブ４３，４４の
山数をそれぞれZ3，Z4とすると次式が成立する。 Also, the rotation angle of SIN curve 42 and SIN curve 43
The rotation angles of are the same and the SIN curve 44 is fixed, so when the SIN curve 42 rotates by θ 2 ,
When the rotation angle θ of the intersection point B is set and the number of peaks of the SIN curves 43 and 44 are Z 3 and Z 4 respectively, the following equation holds true.
CφSZ3（θ2−θ）＝CφSZ4・θ (2)
ここで減速比をＸとすると、減速比は次式にな
る。 CφSZ 3 (θ 2 −θ)=CφSZ 4・θ (2) Here, if the reduction ratio is set to X, the reduction ratio becomes the following formula.
Ｘ＝θ1／θ (3) 上記３つの式を整理すると Ｘ＝Z2／Z1・（Z4／Z3＋１） (4) となる。 X=θ 1 /θ (3) When the above three equations are rearranged, it becomes X=Z 2 /Z 1・(Z 4 /Z 3 +1) (4).
たとえばZ1＝１、Z2＝10、Z3＝１、Z4＝10とす
ると減速比は110になる。 For example, if Z 1 =1, Z 2 =10, Z 3 =1, and Z 4 =10, the reduction ratio will be 110.
このように構成された本発明の減速機では、転
動体が常に円板と接触しながら回転している。そ
のため、従来の減速機のように１〜２枚の歯にの
み伝達動力（負荷）が作用してしまうことがな
く、転動体に負荷が分散して安定した動力伝達が
行われる。そのため、小型・大減速比・伝達動力
の減速機が実現する。 In the speed reducer of the present invention configured as described above, the rolling elements rotate while always being in contact with the disk. Therefore, unlike conventional speed reducers, the transmitted power (load) does not act on only one or two teeth, and the load is distributed to the rolling elements, resulting in stable power transmission. As a result, a reduction gear with a small size, large reduction ratio, and transmission power can be realized.
なお、本発明によれば正弦波状の溝の周波数を
変化させることによつて減速比を自由に選定する
ことができる。 According to the present invention, the reduction ratio can be freely selected by changing the frequency of the sinusoidal groove.
第１図は本発明の縦断面図、第２図は本発明の
円板の平面に形成された正弦波状の溝を示す正面
図、第３図は本発明の保持器の正面図、第４図は
本発明の原理図である。
１，２，３……円板、４，５，６，７……平
面、８，９，１０，１１……正弦波状の溝、１
２，１４……転動体、１３，１５……保持器、１
６，１８，１９……保持器、１７……ハウジン
グ、２１……円板、２２……正弦波状の溝、３１
……保持器、３２……長穴、４１，４２，４３，
４４……SINカーブ。
FIG. 1 is a longitudinal sectional view of the present invention, FIG. 2 is a front view showing sinusoidal grooves formed in the plane of the disk of the present invention, FIG. 3 is a front view of the cage of the present invention, and FIG. The figure is a diagram of the principle of the present invention. 1, 2, 3... Disk, 4, 5, 6, 7... Plane, 8, 9, 10, 11... Sinusoidal groove, 1
2, 14...Rolling element, 13, 15...Cage, 1
6, 18, 19...Cage, 17...Housing, 21...Disc, 22...Sinusoidal groove, 31
...Retainer, 32...Elongated hole, 41, 42, 43,
44...SIN curve.
