JPH0631642A - Screw tightening machine - Google Patents
Screw tightening machineInfo
- Publication number
- JPH0631642A JPH0631642A JP20967192A JP20967192A JPH0631642A JP H0631642 A JPH0631642 A JP H0631642A JP 20967192 A JP20967192 A JP 20967192A JP 20967192 A JP20967192 A JP 20967192A JP H0631642 A JPH0631642 A JP H0631642A
- Authority
- JP
- Japan
- Prior art keywords
- screw
- spring
- cam
- speed change
- torque
- 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
Landscapes
- Friction Gearing (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は比較的径が大きいねじ
（例えば径が１０〜１６ｍｍ程度のねじ）の取り付けお
よび取り外し（着脱）に使用されるねじ締め機に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a screw tightening machine used for attaching and detaching (removing) a screw having a relatively large diameter (for example, a screw having a diameter of about 10 to 16 mm).
【０００２】[0002]
【従来の技術】現在市販されているねじ締め機の大半は
空気圧を利用するインパクトレンチである。このものは
比較的軽量で作業性も良いが、激しい衝撃音を発生する
という大きな欠点がある。インパクトレンチのような騒
音を発生しないねじ締め機として電動機駆動のものも知
られているが、この形式に属する多くのものは捩込み時
間が長すぎるという難点がある。2. Description of the Related Art Most of the screw tighteners currently on the market are pneumatic impact wrench. Although this is relatively lightweight and has good workability, it has a major drawback that it produces a violent impact sound. An electric motor driven screw tightener such as an impact wrench is also known, but most of the screw tighteners of this type have a drawback that the screwing time is too long.
【０００３】一方、本願の出願人はねじ締め機に利用し
得る実公平１ー２２９９４号公報に記載される実用新案
登録第１８０６７１７号の摩擦無段変速機を先に開発し
た。この摩擦無段変速機は、入力軸より出力軸に至る伝
動系が遊星運動を行う複数の円錐形転子を含んで構成さ
れ、複数の円錐形転子の円錐面に共通に摩擦係合する非
回転の変速リングが設けられると共に、入力軸上の伝動
車に摩擦係合する凹断面形の伝動面と出力軸上の伝動車
に摩擦係合する平坦な伝動面とが円錐形転子上に設けら
れている形式のものにおいて、一端を変速機のケーシン
グにより支持される複数本のばね杆を設けこれら複数本
のばね杆の他端を変速リングに係合させたものである。On the other hand, the applicant of the present application first developed a friction continuously variable transmission of utility model registration No. 1806717 described in Japanese Utility Model Publication No. 1-29944, which can be used for a screw tightener. In this friction continuously variable transmission, a transmission system from an input shaft to an output shaft is configured to include a plurality of conical rotors that perform planetary motion, and frictionally engages conical surfaces of the plurality of conical rotors in common. A non-rotational speed change ring is provided, and a transmission surface having a concave cross section that frictionally engages with a transmission wheel on the input shaft and a flat transmission surface that frictionally engages with the transmission wheel on the output shaft are provided on the conical rotor. Of the type provided in (1), a plurality of spring rods, one end of which is supported by the casing of the transmission, are provided, and the other ends of the plurality of spring rods are engaged with the transmission ring.
【０００４】上記摩擦無段変速機は出力軸の回転速度が
０のときまたは出力軸の回転速度が０となったときに発
生し得るトルク（以下、ストールトルクと言う。）が大
きいのでその点を利用してねじ締め機を構成させること
ができるのであるが、この摩擦無段変速機を利用するね
じ締め機は、適用することができるのは径が５ｍｍ以下
の小ねじに限られ、径が大きいねじには適用することが
できない。The friction continuously variable transmission has a large torque (hereinafter referred to as a stall torque) which can be generated when the rotation speed of the output shaft is 0 or when the rotation speed of the output shaft is 0. It is possible to configure a screw tightening machine by using the. However, the screw tightening machine using this friction continuously variable transmission can be applied only to machine screws with a diameter of 5 mm or less. Cannot be applied to large screws.
