JPS59187152A - Reduction gear - Google Patents
Reduction gearInfo
- Publication number
- JPS59187152A JPS59187152A JP6125683A JP6125683A JPS59187152A JP S59187152 A JPS59187152 A JP S59187152A JP 6125683 A JP6125683 A JP 6125683A JP 6125683 A JP6125683 A JP 6125683A JP S59187152 A JPS59187152 A JP S59187152A
- Authority
- JP
- Japan
- Prior art keywords
- belt
- input shaft
- large diametral
- diametral hole
- output shaft
- 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.)
- Pending
Links
Abstract
Description
【発明の詳細な説明】
この発明は、車両においてエンジンと駆動輪との間に介
設される減速装置として好適な同軸形減速装置に関する
。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a coaxial reduction gear that is suitable as a reduction gear that is interposed between an engine and drive wheels in a vehicle.
入力軸と出力軸とが同軸上番こ配置された減速装置とし
ては、入力軸の軸心上で本体ｌ１１１ケースに設けられ
た内歯歯車へ楕円形のカム部材により、内歯歯車よりや
や小径の外歯リングを押し付け、外歯リングと出力軸と
を連結して出力軸に減速回転を取り出すようにした装置
が知られでいる。As a speed reducer in which the input shaft and the output shaft are coaxially arranged, an oval cam member connects the internal gear provided in the main body l111 case on the axis of the input shaft. There is a known device in which an externally toothed ring is pressed, the externally toothed ring is connected to an output shaft, and decelerated rotation is taken out to the output shaft.
このような従来の減速装置は外歯リングと出力軸との連
結が容易でなく外歯リング等を特殊なものとする必要が
あり（例えば実公昭５０−３５２７３号公＠）、製造コ
ストの低減を妨げる一因となっていた。In such conventional reduction gears, it is not easy to connect the external toothed ring and the output shaft, and the external toothed ring etc. must be made special (for example, Utility Model Publication No. 50-35273@), which reduces manufacturing costs. This was a contributing factor to the hindrance.
この発明は、上記従来の問題点に鑑みなされたもので、
市販の材料が利用できるようにして、減速装置の製作を
容易にすることを目的とする。This invention was made in view of the above-mentioned conventional problems.
The purpose is to facilitate the production of reduction gears by making commercially available materials available.
上記目的を達成するこの発明による減速装置は。A speed reduction device according to the present invention achieves the above object.
入力軸から出力軸へ減速して動力を伝達する手段として
、製作の容易な無端伝動帯を用いることを特徴とする。It is characterized by using an easy-to-manufacture endless transmission band as a means for decelerating and transmitting power from the input shaft to the output shaft.
以下、この発明の実施例を図に従い説明する。Embodiments of the present invention will be described below with reference to the drawings.
第１図から第５図はこの発明の第１実施例を示し、（１
）は減速装置で、自動二輪車に適用さねた場合を示して
いる。図において、（２）はエンジン、（３）は伝動ケ
ースで減速ｇｉｕ＋を覆い、このケース（３）の後部に
は後車軸か設けられてこわに駆動軸たる後輪（４）か設
けら、ｌ−ｊ ７−。エノシン（２）のクランク軸（５
：に減速装Ｍ（］）の入力軸（６）が一体成形される。1 to 5 show a first embodiment of the present invention, (1
) indicates a reduction gear and is not applicable to motorcycles. In the figure, (2) is the engine, (3) is a transmission case that covers the deceleration GIU+, and the rear axle is installed at the rear of this case (3), and the rear wheel (4) that is the drive shaft is installed. l-j 7-. Enosine (2) crankshaft (5
: The input shaft (6) of the reduction gear M(]) is integrally molded.
この入力軸（６）と同軸上に、別体に形成された出力軸
（７）か設けられ、この出力軸（７）はベルト伝動機ｉ
Ｊ ＋８） ｉこより後輪（４）を駆動する。A separately formed output shaft (7) is provided coaxially with this input shaft (6), and this output shaft (7) is connected to the belt transmission i.
J +8) Drive the rear wheel (4) from i.
