JP3446467B2 - Electric cutting or bending tool - Google Patents
Electric cutting or bending toolInfo
- Publication number
- JP3446467B2 JP3446467B2 JP08801696A JP8801696A JP3446467B2 JP 3446467 B2 JP3446467 B2 JP 3446467B2 JP 08801696 A JP08801696 A JP 08801696A JP 8801696 A JP8801696 A JP 8801696A JP 3446467 B2 JP3446467 B2 JP 3446467B2
- Authority
- JP
- Japan
- Prior art keywords
- cam
- cutting
- bending
- output shaft
- pin
- 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
Description
【０００１】[0001]
【発明の属する技術分野】本発明は住宅やビルの建築、
外構、土木工事等において、鉄筋等の棒材やパイプ材等
の被加工材を任意の長さに切断すると共に曲げることが
できる携帯式の電動切断曲げ工具に関するものである。
以下切断及び曲げるものを鉄筋として説明する。TECHNICAL FIELD The present invention relates to the construction of houses and buildings,
The present invention relates to a portable electric cutting / bending tool capable of cutting and bending a work material such as a bar material such as a reinforcing bar or a pipe material into an arbitrary length in an exterior structure, a civil engineering work, or the like.
Hereinafter, what is cut and bent will be described as a reinforcing bar.
【０００２】[0002]
【従来の技術】住宅の基礎、外構のブロック塀、ビルの
鉄筋コンクリートその他土木工事のコンクリート構造物
には、コンクリートの補強材として鉄筋が多数使用され
る。直径が１０、１３、１６、１９、２２ｍｍと規格に
定められた寸法の鉄筋が通常５ｍ程度の定尺で市販され
ており、これを建築図面に基づいて所定の長さに切断し
たり、所定の角度に曲げて結束線７４等で組み立てて用
いる。図５は住宅の基礎に用いる鉄筋の状態を示す。直
径１０ｍｍの鉄筋７２を長さ１ｍ程度に切断し９０度に
Ｌ字型に曲げて用いる場合、直径１３ｍｍの鉄筋７３を
１．２ｍ程度に切断した後上端を１８０度のＵ字形に曲
げて用いる場合等、切断し曲げて使うパターンは様々で
ある。これらの切断・曲げ作業に用いられる工具は、鉄
筋を任意の長さに切断可能であると共に４５〜１８０度
まで任意の角度で曲げれるようにする必要がある。2. Description of the Related Art A large number of reinforcing bars are used as a reinforcing material for concrete in a foundation of a house, a block wall of an exterior, a reinforced concrete of a building and other concrete structures for civil engineering work. Reinforcing bars with diameters of 10, 13, 16, 19, 22 mm and standard dimensions are usually sold on the market with a fixed length of about 5 m, which can be cut to a predetermined length based on architectural drawings or It is bent at an angle of 7 and assembled by using a binding wire 74 or the like. FIG. 5 shows the state of the reinforcing bars used for the foundation of the house. When the rebar 72 having a diameter of 10 mm is cut to a length of about 1 m and bent to an L shape at 90 degrees and used, the rebar 73 having a diameter of 13 mm is cut to about 1.2 m and then the upper end is bent to a U shape of 180 degrees for use. In various cases, there are various patterns for cutting and bending. The tools used for these cutting / bending operations are required to be able to cut the reinforcing bar to an arbitrary length and to be able to bend at an arbitrary angle of 45 to 180 degrees.
【０００３】従来切断・曲げ作業は、量が多量の場合
は、鉄筋加工専門業者が大型の専用機で切断や曲げをま
とめて数百数千と同時に行い使う業者に納めていた。し
かし、一般の戸建て住宅や外構工事あるいはビル等の鉄
筋の現場合わせの追加や誤りの修正には、１日２００〜
４００本と比較的少ないので鉄筋加工専門業者に頼むと
割高になる。あるいは現場合わせの加工が多く、鉄筋を
組む現場で現物に合わせて切断や曲げを行わねばならな
い等の理由により、例えば特開昭５６ー１４４８２６号
公報記載の切断曲げ工具を用いて切断・曲げを行ってい
た。この切断曲げ工具は、電動機の回転を複数の歯車列
で減速して出力軸に伝達し、出力軸上に形成された偏心
カムの最大径部で先端に切断刃が装着されたピストン状
の摺動子を押して鉄筋を切断すると共に同一出力軸の上
端に曲げ用のローラを装着したクランク状の腕金を取り
付け、腕金を回転させて鉄筋を曲げるものである。Conventionally, in the case of a large amount of cutting and bending work, a rebar processing specialist has used a large dedicated machine to perform cutting and bending at the same time for several hundreds and thousands at the same time, and then the cutting and bending work is carried out. However, for general detached houses, exterior construction work, addition of on-site alignment of reinforcing bars in buildings, etc.