【０００５】多くの場合、ねじの弛めに必要とするトル
クＴ2は締めに必要とするトルクＴ1より大きい。従っ
て、ねじ締め機はそれを逆転して弛め作業を行なおうと
するときに発生するトルクの最大値がそれを正転して締
め作業を行なおうとするときに発生するトルクの最大値
より大きいことが望ましいのであるが、上記摩擦無段変
速機を利用するねじ締め機はこの機能をもつものとして
構成され難い。In many cases, the torque T 2 required for loosening the screw is greater than the torque T 1 required for tightening. Therefore, the maximum value of the torque generated when the screw tightener reverses it and tries to perform loosening work is greater than the maximum torque generated when it rotates forward and tightens. It is desirable that the size is large, but it is difficult for a screw tightener utilizing the friction continuously variable transmission to be configured to have this function.
【０００６】[0006]
【発明が解決しようとする課題】本発明は、従来のねじ
締め機の上記事情にかんがみ、運転が静粛に行われ、且
つ、程度を所期の通りにした締め込みが行われるばかり
でなく、締め込まれたねじの弛めを必要に応じ容易に行
い得るようにすることを解決されるべき課題とするもの
である。SUMMARY OF THE INVENTION In view of the above circumstances of the conventional screw tightening machine, the present invention not only performs the operation quietly and tightens the screw in a desired degree, The problem to be solved is to make it possible to loosen the tightened screw easily if necessary.
【０００７】[0007]
【課題を解決するための手段】本発明によるねじ締め機
は、変速リングを高速側に移動させようとする力を及ぼ
すばねと、負荷トルクの増大に伴って変速リングを低速
側に移動させようとする力を及ぼすカム機構とを備え、
出力軸の回転速度を０にする点を変速範囲に含み、上記
カム機構にはねじ込み作業用のカム面と弛め作業用のカ
ム面とが後者の発生する力が前者の発生する力より大き
くして設けられている摩擦無段変速機によりドライバー
要素が駆動されていることを特徴とする。SUMMARY OF THE INVENTION In a screw tightener according to the present invention, a spring exerting a force to move a speed change ring to a high speed side and a speed change ring to a low speed side as load torque increases. And a cam mechanism that exerts a force
The point where the rotational speed of the output shaft is set to 0 is included in the shift range, and in the cam mechanism, the force generated by the latter is greater than the force generated by the former by the cam surface for screwing work and the cam surface for loosening work. The driver element is driven by the continuously variable friction continuously variable transmission.
【０００８】以下においては上記本発明によるねじ締め
機を図に関連して具体的に説明することとする。図１〜
図５のうち、図１は本発明によるねじ締め機の１例を示
す垂直断面図、図２，図３，図４は図１のねじ締め機に
おいて設けられた「締め作業用カム面」と「弛め作業用
カム面」との説明図，図５は図１のねじ締め機に設けら
れた摩擦無段変速機の「トルクー回転速度」線図であ
る。The screw tightener according to the present invention will be described below in detail with reference to the drawings. Figure 1
5, FIG. 1 is a vertical sectional view showing an example of a screw tightening machine according to the present invention, and FIGS. 2, 3 and 4 show “cam surface for tightening work” provided in the screw tightening machine of FIG. FIG. 5 is an explanatory view of a "slackening cam surface", and FIG. 5 is a "torque-rotational speed" diagram of the friction continuously variable transmission provided in the screw tightener of FIG.
【０００９】図１において、１は駆動源としての電動
機、２は電動機１により駆動される摩擦無段変速機、
３，４は、それぞれ、摩擦無段変速機２の入力軸と出力
軸である。摩擦無段変速機２の入力軸３より出力軸４に
至る伝動系は遊星運動を行う複数の円錐形転子５を含ん
で構成され、これら複数の円錐形転子５の円錐面に共通
に摩擦係合する非回転の変速リング６が設けられると共
に、円錐形転子５には入力軸３上の伝動車７に摩擦係合
する凹断面形の伝動面８と、出力軸４上の軌道リング９
に摩擦係合する平坦な伝動面１０とが設けられている。In FIG. 1, 1 is an electric motor as a drive source, 2 is a friction continuously variable transmission driven by the electric motor 1,
Reference numerals 3 and 4 are an input shaft and an output shaft of the friction continuously variable transmission 2, respectively. The transmission system from the input shaft 3 to the output shaft 4 of the friction continuously variable transmission 2 is configured to include a plurality of conical rotors 5 that perform a planetary motion, and the conical surfaces of the plurality of conical rotors 5 are commonly provided. A non-rotational speed change ring 6 for frictional engagement is provided, and a conical rotor 5 has a concave transmission surface 8 for frictionally engaging a transmission wheel 7 on the input shaft 3 and a track on the output shaft 4. Ring 9
And a flat transmission surface 10 frictionally engaged with.
