JPS6084461A - Transmission gear of toothed belt - Google Patents
Transmission gear of toothed beltInfo
- Publication number
- JPS6084461A JPS6084461A JP19208083A JP19208083A JPS6084461A JP S6084461 A JPS6084461 A JP S6084461A JP 19208083 A JP19208083 A JP 19208083A JP 19208083 A JP19208083 A JP 19208083A JP S6084461 A JPS6084461 A JP S6084461A
- Authority
- JP
- Japan
- Prior art keywords
- belt
- tooth
- pulley
- pitch
- teeth
- 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.)
- Granted
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
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
- F16H7/023—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts with belts having a toothed contact surface or regularly spaced bosses or hollows for slipless or nearly slipless meshing with complementary profiled contact surface of a pulley
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pulleys (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、精密伝動や位置決め伝動に有用なバックラッ
シニレス歯付きベルト伝動装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a backlash-free toothed belt transmission device useful for precision transmission and positioning transmission.
歯付きベルト伝動装置においては９通常、第１図に示す
ように、歯付きベルト１００のピッチＰＢとζスＪ
歯つきプーリ１０１のＰＰとが等しい。そして、ベルト
１７１０２とプーリｎ１０３との間に適度な大きさのバ
ツクラツシユＢが存在する。そのために、ベルト歯やプ
ーリ溝がそれほど高寸法精度に製作されていなくてもベ
ルト伝動装置は滑らかな回転動力伝動をなしえる。しか
しながら、精密伝動や位置決め伝動に必要なベルト伝動
装［疲においては、プＩＪが正逆回転を行なうとき、バ
ックラッシュの大きさに比例して駆動ブーりと被動プー
リとの動きにタイムラグが生じる。このタイムラグが位
置決めの精度を著しく低下させる。これが高精度の数値
制御を行なうＮＧ工作機やマニシングセンターおよびＯ
Ａ機器などにおける決定的な欠点となっている。In a toothed belt transmission device, normally, as shown in FIG. 1, the pitch PB of the toothed belt 100 and the pitch PP of the toothed pulley 101 are equal. A bump B of an appropriate size exists between the belt 17102 and the pulley n103. Therefore, even if the belt teeth and pulley grooves are not manufactured with high dimensional accuracy, the belt transmission device can achieve smooth rotational power transmission. However, when the belt transmission system required for precision transmission and positioning transmission becomes fatigued, when the IJ rotates in forward and reverse directions, a time lag occurs between the movement of the driving pulley and the driven pulley in proportion to the amount of backlash. . This time lag significantly reduces positioning accuracy. These are NG machine tools, machining centers, and OEMs that perform high-precision numerical control.
This is a decisive drawback in devices such as A.
この対策としてバツクラツシユを少なくする伝動装置が
いくつか提案されている。その一つは。As a countermeasure to this problem, several transmission devices that reduce backlash have been proposed. One of them is.
第２図に示すように、ベルト歯１０４の幅をプーリ歯溝
１０５の幅と等しくするか、やや大きめにしてかみ合わ
せる装置である。この装置によれば、プーリ外径および
ベルト長さの精度を厳しく管理しても、ベルトａが摩耗
するなどのベルト歯の損傷か発生し易く、実用的ではな
い。別の一つは、第３図および第４図１こ示すように、
駆動ブーりと被動プーリとのいづれをも二個のブーＩＪ
１０６，１０７で構（ｉｙ Ｌ 、そのプーリ歯の位
相がずれている。この装置においてもベルト歯溝の幅と
プーリ歯の幅とがほぼ等しいため、結局、上記第２図の
場合と同じくベルト歯の損傷が発生しやすい。しかも、
ベルト縦裂の原因ともなり、実用的ではない。As shown in FIG. 2, this is a device in which the width of the belt teeth 104 is made equal to or slightly larger than the width of the pulley tooth groove 105 and engaged. According to this device, even if the accuracy of the pulley outer diameter and belt length is strictly controlled, damage to the belt teeth such as wear of the belt a tends to occur, which is not practical. Another one is as shown in Figures 3 and 4.
Both the driving pulley and the driven pulley are equipped with two boots IJ.
106 and 107 (iy L, the phase of the pulley teeth is shifted. In this device as well, the width of the belt tooth groove and the width of the pulley tooth are almost equal, so in the end, the belt Teeth damage is more likely to occur.Moreover,
This is not practical as it may cause the belt to crack vertically.
