JPH028123Y2 - - Google Patents
Info
- Publication number
- JPH028123Y2 JPH028123Y2 JP1984013222U JP1322284U JPH028123Y2 JP H028123 Y2 JPH028123 Y2 JP H028123Y2 JP 1984013222 U JP1984013222 U JP 1984013222U JP 1322284 U JP1322284 U JP 1322284U JP H028123 Y2 JPH028123 Y2 JP H028123Y2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- disc spring
- boss
- rim
- gear rim
- 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
- 238000006073 displacement reaction Methods 0.000 claims description 5
- 230000002093 peripheral effect Effects 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Landscapes
- Gear Transmission (AREA)
- Gears, Cams (AREA)
Description
【考案の詳細な説明】
本考案は歯車に関するものであり、特に、歯車
ボスと歯車リムとの間の構造に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear, and particularly to a structure between a gear boss and a gear rim.
歯車装置において、装置を小型、軽量化するた
めに、原動機より与えられる入力を2〜3個の歯
車に分岐して被動機に伝えることが良く行なわれ
ている。このような歯車装置を、一般に、ロツク
ドトレーン歯車装置と通称している。従来型のこ
のロツクドトレーン歯車装置の一例を第1図に示
す。 In gear devices, in order to reduce the size and weight of the device, it is common practice to branch the input from the prime mover to two or three gears and transmit the input to the driven device. Such a gear device is generally called a locked train gear device. An example of this conventional locked train gear system is shown in FIG.
第1図において、原動機1より第1ピニオン2
に伝達された入力は、2個の第1ギア3a,3b
に分岐して伝えられる。第1ギア3a,3bには
夫々トーシヨン軸4a,4bを介して第2ピニオ
ン5a,5bが接続され、第2ギア6をへて出力
軸7より被動機8に伝達される。9a,9b,1
0a,10b,11a,11b,12a,12b
はそれぞれ軸受である。 In FIG. 1, the first pinion 2 is connected to the prime mover 1.
The input transmitted to the two first gears 3a, 3b
It is divided into two parts and communicated. Second pinions 5a, 5b are connected to the first gears 3a, 3b via torsion shafts 4a, 4b, respectively, and the signal is transmitted from the output shaft 7 to the driven machine 8 via the second gear 6. 9a, 9b, 1
0a, 10b, 11a, 11b, 12a, 12b
are each a bearing.
かかる構造の歯車装置にあつては、入力が数個
の歯車3a,3b,5a,5bに分岐して伝達さ
れるため、分岐された各歯車3a,3b,5a,
5bの製作誤差や組立誤差を吸収して、各分岐歯
車3a,3b,5a,5bに対し等分に荷重を分
担させるための荷重等配機能を具備することが必
要であつた。 In a gear device having such a structure, since the input is branched and transmitted to several gears 3a, 3b, 5a, 5b, each of the branched gears 3a, 3b, 5a,
It was necessary to provide a load equalization function for absorbing manufacturing errors and assembly errors of the gear 5b and equally distributing the load to each of the branch gears 3a, 3b, 5a, and 5b.
第1図に示されるものにおいては、中空状の第
2ギア5a,5bの軸穴を貫通して設けられてい
るトーシヨン軸4a,4bのねじり変位を利用し
て、分岐歯車3a,3b,5a,5bの荷重等配
を行なわせている。 In the one shown in FIG. 1, the branch gears 3a, 3b, 5a are made by utilizing the torsional displacement of the torsion shafts 4a, 4b provided through the shaft holes of the hollow second gears 5a, 5b. , 5b are equally distributed.
しかしながら、この方法によると、所定のねじ
り変位を得るためには、トーシヨン軸4a,4b
が長くなり、そのため第2ピニオン5a,5bを
中空にして、その中にトーシヨン軸4a,4bを
設けているのである。さらに、トーシヨン軸4
a,4bがあるために、第1ギア3a,3bと第
2ピニオン5a,5bを夫々別々の軸受9a,9
b,10a,10bで支承する必要が生じる。こ
のため、面間寸法Aを短縮できないと云う欠点が
あつた。又、第2ピニオン5a,5bの直径も小
さくできないため、最近の趨勢である浸炭歯車を
採用した歯車装置の小型、軽量化に際し、支障と
なつていた。 However, according to this method, in order to obtain a predetermined torsional displacement, it is necessary to
The second pinions 5a, 5b are made hollow, and the torsion shafts 4a, 4b are provided therein. Furthermore, the torsion shaft 4
a, 4b, the first gears 3a, 3b and the second pinions 5a, 5b are mounted on separate bearings 9a, 9, respectively.