【００１０】１１はねじに回転を与える作用を行うドラ
イバー要素で、このドライバー要素１１は摩擦無段変速
機２の出力軸４により減速歯車装置１２ａ，１２ｂを介
して駆動される。減速歯車装置１２ａ，１２ｂは太陽歯
車，遊星歯車，遊星歯車にかみ合う内歯歯車および遊星
歯車のキャリアより成り、出力回転はキャリアより取り
出される差動歯車形式のものである。減速歯車装置１２
ａ，１２ｂは摩擦無段変速機２の回転速度が０に近付い
たときに発生するトルクの大きさを適宜増大するための
要素でそれらの減速比はねじ込まれるねじの径，ピッチ
等を考慮に入れて決定される。Reference numeral 11 denotes a driver element for giving a rotation to the screw. The driver element 11 is driven by the output shaft 4 of the friction continuously variable transmission 2 through reduction gear units 12a and 12b. The reduction gear units 12a and 12b are composed of a sun gear, a planetary gear, an internal gear meshing with the planetary gear, and a carrier of the planetary gear. The output rotation is of a differential gear type taken out from the carrier. Reduction gear unit 12
Reference characters a and 12b are elements for appropriately increasing the magnitude of the torque generated when the rotational speed of the friction continuously variable transmission 2 approaches 0, and their reduction ratios take into consideration the diameter and pitch of the screwed screw. It is decided to put.
【００１１】摩擦無段変速機２には変速リング６を高速
側に移動させようとする力を及ぼすばね１３と負荷トル
クの増大に伴って変速リング６を低速側に移動させよう
とする力を及ぼすカム装置１４とが設けられている。図
２，図３，図４はカム装置１４の説明図で、図２は軽負
荷の高速回転時の状態を、図３はねじ込み作業の終わり
の状態を、図４は弛め作業の開始時の状態を示す。これ
らの図において、１５は変速機のケース（静止部）、１
６は変速機のケース１５と変速リング６との間に介在さ
れたボールである。カム装置１４には、ねじ込み作業時
に作用するカム面１７ａ，１７ｂと、ねじの弛め作業時
に作用するカム面１８ａ，１８ｂとが設けられている。
ねじの弛め作業時に作用するカム面18ａ，18ｂの傾斜角
θ2はねじ込み作業時に作用するカム面１７ａ，１７ｂ
の傾斜角θ1より大きく、従ってねじの弛め作業はねじ
込み作業が行われるときに作用するトルクより大きいト
ルクを作用させて行われる。The friction continuously variable transmission 2 is provided with a spring 13 exerting a force for moving the speed change ring 6 to a high speed side and a force for moving the speed change ring 6 to a low speed side as the load torque increases. A cam device 14 is provided. 2, 3 and 4 are explanatory views of the cam device 14, FIG. 2 shows a state at the time of light load and high speed rotation, FIG. 3 shows a state at the end of screwing work, and FIG. 4 shows a state at the start of loosening work. Indicates the state of. In these figures, 15 is a transmission case (stationary part), 1
Reference numeral 6 is a ball interposed between the case 15 of the transmission and the transmission ring 6. The cam device 14 is provided with cam surfaces 17a and 17b that act during a screwing operation and cam surfaces 18a and 18b that act during a screw loosening operation.
The inclination angles θ 2 of the cam surfaces 18a and 18b that act during the screw loosening work are determined by the cam surfaces 17a and 17b that act during the screwing work.
Is larger than the inclination angle θ 1 of the screw, and therefore the screw loosening work is performed by applying a torque larger than the torque that acts when the screwing work is performed.
【００１２】１９は変速リング６を高速側に移動させよ
うとする力を及ぼすばね１３の調節装置で、この装置は
ばね１３を受けるばね受座２０と、変速リング６の端面
を受ける推力軸受２１と、ばね受座２０の位置を外部よ
り調節するねじ送り装置２２とより成る。Reference numeral 19 is an adjusting device for the spring 13 which exerts a force for moving the transmission ring 6 to the high speed side. This device has a spring seat 20 for receiving the spring 13 and a thrust bearing 21 for receiving the end face of the transmission ring 6. And a screw feed device 22 for adjusting the position of the spring seat 20 from the outside.