本発明の目的は、バックラッシュがなくしかもベルト歯
の損傷が極小である歯付きベルト伝動装置を提供するこ
とにある。本発明の他の目的は。SUMMARY OF THE INVENTION An object of the present invention is to provide a toothed belt transmission device that is free from backlash and causes minimal damage to belt teeth. Another object of the invention is.
バックラッシュがないために精密伝動や位置決め伝動に
有用な歯付きベルト伝動装置を提供することにある。An object of the present invention is to provide a toothed belt transmission device that is useful for precision transmission and positioning transmission because it has no backlash.
本発明の装置は、歯付きベルトおよびプーリを崩し、該
ベルトもしくはプーリーの歯ピッチか一つおきにＰｌｇ
よひＰ２であり、これとかみ合う該プーリもしくはベル
トの歯ピッチがＰ３であり。The device of the present invention breaks down a toothed belt and a pulley so that every other tooth pitch of the belt or pulley is
The pitch is P2, and the tooth pitch of the pulley or belt that meshes with this is P3.
そしてこれら歯ピッチが下記式ＩＩＩ〜＋３１の関係を
満たすものであり、そのことにより上記目的が達成され
る：
ｐｌ ＋ｐ２工２Ｐ３ ・・ｆｉｌ
Ｐ１＋ α＝ Ｐ３ ・（２）
Ｐ２−α＝ ｐ３ ・・・（３１
（α：淀数）
定数αは歯ピッチＰ３の約１〜約３０φ、好ましくは約
５〜約２０係に設定される。αが過度に小さいとベルト
歯とプーリ溝との間隙が過小となり、ベルト歯の損傷の
原因となる。αが［相］度に太きいとベルト歯とプーリ
溝との間隙が過大となり。These tooth pitches satisfy the relationships of the following formulas III to +31, thereby achieving the above purpose: pl + p2 2 P3...fil P1+ α= P3 (2) P2-α= p3...・(31 (α: stagnant number) The constant α is set to about 1 to about 30φ of the tooth pitch P3, preferably about 5 to about 20 times. If α is too small, the gap between the belt teeth and the pulley groove will increase. If α is too large, the gap between the belt teeth and the pulley groove will become too large.
ベルト走行性ぢよびベルト伝動能力か低下する。Belt runnability and belt transmission capacity decrease.
ＰｌおよびＰ２がベルト歯ピッチであるとき。When Pl and P2 are belt tooth pitches.
Ｐ３はブーり歯ピッチとなり、上記式ｉ１１〜（３１は
次式（４）〜（６）に置きかえられる：
ＰＢＸ ＋ ＰＢ２＝２Ｐｐ３ ・・（４１１’Ｂ１＋
σ ＝ Ｐｐ３ ・・・（５）Ｐｌ２− α ＝ Ｐ
ｐ３ ・・・（６）（ＰａｌおよびＰｌ２は一つおきの
ベルト歯ピッチｉ ’ｐ３はプーリ歯ピッチ；そしてα
は定数）ＰｌおよびＰ２がプーリ歯ピッチであるとき、
Ｐ３はベルト歯ピッチとなり、上記式ｉｌｌ〜（３１
は次式（７）〜（９）に置きかえられる：
Ｐｐｌ ＋ Ｐｐ２ ＝ ２ＰＢ３ ・（７）１）ｐ
ｌ＋ α ＝ ｌ’Ｂ３ ・・・（８１１′Ｐ２− α
＝ Ｐｌ３ ・・・（９）（ＰｐｌおよびＰア２は一
つおきのグーり歯ピッチ；Ｐｌ３はベルト歯ピッチ；そ
してαは定数）本発明に用いられる歯伺きベルトはその
材ＪＢや歯形において格別である必要はなく、従来から
知られている台形歯形のタイミングベルト、開−歯形の
タイミングベルトなど′の歯ピッチをイ蔭正したものと
考えられうる。歯付きブーりについても同じく格別であ
る必要はなく、従来からよく知られているブーりの歯ピ
ッチを本発明の歯ピ・ノチに修正したものと考えられう
る。P3 becomes the boolean tooth pitch, and the above formulas i11 to (31) are replaced with the following formulas (4) to (6): PBX + PB2=2Pp3 ... (411'B1+
σ = Pp3 ... (5) Pl2- α = P
p3...(6) (Pal and Pl2 are every other belt tooth pitch i 'p3 is the pulley tooth pitch; and α
is a constant) When Pl and P2 are the pulley tooth pitches,
P3 is the belt tooth pitch, and the above formula ill ~ (31
is replaced with the following equations (7) to (9): Ppl + Pp2 = 2PB3 ・(7)1)p
l+ α = l'B3...(811'P2- α
= Pl3...(9) (Ppl and Pa2 are every other tooth pitch; Pl3 is the belt tooth pitch; and α is a constant) The toothed belt used in the present invention is determined by its material JB and tooth profile. There is no need to be particular about this, and it can be considered as a modification of the tooth pitch of conventionally known trapezoidal tooth-shaped timing belts, open-toothed timing belts, etc. Similarly, the toothed boob does not need to be particularly special, and can be considered as a modification of the tooth pitch of a conventionally well-known boob to the tooth pitch and notch of the present invention.