」７記入力軸（６）には、支持部材（９１を介して入力
軸（６］と平行な軸心上に一対の転動輪たるローラ（］
０ａ）（］Ｏａ）が軸支される（第３図）。Ｔなわち、
上記支持部材（９）は１人力軸（６）に同着された支持
杆ｆｌ１１と、支持杆（１１１の各端に枢支された一対
の支持体（＋２１０２）と・両支持体Ｑ２１！＋２＋に
、引張方向に働くように架設されるスプリングｆｌｆｆ
ｉとで構成される。一方、この支持体（１２＋ｆ＋２１
にはそれぞれ１個づつローラ（ｌｎａ）が軸支さ第１る
。減速装置本体たる伝動ケース（３）には入力軸（６）
と同軸上にＫｆ ｉｌｉ円形の大径孔０４）か形成され
る。”7 The input shaft (6) is connected to a pair of rollers (rolling wheels) on an axis parallel to the input shaft (6) via a support member (91).
0a) (]Oa) is pivoted (Fig. 3). T that is,
The support member (9) includes a support rod fl11 attached to the manual shaft (6), a pair of supports (+2102) pivotally supported at each end of the support rod (111), and both supports Q21!+2+ The spring flff is installed so as to act in the tensile direction.
It consists of i. On the other hand, this support (12+f+21
One roller (lna) is pivotally supported in each of the first and second rollers. The transmission case (3), which is the main body of the reduction gear, has an input shaft (6).
A large circular hole 04) is formed coaxially with the hole 04).
無端伝動帯たるゴム質の歯付ベルト（１５ａ）は。The rubber toothed belt (15a) is an endless transmission band.
大径孔０４）の内周寸法より短い外周寸法を有し、この
ベルト（１５ａ）は両ローラｆｌＯａ）＋１０ａ）間に
巻回さね、かつ、大径孔α舶内周面とローラ（］Ｏａ）
との闇に挿入される。そして入力軸（６１の回転が所定
速度以上の冒速に至ると両ローラ（’Ｉ’０ａ）（１（
’ｌａ’）を支持する支持体ｆ＋２１ Ｆ＋２１がスプ
リングｔｌ ＋Ｊ ｆ＋ ３１の弾性力に抗して拡開し
、歯付ベルト（１５ａ）はローラ（１０ａ）と大径孔（
１４）の内周面と番こ挾持されて大径孔（１４）の内周
面ＣＣ係合しこの面上を転動する。This belt (15a) has an outer circumferential dimension shorter than the inner circumferential dimension of the large diameter hole 04), and this belt (15a) is wound between both rollers flOa)+10a), and the inner circumferential surface of the large diameter hole α and the roller (] Oa)
It is inserted into the darkness. When the rotation of the input shaft (61) reaches a predetermined speed or higher, both rollers ('I'0a) (1 (
The support f+21 F+21 that supports the roller (10a) and the large diameter hole ('la') expands against the elastic force of the spring tl +J f+
It is clamped by the inner circumferential surface of the large diameter hole (14) and engages with the inner circumferential surface CC of the large diameter hole (14), and rolls on this surface.
なお、上記入力軸（６１に、円弧面（１ｍを有する案内
部材（１７！が設けられ、この円弧面（＋６１が、隣合
うローラｆｌＯａ）（１０ａ’）間のベルト（１５ａ）
に摺接してこのベルト（１５ａ）を案内する。Note that the input shaft (61 is provided with a guide member (17!) having a circular arc surface (1 m), and this circular arc surface (+61 is a belt (15a) between adjacent rollers flOa) (10a').
The belt (15a) is guided by sliding contact with the belt (15a).
前記出力軸（７）（こは、円弧面（１６）とほぼ同径の
出力輪たる出カブ−ＩＪ（１８ａ’）が設けらね、この
出カブ’Ｊ （１８ａ）がベルト（１５２）と噛み合っ
て回転せしめられ、この出カブ−’Ｊ（１８ａ）とベル
ト伝動機構＋８１の出力ベルト（＋９）とが噛み合って
いる。The output shaft (7) is not provided with an output wheel IJ (18a') having approximately the same diameter as the arcuate surface (16), and this output shaft 'J (18a) is connected to the belt (152). They are meshed and rotated, and this output belt -'J (18a) and the output belt (+9) of the belt transmission mechanism +81 are meshed with each other.