Claims (1)
方の面に周期溝が形成された第１の円板と、 両方の面に周期溝が形成され、その一方の面を
前記第１の円板の前記他方の面に対向して配置さ
れた第２の円板と、 一方の面に周期溝が形成され、この面を前記第
２の円板の他方の面に対向して配置された第３の
円板と、 前記第１の円板と前記第２の円板との対向する
周期溝内に配置される転動体を一定間隔に保持す
る第１の保持器と、 出力軸が設けられるとともに、前記第２の円板
と前記第３の円板との対向する周期溝内に配置さ
れる転動体を一定間隔に保持する第２の保持器
と、 前記第３の円板と前記第１の保持器とが固定さ
れるケーシングと、 を有することを特徴とする減速機。[Claims] 1. A first disk having an input shaft provided on one surface and a periodic groove formed on the other surface, and a first disk having periodic grooves formed on both surfaces, a second disc disposed opposite to the other surface of the first disc, a periodic groove being formed on one surface, and this surface facing the other surface of the second disc; a first retainer that holds rolling elements disposed in opposing periodic grooves of the first disc and the second disc at a constant interval; , a second cage that is provided with an output shaft and that holds rolling elements disposed in opposing periodic grooves of the second disk and the third disk at a constant interval; and the third cage. A reduction gear comprising: a casing to which the disc and the first retainer are fixed;
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11286083A JPS604663A (en) | 1983-06-24 | 1983-06-24 | Reduction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11286083A JPS604663A (en) | 1983-06-24 | 1983-06-24 | Reduction gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS604663A JPS604663A (en) | 1985-01-11 |
| JPH0541854B2 true JPH0541854B2 (en) | 1993-06-24 |
Family
ID=14597340
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11286083A Granted JPS604663A (en) | 1983-06-24 | 1983-06-24 | Reduction gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS604663A (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5321988A (en) * | 1991-03-14 | 1994-06-21 | Synkinetics, Inc. | Oscillatory motion speed converter having drive and driven cams with balls and retainer |
| US5514045A (en) * | 1991-03-14 | 1996-05-07 | Synkinetics, Inc. | Speed converter with zero backlash |
| US5312306A (en) * | 1991-03-14 | 1994-05-17 | Synkinetics, Inc. | Speed converter |
| US5873800A (en) * | 1993-06-11 | 1999-02-23 | Synkinetics, Inc. | Variable output speed drive |
| US6270442B1 (en) | 1997-03-08 | 2001-08-07 | Synkinetics, Inc. | Multi-function speed converter |
| US6186922B1 (en) | 1997-03-27 | 2001-02-13 | Synkinetics, Inc. | In-line transmission with counter-rotating outputs |
| WO2020067160A1 (en) * | 2018-09-28 | 2020-04-02 | Ntn株式会社 | Reduction gear |
| JP2020051570A (en) * | 2018-09-28 | 2020-04-02 | Ntn株式会社 | Reduction gear |
| JP7021043B2 (en) * | 2018-09-28 | 2022-02-16 | Ntn株式会社 | Power transmission device |
-
1983
- 1983-06-24 JP JP11286083A patent/JPS604663A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS604663A (en) | 1985-01-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS59133863A (en) | Reduction gear | |
| US4966573A (en) | Differential speed reduction apparatus and double-toothed gear for use therein | |
| JPS60168954A (en) | Reduction gear | |
| JPS622064A (en) | Differential reduction gear mechanism of rolling ball type | |
| JPH0541854B2 (en) | ||
| JPS6347942B2 (en) | ||
| JPS58152958A (en) | Power transmission device | |
| JPH01312250A (en) | Differential gear mechanism using planetary gear speed reducer of internal engagement type | |
| US4096763A (en) | Hypocycloidal reduction gearing | |
| JPH0534538B2 (en) | ||
| JPS60129462A (en) | Speed reducer | |
| US3524362A (en) | Large ratio planetary friction drive | |
| JPH01158249A (en) | Reduction gear provided with oldham's coupling | |
| JPS59164449A (en) | Drive for worm gear | |
| JPH05302649A (en) | Worm speed reducer | |
| JPS6233462B2 (en) | ||
| JPH0231258B2 (en) | ||
| JPH10299841A (en) | Inscribed meshing epicyclic gear structure | |
| JPS62101943A (en) | Reducer | |
| KR0123419B1 (en) | Speed reducer | |
| JPH0740776B2 (en) | Reducer motor | |
| JPS6040863A (en) | Speed reducer | |
| JPS6091056A (en) | Reduction gear | |
| JP2646270B2 (en) | Planetary gear set | |
| JP3715427B2 (en) | Inner meshing planetary gear structure |