【００１３】図５はねじ締め機の出力トルク特性を示す
線図で、横座標に変速範囲を、縦座標に出力トルクを取
って示す。この図において、点Ａ，Ｂ，Ｃはそれぞれ、
軽負荷の高速回転時のトルク，ねじ込み作業の終わりの
時のトルク，弛め作業の開始点のトルクを示す。Ｗは変
速範囲である。FIG. 5 is a diagram showing the output torque characteristic of the screw tightener, in which the abscissa represents the speed change range and the ordinate represents the output torque. In this figure, points A, B and C are respectively
The torque at the time of light load high speed rotation, the torque at the end of screwing work, and the torque at the starting point of loosening work are shown. W is a shift range.
【００１４】[0014]
【発明の効果】多くの場合、締め付けられたねじを弛め
るのに必要とするトルクの大きさはねじの取り付けに際
して加えられたトルクより可なり大きいので、従来のね
じ締め機はねじの装着とねじの取り外しに共用すること
ができないのであるが、本発明によるねじ締め機は入力
軸を正転させてねじの締め付けを行うときに発生し得る
トルクの最大値より充分大きいトルクを入力軸を逆転さ
せて締め付けられたねじの弛めを行うときに発生し得る
ようにされているので取り付けられたねじに何等かの欠
陥（疵，径の偏差等）が発見されたときに欠陥のあるね
じを直ちに外して除去し得るようにするものである。作
業能率の面より言えば、本発明は出力軸の回転速度を０
とする点を変速範囲に含み、且つ出力軸の回転速度が０
となる点において大きい出力トルクを発生しうる形式の
摩擦無段変速機を利用してねじ締め機を小形化すると共
にねじの取り付けが高い効率の下に行われるようにする
ものである。In many cases, the amount of torque required to loosen a tightened screw is significantly greater than the torque applied during screw installation, so that conventional screw tighteners use screw mounting and screwing. However, the screw tightener according to the present invention reverses the input shaft with a torque sufficiently larger than the maximum torque that can be generated when the screw is tightened by rotating the input shaft in the forward direction. It is designed to occur when loosening a tightened screw so that if any defect (defect, diameter deviation, etc.) is found in the attached screw, the defective screw is immediately replaced. It should be removed so that it can be removed. In terms of work efficiency, the present invention reduces the rotational speed of the output shaft to 0.
Is included in the speed change range, and the output shaft rotation speed is 0
In view of the above, the friction continuously variable transmission of the type capable of generating a large output torque is used to downsize the screw tightener and to attach the screw with high efficiency.
【図１】本発明によるねじ締め機の１例を示す垂直断面
図である。FIG. 1 is a vertical sectional view showing an example of a screw tightener according to the present invention.
【図２】図１に示すものの「締め作業用カム面」と「弛
め作業用カム面」との関係を軽負荷の高速回転時におい
て示す図である。FIG. 2 is a diagram showing the relationship between the “tightening work cam surface” and the “slackening work cam surface” shown in FIG. 1 during high-speed rotation with a light load.
【図３】図３は図１に示すものの「締め作業用カム面」
と「弛め作業用カム面」との関係をねじ込み作業の終了
時において示す図である。FIG. 3 is a “cam surface for tightening work” of the one shown in FIG. 1.
It is a figure which shows the relationship between "the cam surface for loosening work" at the time of the completion of screwing work.
【図４】図４は図１に示すものの「締め作業用カム面」
と「弛め作業用カム面」との関係を弛め作業の開始時に
おいて示す図である。FIG. 4 is a “cam surface for tightening work” of FIG. 1;
It is a figure which shows the relationship between "and a loosening cam surface" at the time of the start of loosening work.
【図５】図５はねじ締め機の出力トルク特性を示す線図
である。FIG. 5 is a diagram showing an output torque characteristic of a screw tightener.