そのため、駆動さ第１だ人力軸（６）がベルト（１５ａ
）の外周寸法と大径孔０４）の内周寸法との差をベルト
に減速回転させ、これに運動して後部（４）が回動し。Therefore, the first driven human power shaft (6) is connected to the belt (15a).
) and the inner circumference of the large diameter hole 04) causes the belt to rotate at a reduced speed, and the rear part (4) rotates due to this movement.
車両か走行する・
上記構成によねば、歯付ベルト（１５ａ）が案内部材０
７）と出カブ−’Ｊ（１８ａ）とに跨って巻回されるた
め、伝動力によってベルト（１５ａ）が捩れることはな
く、安定した連動状態が得らね、正確な動力伝達が得ら
オ′する。才だ、ベルト（１５ａ）の耐久性の面からも
有益である・
以下の図面は、他の実施例を示し、ｆｉＱ記第１実施伊
１と面構ｌｊｖの部分１ごついては図面に符号を付して
その説明を省略する。When the vehicle is running, according to the above configuration, the toothed belt (15a) is attached to the guide member 0.
7) and the output turnip (18a), the belt (15a) will not be twisted by the transmission force, making it impossible to obtain a stable interlocking condition and accurate power transmission. Rao'. The drawings below show other embodiments, and the drawings are marked with reference numbers for parts 1 and 1 of the surface structure ljv. The explanation will be omitted.
第６図と第７図は第２実施例を示しケース（３）に断面
円形の支持孔Ｑｉ１１か形成さね、支持孔α１１の内周
面に係止孔１２１）か形成される。弾性の係合環＠が支
持孔■Ｊ）内に遊嵌さね、保合環のに突設さ才］だ突起
力）が保止孔（２１１に嵌合する。この保合環＠の内孔
が大径孔０４）とされる。一方、歯車（１０ｂ）（］Ｏ
ｂ）にベルト（１５ｂ）が巻かれ、歯車ｆ１０１ｉ）（
ｌｒｌｂ）に噛み合った部分のベルト（１５ｂ）が保合
環■を径方向外方に弾性変形させ、ベルト（１５ｂ）外
周面と大径孔０４）内周面とが、保合環ガの弾性力で接
している。捷だ、出力プーリ（１８ｈ）は、ベルト（１
５ｂ）と噛み合っている。6 and 7 show a second embodiment, in which a support hole Qi11 having a circular cross section is formed in the case (3), and a locking hole 121) is formed in the inner peripheral surface of the support hole α11. The elastic engagement ring (211) fits loosely into the support hole (J), and the retaining ring's protruding force (211) fits into the retaining hole (211). The inner hole is a large diameter hole 04). On the other hand, gear (10b) (]O
The belt (15b) is wound around b), and the gear f101i) (
The part of the belt (15b) meshed with lrlb) elastically deforms the retaining ring (2) outward in the radial direction, and the outer peripheral surface of the belt (15b) and the inner peripheral surface of the large diameter hole (04) deform the retaining ring (2) elastically. It is approached with force. The output pulley (18h) is the belt (1
5b).
上記構成によれば、大径孔（Ｉ４）とベルｈ （１５ｂ
）七が常時弾性力で接するため１両者の相対摺動が防止
さねて正確な減速比が得られる。According to the above configuration, the large diameter hole (I4) and the bell h (15b
) Since 7 is always in contact with elastic force, relative sliding between 1 and 1 is prevented and an accurate reduction ratio can be obtained.
第８図から第１０図は第３実施例を示し、大径孔０４）
は内鎖車を有する構造とさ第１、支持部材（９）の両端
に軸支された鎖車（Ｈｌｃ）（１０ｃ）にチェーン（１
５Ｃ）が巻装される。チェーンｆ１５ｃ）は二連式とさ
れ、その一方が鎖車Ｎ０Ｃ）と大径孔α４）の内鎖車に
挾捷ねた状態で噛み合う。才だ、出力鎖車（１８Ｃ）は
上記チェーン（１５Ｃ）の他方と噛み合う。Figures 8 to 10 show the third embodiment, with large diameter hole 04)
First, the chain (1) is attached to the chain wheel (Hlc) (10c) pivotally supported at both ends of the support member (9).