以下に本発明を実施例について述べる。The present invention will be described below with reference to examples.
実施例１
第５図および第６図に示すように１本発明の歯付きベル
ト１はその歯１１のピッチか一向毎にＦＢＩおよびＰｌ
２である。ベルト１のピッチは、それゆえ、全体として
ＰＢＩ −Ｐｌ２− Ｐａｌ −Ｐｌ２・・・となる。Embodiment 1 As shown in FIGS. 5 and 6, the toothed belt 1 of the present invention has FBI and Pl.
It is 2. The pitch of the belt 1 is therefore PBI - Pl2 - Pal - Pl2 . . . as a whole.
これとかみ合うプーリ２は、一定のピッチＰＰ３である
。これら歯ピッチは前記式１４）〜（６）の関係を満た
すので、第７図に示すように、ベルト歯１１のピッチＰ
Ｂ１の部分においてはプーリ＃２１に対してバックラッ
シュがまったくない。バックラッシュのないプーリ歯の
隣に位置するプーリ歯２１０１こ対してはベルト歯１１
が接触しておらず間隙が午じているが、これはプーリ歯
２１を包しベルト歯１１および１１がプーリ＃２１とか
み合うときのベルト歯１１の逃げ場の役目を果たしてい
る。そのため、ブーり歯２１に接するベルト歯１１ｉこ
は大きな圧力がかからず、その結果、ベルト歯の摩耗損
傷か極小となる。The pulley 2 that meshes with this has a constant pitch PP3. Since these tooth pitches satisfy the relationships of equations 14) to (6) above, the pitch P of the belt teeth 11 as shown in FIG.
In the part B1, there is no backlash at all with respect to pulley #21. Belt tooth 11 as opposed to pulley tooth 2101 located next to the pulley tooth without backlash.
are not in contact and there is a gap, which wraps around the pulley teeth 21 and serves as an escape area for the belt teeth 11 when the belt teeth 11 and 11 mesh with the pulley #21. Therefore, no large pressure is applied to the belt teeth 11i in contact with the boob teeth 21, and as a result, wear and tear on the belt teeth is minimized.
実施例２
第８図および第９図に示すように１本発明の歯付きベル
ト１は一定のピッチＰａ３である。これとかみ合うプー
リ２はその歯２１のピッチが一歯毎にＰｐｌおよびＰＰ
２である。よって、プーリ２のピッチは全体としてＰｐ
ｌ −ＰＰ２− Ｐｐｌ −ＰＰ２・・となる。Embodiment 2 As shown in FIGS. 8 and 9, the toothed belt 1 of the present invention has a constant pitch Pa3. The pulley 2 that meshes with this has a pitch of Ppl and PP for each tooth 21.
It is 2. Therefore, the overall pitch of pulley 2 is Pp
l -PP2- Ppl -PP2...
これら歯ピッチは前記式（７１〜（９）の関係を満たす
ので、第１０図に示すように、ベルト歯１１はプーリ歯
２１に対し一つおきにバックラッシュかまっｋく存在し
ない。Since these tooth pitches satisfy the relationships of equations (71 to (9)), there is no backlash between every other belt tooth 11 and pulley tooth 21, as shown in FIG.
本発明のベルト伝導装置は、このように、ベルト歯もし
くはブーり歯のピッチを独特の関係に設定し、相隣る二
つの歯でバックラッシュをなくすよう構成されている。The belt transmission device of the present invention is thus configured so that the pitches of the belt teeth or boolean teeth are set in a unique relationship to eliminate backlash between two adjacent teeth.