１ 電動機 ２ 摩擦無段変速機 ３ 入力軸 ４ 出力軸 ５ 円錐形転子 ６ 変速リング ７ 入力軸上の伝動車 ８ 凹断面形の伝動面 ９ 軌道リング １０ 平坦な伝動面 １１ ドライバー要素 １２ａ，１２ｂ 減速歯車装置 １３ 変速リングを高速側に移動させようとする力を及
ぼすばね １４ カム装置 １５ 変速機のケース １６ ボール １７ａ，１７ｂ ねじ込み作業時に作用するカム面 １８ａ，１８ｂ ねじの弛め作業時に作用するカム面 １９ ばね１３の調節装置 ２０ ばね受座 ２１ 推力軸受 ２２ ねじ送り装置 Ａ 軽負荷の高速回転時のトルク Ｂ ねじ込み作業の終わりの時のトルク Ｃ ねじの弛め作業の開始点のトルク Ｗ 変速範囲 θ1 ねじ込み作業時に作用するカム面の傾斜角 θ2 ねじの弛め作業時に作用するカム面の傾斜角DESCRIPTION OF SYMBOLS 1 Electric motor 2 Friction continuously variable transmission 3 Input shaft 4 Output shaft 5 Conical rotor 6 Transmission ring 7 Transmission wheel on input shaft 8 Transmission surface with concave cross section 9 Track ring 10 Flat transmission surface 11 Driver element 12a, 12b Reduction gear device 13 Spring that exerts a force to move the speed change ring to the high speed side 14 Cam device 15 Transmission case 16 Balls 17a, 17b Cam surfaces 18a, 18b that act during screwing work Act when loosening work Cam surface 19 Spring 13 adjustment device 20 Spring seat 21 Thrust bearing 22 Screw feed device A Torque at high speed with light load B Torque at the end of screwing work C Torque at start of screw loosening work W Shift Range θ 1 Inclination angle of cam surface that acts during screwing operation θ 2 Inclination angle of cam surface that acts during loosening operation
Claims (2)
る力を及ぼすばねと、負荷トルクの増大に伴って変速リ
ングを低速側に移動させようとする力を及ぼすカム機構
とを備え、出力軸の回転速度を０にする点を変速範囲に
含み、上記カム機構にはねじ込み作業用のカム面と弛め
作業用のカム面とが後者の発生する力が前者の発生する
力より大きくして設けられている摩擦無段変速機により
ドライバー要素が駆動されることを特徴とするねじ締め
機。1. A spring equipped with a spring for exerting a force to move the speed change ring to a high speed side, and a cam mechanism for exerting a force to move the speed change ring to a low speed side with an increase in load torque. The point where the rotational speed of the shaft is set to 0 is included in the speed change range, and the cam mechanism for screwing work and the cam surface for loosening work have a force generated by the latter that is larger than the force generated by the former. A screw tightening machine characterized in that a driver element is driven by a friction continuously variable transmission provided in the.
る力を及ぼすばねを受けるばね受座と変速リングの端面
との間に推力軸受とばねとを介在させると共に、このね
じの強さを変速機の外部より加減する調節装置を設けた
請求項１のねじ締め機。2. A thrust bearing and a spring are interposed between a spring seat for receiving a spring exerting a force for moving the speed change ring to a high speed side and an end face of the speed change ring, and the strength of this screw is adjusted. The screw tightener according to claim 1, further comprising an adjusting device that adjusts from outside the transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20967192A JPH0631642A (en) | 1992-07-14 | 1992-07-14 | Screw tightening machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20967192A JPH0631642A (en) | 1992-07-14 | 1992-07-14 | Screw tightening machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0631642A true JPH0631642A (en) | 1994-02-08 |
Family
ID=16576682
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20967192A Pending JPH0631642A (en) | 1992-07-14 | 1992-07-14 | Screw tightening machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0631642A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011089766A1 (en) * | 2010-01-25 | 2011-07-28 | 株式会社マキタ | Power tool |
| JP2011148070A (en) * | 2010-01-25 | 2011-08-04 | Makita Corp | Power tool |
-
1992
- 1992-07-14 JP JP20967192A patent/JPH0631642A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011089766A1 (en) * | 2010-01-25 | 2011-07-28 | 株式会社マキタ | Power tool |
| JP2011148070A (en) * | 2010-01-25 | 2011-08-04 | Makita Corp | Power tool |
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