5C) is wrapped. The chain f15c) is a two-chain type, one of which meshes with the chain wheel N0C) and the inner chain wheel of the large diameter hole α4) in a pinched state. The output chain wheel (18C) meshes with the other chain (15C).
上記構成によれば、大径孔（１４）と鎖車（ＩＯＣ）か
チェーン（１５Ｃ）を挾んだ状態で、このチェーン（１
５Ｃ■噛み合うため、この動力伝達が正確に維持される
。According to the above configuration, the chain (15C) is sandwiched between the large diameter hole (14) and the chain wheel (IOC).
Because of the 5C■ meshing, this power transmission is maintained accurately.
尚１以上各夾施例はＩＱ＋示の例によるが、転動輪は単
一であってもよく、三つ以上であってもよい。In addition, each of the embodiments with one or more inclusions is based on the example shown in IQ+, but the number of rolling wheels may be single, or three or more.
寸だ、各実施例の各部構成を神々組合せてこの発明を達
１戊してもよい。Indeed, it is possible to achieve this invention by combining various parts of each embodiment.
この発明によイ１ば、込力軸に運動して無端伝動帯が大
径孔内周面上を転動し、この無端伝動帯の転動ｌこよる
回転が出力軸に伝達さイ９る構成であるため、一般に巻
き掛は伝動用として用いられる歯付ベルト、チェノ等の
無端伝動帯の利用ｌごより減速機能が発揮さ、ｌ″ｌる
。よって、従来のような特殊な外歯リングが不要となり
、市販の伝動部品を流用できるので、減速装置の製作の
容易化が達成される。According to this invention, the endless transmission band moves on the input shaft and rolls on the inner peripheral surface of the large diameter hole, and the rotation due to the rolling of the endless transmission band is transmitted to the output shaft. Because of the structure, the deceleration function is generally achieved by using an endless transmission band such as a toothed belt or a chain belt used for transmission. Since tooth rings are no longer required and commercially available transmission parts can be used, the reduction gear can be manufactured easily.
以下各図はこの発明の実施例を示し、第１図から第５図
は第１実施例で第１図１は全体横断部図。
第２図は第１図の部分拡大図、第３図は第２図のＩＩＩ
−Ｉｌｌ線矢視図、第４図は第２図のＩＶ−ＩＶ線矢
視図、第５図は第２図のＶ−Ｖ線矢視断面図、第６図と
第７図は第２実施例で第６図はその正面断面図、第７図
は第６図の■−■線矢視断面図、第８図から第１０図は
第３実施例で第８図はその正面図、第９図は第８図のＩ
Ｘ−ＩＸ線矢視断面図、第１０図は第９図のＸ−Ｘ線矢
視部分図である。
（１）・・−減速装置、（３）・・・伝動ケース、（６
１・・−人力軸。
（７）・・・出力軸％（９）・・・支持部材、 （１
０ａ）・・・ ローラ、（］Ｏｂ）・・・歯車、 Ｃｌ
０Ｃ）−・−鎖車、 Ｑ４１・・−大径孔、（１５ａ）
（１５ｂ）・・−べ／Ｌ／ト、（１５Ｃ）・・・チェー
ン、０７）−・・案内部材、（１８ａ）＋ １８ｂ）’
−出力プーリ、 （１８Ｃ）−出力鎖車・Each figure below shows an embodiment of the present invention, and FIGS. 1 to 5 are the first embodiment, and FIG. 1 is a cross-sectional view of the whole. Figure 2 is a partially enlarged view of Figure 1, Figure 3 is Figure III of Figure 2.
- Ill line arrow view, Figure 4 is a IV-IV line arrow view in Figure 2, Figure 5 is a V-V line cross-sectional view in Figure 2, Figures 6 and 7 are 2 6 is a front sectional view of the embodiment, FIG. 7 is a sectional view taken along the line ■-■ in FIG. 6, and FIGS. 8 to 10 are the third embodiment, and FIG. 8 is a front view thereof. Figure 9 is I of Figure 8.