それゆえ、簡単な構造でありながら、バックラッシュが
まったくなく、シたがって、ベルト歯の摩耗ｔμ傷かな
い。しかもプーリを正逆回転させて精密伝動・位置決め
伝動を行なう必要のある精密機器に有効に利用されうる
。Therefore, although it has a simple structure, there is no backlash at all, and therefore the belt teeth are not damaged by wear. Furthermore, it can be effectively used in precision equipment that requires precision transmission and positioning transmission by rotating the pulley in forward and reverse directions.
第１図〜第４図はそれぞれ従来の歯付きベルト伝動装置
の要部正面図および要部斜視図、第５図〜ｌ耶７図は本
発明の歯付きベルト伝動装置の一実施例の要部説明図お
よび第８図〜第１０図は本発明の他の実施例の要部説明
図である：
１．１００ ・歯１゛」きベルト、 ２．１０１．１０
６．１０７−・・プーリ、１．１，１０２，１０４・・
ベルト歯、２１，２１０・、ブーり歯、 Ｐａｌ、 Ｐ
Ｈ１，ＰＨ１・ベルト歯ピ・ンチ。
Ｐｐｌ、 ＰＰ２． ＰＰ３・・ブーり歯ピッチ。
以 上
第１図
第２図
第３図 第４図
第５図
第６図
第７図1 to 4 are a front view and a perspective view of a main part of a conventional toothed belt transmission device, respectively, and FIGS. 1.100 - Belt with 1" tooth, 2.101.10
6.107-...Pulley, 1.1,102,104...
Belt tooth, 21,210・, boolean tooth, Pal, P
H1, PH1・Belt tooth pinch. Ppl, PP2. PP3...boo tooth pitch. Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 Figure 6 Figure 7
Claims (1)
くはプーリの歯ピッチが一つおきにＰｌおよびＰ２であ
り、これとかみ合う該ブーりもしくはベルトの歯ピッチ
がＰ３であり、そしてこれら歯ピッチが下記式ｉ１１〜
（３）の関係を満たす歯付きベルト伝動装置： ）’１＋Ｐ２＝２Ｐ３ ・・・ｉｌ＋ Ｐ１＋α＝ Ｐ３ ・・・（２） Ｐ２− ａ ＝ Ｐ３ ＝ｌ：ｌｌ （α：定数） ２、前記定数αが該歯ピッチＰ３の約１〜約３０係の範
囲にある特許請求の範囲第１ＪＡに記載の装置。[Claims] 1. It has a toothed belt and a pulley, and the tooth pitch of the belt or pulley is Pl and P2 every other time, and the tooth pitch of the booby or belt that meshes with the belt is P3. , and these tooth pitches are expressed by the following formula i11~
A toothed belt transmission device that satisfies the relationship (3): )'1+P2=2P3...il+P1+α=P3...(2) P2- a=P3=l:ll (α: constant) 2. The constant α The apparatus of claim 1, wherein the tooth pitch P3 is in the range of about 1 to about 30 parts of the tooth pitch P3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19208083A JPS6084461A (en) | 1983-10-13 | 1983-10-13 | Transmission gear of toothed belt |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19208083A JPS6084461A (en) | 1983-10-13 | 1983-10-13 | Transmission gear of toothed belt |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6084461A true JPS6084461A (en) | 1985-05-13 |
| JPS622172B2 JPS622172B2 (en) | 1987-01-19 |
Family
ID=16285302
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19208083A Granted JPS6084461A (en) | 1983-10-13 | 1983-10-13 | Transmission gear of toothed belt |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6084461A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999022922A3 (en) * | 1997-11-04 | 2000-02-10 | Loctite Corp | Gaskets and method and apparatus for forming gaskets |
| DE102007003399A1 (en) * | 2007-01-23 | 2008-07-24 | Schaeffler Kg | Rotational disc with a periodically changing tooth space geometry |
-
1983
- 1983-10-13 JP JP19208083A patent/JPS6084461A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999022922A3 (en) * | 1997-11-04 | 2000-02-10 | Loctite Corp | Gaskets and method and apparatus for forming gaskets |
| DE102007003399A1 (en) * | 2007-01-23 | 2008-07-24 | Schaeffler Kg | Rotational disc with a periodically changing tooth space geometry |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS622172B2 (en) | 1987-01-19 |
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