It becomes necessary to support it with b, 10a, and 10b. For this reason, there was a drawback that the face-to-face dimension A could not be shortened. Further, the diameter of the second pinions 5a, 5b cannot be made small, which has been an obstacle to the recent trend of downsizing and weight reduction of gear devices employing carburized gears.
本考案は従来型ロツクドトレーン歯車装置のか
かる欠点をなくする目的で行なつたものである。 The present invention has been made to eliminate these drawbacks of conventional locked train gear systems.
第2図は本考案の一実施例を示す歯車であり、
従来型の一例を示す第1図において第1ギア3
a,3bに相当する歯車であり、本考案において
は、第2図に示す如く、従来のトーシヨン軸4
a,4bの機能を、歯車リム13と歯車ボス14
の間に組み込んだ皿ばねセツト15で行なわせる
ことにより、歯車装置を小型、軽量化せんとする
ものである。 FIG. 2 shows a gear showing an embodiment of the present invention.
In FIG. 1 showing an example of the conventional type, the first gear 3
These are gears corresponding to gears a and 3b, and in this invention, as shown in FIG. 2, the conventional torsion shaft 4
a, 4b, gear rim 13 and gear boss 14
The purpose is to reduce the size and weight of the gear device by using a disc spring set 15 installed between the two.
以下に本考案を詳細に説明する。 The present invention will be explained in detail below.
第2図、第3図、第4図は本考案の歯車23の
の一実施例を示すものである。歯車リム13は歯
車リム13の両側面部に固定されていてかつ内周
部に円筒部を有する支え環16a,16bによ
り、歯車ボス14の外周に設けたスリーブ17
a,17bに回動自在に支持されている。 FIGS. 2, 3, and 4 show an embodiment of the gear 23 of the present invention. The gear rim 13 is fixed to both side surfaces of the gear rim 13 and has a sleeve 17 provided on the outer periphery of the gear boss 14 by support rings 16a and 16b having a cylindrical portion on the inner periphery.
It is rotatably supported by a and 17b.
一方、歯車リム13の内側には複数個の皿ばね
セツト15がリーマボルト18で締付されてい
る。皿ばねセツト15のボツクス15a内には、
歯車の伝達すべきトルクに見合つた強さを有する
皿ばね19が円周方向に向けて組込まれ、球面状
の座をもつた皿ばね押え20,21、及びボツク
ス15a内から歯車ボス14方向に延びている特
殊キー22と共に皿ばねセツト15を構成してい
る。すなわち、第4図に示すように、皿ばねセツ
ト15のボツクス15a内では、中央の半径方向
に配した特殊キー22の先端部の両側に、それぞ
れ、皿ばね押え21,20と皿ばね19を円周方
向に配した。特殊キー22の他方の端は、それぞ
れ歯車ボス14の外周部に嵌合され、皿ばね19
を介して歯車リム13と歯車ボス14間のトルク
伝達が行なわれるように構成されている。 On the other hand, a plurality of disc spring sets 15 are tightened inside the gear rim 13 with reamer bolts 18. In the box 15a of the disc spring set 15,
A disc spring 19 having a strength commensurate with the torque to be transmitted by the gear is incorporated in the circumferential direction, and a disc spring holder 20, 21 having a spherical seat is installed in the direction of the gear boss 14 from inside the box 15a. Together with the extending special key 22, it constitutes a disc spring set 15. That is, as shown in FIG. 4, in the box 15a of the disc spring set 15, disc spring retainers 21 and 20 and disc springs 19 are mounted on both sides of the tip of the special key 22 arranged in the radial direction at the center. Arranged in the circumferential direction. The other end of the special key 22 is fitted to the outer periphery of the gear boss 14, and is connected to the disc spring 19.
The structure is such that torque is transmitted between the gear rim 13 and the gear boss 14 via the gear rim 13 and the gear boss 14.
したがつて、歯車リム13と歯車ボス14のい
ずれか一方から他の一方へトルク伝達を行う場
合、皿ばね19の撓み量に相当するねじり変位を
生じることになる。 Therefore, when transmitting torque from either the gear rim 13 or the gear boss 14 to the other, a torsional displacement corresponding to the amount of deflection of the disc spring 19 will occur.