A sectional view taken along the line X-IX, and FIG. 10 is a partial view taken along the line X-X of FIG. (1)... - reduction gear, (3)... transmission case, (6
1...-Human power axis. (7)...Output shaft% (9)...Supporting member, (1
0a)...Roller, (]Ob)...Gear, Cl
0C) ---Chain wheel, Q41...-Large diameter hole, (15a)
(15b)...-B/L/T, (15C)...Chain, 07)--Guiding member, (18a)+18b)'
-Output pulley, (18C) -Output chain wheel/
Claims (1)
置であって、上記入力軸に、支持部材を介してこの入力
軸と平行な軸心上に軸支された転動輪と；入力軸と同一
軸心上で本体側に形成された断面略円形の大径孔と；上
記転動輪間に巻回されこの転動輪によって大径孔の内周
面と係合する無端伝動帯と：出力軸に支持されると共に
上記無端伝動帯の内周に係合する出力輪とを備えたこと
を特徴とする減速装置。1. A speed reduction device in which an input shaft and an output shaft are provided on the same axis, and a rolling wheel is supported on the input shaft via a support member on an axis parallel to the input shaft. ; a large-diameter hole with a substantially circular cross section formed on the main body side on the same axis as the input shaft; and an endless transmission band wound between the rolling wheels and engaged with the inner peripheral surface of the large-diameter hole by the rolling wheels. and: an output wheel supported by an output shaft and engaged with an inner periphery of the endless transmission band.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6125683A JPS59187152A (en) | 1983-04-06 | 1983-04-06 | Reduction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6125683A JPS59187152A (en) | 1983-04-06 | 1983-04-06 | Reduction gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59187152A true JPS59187152A (en) | 1984-10-24 |
Family
ID=13165969
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6125683A Pending JPS59187152A (en) | 1983-04-06 | 1983-04-06 | Reduction gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59187152A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6330658U (en) * | 1986-08-12 | 1988-02-29 | ||
| JP2019199966A (en) * | 2009-03-30 | 2019-11-21 | テークー−ジステームス ゲーエムベーハー | Gear, motor-gear unit, internal combustion engine-gear unit, vehicle, and power generator with gear |
| US11280394B2 (en) | 2009-03-30 | 2022-03-22 | Tq-Systems Gmbh | Gear, motor-gear unit, vehicle, generator with a gear, and force transmitting element |
| US11286979B2 (en) | 2016-11-28 | 2022-03-29 | Tq-Systems Gmbh | Power transmission elements, torque measuring device and freewheel assembly |
| US11808338B2 (en) | 2013-03-20 | 2023-11-07 | Tq-Systems Gmbh | Harmonic pin ring gearing |
-
1983
- 1983-04-06 JP JP6125683A patent/JPS59187152A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6330658U (en) * | 1986-08-12 | 1988-02-29 | ||
| JP2019199966A (en) * | 2009-03-30 | 2019-11-21 | テークー−ジステームス ゲーエムベーハー | Gear, motor-gear unit, internal combustion engine-gear unit, vehicle, and power generator with gear |
| JP2021081071A (en) * | 2009-03-30 | 2021-05-27 | テークー−ジステームス ゲーエムベーハー | Gear, motor-gear unit, internal combustion engine-gear unit, vehicle, and power generator with gear |
| US11280394B2 (en) | 2009-03-30 | 2022-03-22 | Tq-Systems Gmbh | Gear, motor-gear unit, vehicle, generator with a gear, and force transmitting element |
| US11808338B2 (en) | 2013-03-20 | 2023-11-07 | Tq-Systems Gmbh | Harmonic pin ring gearing |
| US11286979B2 (en) | 2016-11-28 | 2022-03-29 | Tq-Systems Gmbh | Power transmission elements, torque measuring device and freewheel assembly |
| US11781590B2 (en) | 2016-11-28 | 2023-10-10 | Tq-Systems Gmbh | Load cell for determining a radial force acting on a crankshaft |
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| JPH03272351A (en) | Continuously variable automatic transmission |