このように、本考案においては、歯車23に皿
ばね19を採用することにより、小型で大容量の
トルクを伝達することが可能であり、皿ばねの厚
さや枚数を種々変更することにより、極めて簡単
に所要のトルクやねじり変位を得ることができ
る。なお、皿ばね押え20,21に球面座を設け
ることにより、トルク伝達も円滑に行なうことが
できる。 In this way, in the present invention, by adopting the disc spring 19 for the gear 23, it is possible to transmit a large amount of torque with a small size, and by variously changing the thickness and number of disc springs, it is possible to transmit a large amount of torque. The required torque and torsional displacement can be easily obtained. In addition, by providing spherical seats on the disc spring retainers 20 and 21, torque transmission can also be performed smoothly.
また、本考案においては、歯車リム13を歯車
リム13の両側面部に固定しかつ内周部に円筒部
を有する支え環16a,16bにより、歯車ボス
14の外周に設けたスリーブ17a,17bに回
動自在に支持しているので、摺動面を有する軸受
構造になり、歯車リム13の半径方向の位置も常
に容易に正確に保つことができる。したがつて、
歯車精度も充分に保つことができ、精密歯車とし
て使用することもできる。 In addition, in the present invention, the gear rim 13 is fixed to both side surfaces of the gear rim 13, and the sleeves 17a, 17b provided on the outer periphery of the gear boss 14 are rotated by support rings 16a, 16b having cylindrical parts on the inner periphery. Since it is movably supported, it has a bearing structure with a sliding surface, and the radial position of the gear rim 13 can be easily maintained accurately at all times. Therefore,
The gear accuracy can be maintained sufficiently, and it can also be used as a precision gear.
また、本考案の歯車23を、第1図に示す従来
の第1ギア3a,3bの代りに用いれば、第1図
の装置において、長いトーシヨン軸4a,4bと
中空状の第2ピニオン5a,5bは不要となり、
第2ピニオン5a,5bとして通常の中実状のピ
ニオンを用いることができ、トーシヨン軸4a,
4bの代りに通常の短い軸を用いることができ、
大きい第2ピニオン5a,5bの一部を軸支して
いた軸受10a,10bも小さい歯車軸を軸支す
るものに代えることもできる。そして、第1ギア
3a,3bと第2ピニオン5a,5bを一体の軸
で連結することにより、両者間の軸受9b,10
aもそれぞれ不要となる。そして、第5図に示す
ように、各歯車を配し、第1ピニオン2の軸心
と、第2ギア6と出力軸7の軸心をずらせ、軸受
12aが歯車23に当らなにようにしておけば、
軸受12aの厚みの分だけ歯車23と第2ギア6
を近ずけることができ、第1図に示した面間寸法
Aをその分だけ小さくすることができる。 Furthermore, if the gear 23 of the present invention is used in place of the conventional first gears 3a, 3b shown in FIG. 1, the long torsion shafts 4a, 4b, the hollow second pinion 5a, 5b is no longer needed,
A normal solid pinion can be used as the second pinion 5a, 5b, and the torsion shaft 4a,
4b can be replaced by a regular short shaft,
The bearings 10a, 10b that pivotally support a portion of the large second pinions 5a, 5b may also be replaced with bearings that pivotally support a small gear shaft. By connecting the first gears 3a, 3b and the second pinions 5a, 5b with an integral shaft, bearings 9b, 10 between them
a is also no longer necessary. Then, as shown in FIG. 5, each gear is arranged so that the axial center of the first pinion 2 is shifted from the axial center of the second gear 6 and the output shaft 7, so that the bearing 12a does not hit the gear 23. If you keep it,
The gear 23 and the second gear 6 are removed by the thickness of the bearing 12a.
can be made closer to each other, and the face-to-face dimension A shown in FIG. 1 can be made smaller by that amount.
このように本考案を用いれば、従来型の如くト
ーシヨン軸を使用することなく、分岐歯車の荷重
等配を行なわせることができるので、第1図にお
ける軸受9b,10aを省略することができ第2
ピニオン5a,5bも中空にする必要がないの
で、ロツクドトレーン歯車装置を極めてコンパク
トに構成することができる。 As described above, by using the present invention, it is possible to evenly distribute the load on the branch gear without using a torsion shaft as in the conventional type, so the bearings 9b and 10a in FIG. 1 can be omitted. 2
Since the pinions 5a and 5b also do not need to be hollow, the locked train gear device can be configured extremely compactly.
第1図は従来型のロツクドトレーン歯車装置を
示す平面図(一部断面図)、第2図は本考案の一
実施例を示す縦断面図、第3図は第2図の−
線断面図、第4図は皿ばねセツト部の中央部にお
ける横断面図、第5図は本考案の歯車を用いたロ
ツクドトレーン歯車装置の図で、第1図の−
線矢視に相当する側面図である。
13……歯車リム、14……歯車ボス、15…
…皿ばねセツト、16a,16b……支え環、1
7a,17b……スリーブ、18……リーマボル
ト、19……皿ばね、20,21……皿ばね押
え、22……特殊キー、23……歯車。
Fig. 1 is a plan view (partially sectional view) showing a conventional locked train gear device, Fig. 2 is a vertical sectional view showing an embodiment of the present invention, and Fig. 3 is a -
4 is a cross-sectional view at the center of the disc spring set portion, and FIG. 5 is a diagram of a locked train gear device using the gear of the present invention, which is shown at - in FIG. 1.
FIG. 3 is a side view corresponding to a line arrow view. 13...Gear rim, 14...Gear boss, 15...
...Disc spring set, 16a, 16b...Support ring, 1
7a, 17b...sleeve, 18...reamer bolt, 19...disc spring, 20, 21...disc spring holder, 22...special key, 23...gear.
Claims (1)
定の間隔をあけて歯車リムを設け、歯車ボスの外
周面部の中央部の数箇所に前記特殊キーを半径方
向に向けて設け、特殊キーの先端部の円周方向の
両側と歯車リムの内周部に設けた皿ばねセツトの
ボツクスとの間に球面座を有する皿ばね押えとそ
れぞれ数個の皿ばねを設け、歯車リムを歯車リム
の両側面部に固定しかつ内周部に円筒部を有する
支え環により歯車ボスの外周に設けたスリーブに
回動自在に支持し、皿ばねの定数の選定により歯
車ボスと歯車リムの間に所望のねじり変位を与え
得るように構成した歯車。 A gear rim is provided on the outer periphery of the gear boss at a predetermined interval corresponding to the height of the special key, and the special keys are provided at several locations in the center of the outer peripheral surface of the gear boss so as to face the special key in the radial direction. A disc spring holder having a spherical seat and several disc springs are provided between both sides of the tip in the circumferential direction and the box of the disc spring set provided on the inner circumference of the gear rim, and the gear rim is attached to the gear rim. A sleeve provided on the outer periphery of the gear boss is rotatably supported by support rings fixed to both side surfaces and having a cylindrical part on the inner periphery, and a desired distance between the gear boss and the gear rim is created by selecting the constant of the disc spring. A gear configured to provide torsional displacement.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1322284U JPS60126751U (en) | 1984-02-03 | 1984-02-03 | gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1322284U JPS60126751U (en) | 1984-02-03 | 1984-02-03 | gear |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS60126751U JPS60126751U (en) | 1985-08-26 |
JPH028123Y2 true JPH028123Y2 (en) | 1990-02-27 |
Family
ID=30497030
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1322284U Granted JPS60126751U (en) | 1984-02-03 | 1984-02-03 | gear |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60126751U (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4702505B2 (en) * | 2000-05-25 | 2011-06-15 | ミネベア株式会社 | Gear device |
JP2001336587A (en) * | 2000-05-25 | 2001-12-07 | Minebea Co Ltd | Electro-motive actuator |
FR2910948B1 (en) * | 2006-12-27 | 2009-02-13 | Hispano Suiza Sa | INTEGRATED OVERCOUPLE PROTECTION GEAR |
JP2014021741A (en) * | 2012-07-19 | 2014-02-03 | Hitachi Omron Terminal Solutions Corp | Paper money transaction device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS53141858A (en) * | 1977-05-16 | 1978-12-11 | Caterpillar Tractor Co | Flexible driving gear |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58175255U (en) * | 1982-05-19 | 1983-11-24 | 本田技研工業株式会社 | gear system |
-
1984
- 1984-02-03 JP JP1322284U patent/JPS60126751U/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS53141858A (en) * | 1977-05-16 | 1978-12-11 | Caterpillar Tractor Co | Flexible driving gear |
Also Published As
Publication number | Publication date |
---|---|
JPS60126751U (en) | 1985-08-26 |
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