Since it is a relatively small number of 400, it will be expensive if you ask a reinforcing bar processing specialist. Alternatively, for many reasons, such as processing on site, which requires cutting and bending according to the actual product at the site where the reinforcing bars are assembled, for example, cutting and bending using a cutting and bending tool described in JP-A-56-144826. I was going. This cutting and bending tool decelerates the rotation of the electric motor with a plurality of gear trains and transmits it to the output shaft, and at the maximum diameter part of the eccentric cam formed on the output shaft, a piston-shaped slide with a cutting blade attached to the tip. This is to cut the rebar by pushing the pendulum, and to attach a crank arm with a bending roller attached to the upper end of the same output shaft and rotate the arm to bend the rebar.
【０００４】しかしこの切断曲げ工具では、本発明が目
指す小型軽量で携帯式の低価格な切断曲げ工具を具体化
するには、以下の更なる改善を要する点がある。すなわ
ち
（１）鉄筋を切断する切断力は、例えば直径１３ｍｍの
鉄筋で５６０００Ｎもの強大な値となるが、前記摺動子
には何ら倍力効果が無いので、偏心カムが摺動子のカム
ローラを押す押し上げ力も切断力そのものの５６０００
Ｎ必要であり、偏心カムやこれを支える出力軸が強度確
保のために大きく重いものになり、これを駆動する歯車
列や電動機も大型になってしまう。
（２）前記切断用偏心カムと曲げ用腕金は離れた所に別
体で構成されているので、夫々を別部品として作る必要
があり、重くなると共に出力軸の長さも偏心カムの厚み
分長くなって外枠全体も大きくなってしまい携帯用とし
て不適であり、また別々に作る分コストが高くなる。However, with this cutting and bending tool, the following further improvements are required in order to realize a small, lightweight, portable, and low cost cutting and bending tool aimed at by the present invention. That is, (1) the cutting force for cutting the reinforcing bar is as strong as 56000 N for a reinforcing bar having a diameter of 13 mm, but since there is no boosting effect on the slider, the eccentric cam causes the cam roller of the slider to move. The push-up force and the cutting force itself are 56000.
N is required, the eccentric cam and the output shaft supporting the eccentric cam are large and heavy in order to secure strength, and the gear train and the electric motor for driving the eccentric cam are also large. (2) Since the cutting eccentric cam and the bending arm are separately formed at separate places, it is necessary to make each of them as a separate part, and the weight becomes heavy and the length of the output shaft is equal to the thickness of the eccentric cam. It becomes longer and the whole outer frame becomes larger, which makes it unsuitable for portable use, and the cost increases because it is made separately.
【０００５】[0005]
【発明が解決しようとする課題】本発明の目的は、上記
した従来の電動式切断曲げ工具の欠点を解消するための
下記（１）の課題、併せて現場での切断曲げ作業に最適
な携帯用の電動式切断曲げ工具とするための（２）〜
（４）の課題及びこれらの課題を解決するために新規な
構造の具現化のための（５）〜（８）の技術課題を解消
することである。SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned drawbacks of the conventional electric cutting and bending tool (1) described below, together with the most suitable portable work for cutting and bending work on site. (2) for making an electric cutting and bending tool for
It is to solve the problems (4) and the technical problems (5) to (8) for realizing a new structure in order to solve these problems.
【０００６】（１）従来の電動式切断曲げ工具の改善課
題
カムやこれを駆動する出力軸、歯車、電動機の力やトル
クをいかに小さくして同じ切断力を得、本体を小型軽量
化するか。またカムや腕金等比較的高価な機械加工部品
を共用化して小型で低価格なものにするか。(1) Problem to be solved in the conventional electric cutting and bending tool How to reduce the force and torque of the cam, the output shaft, the gear, and the electric motor for driving the cam to obtain the same cutting force to reduce the size and weight of the main body. . In addition, is it possible to share relatively expensive machined parts such as cams and braces to make them small and inexpensive?
【０００７】（２）カムの転動面の形状を工夫し、いか
に小さい出力軸駆動トルクでより大きな力を発生させ、
歯車や電動機、本体を小型軽量化するか。
（３）目で曲げ角を見ながら手加減でゆっくり調整しな
がら曲げる手動工具の便利さをいかに電動式で実現する
か。
（４）本体を切断曲げ作業を行いたい位置に持ち運び、
持ったままスイッチ操作が容易な手持式両用機とし、組
立後の鉄筋の所に本体を持ち上げて追加工できる工具を
提供する。(2) The shape of the rolling surface of the cam is devised to generate a larger force with a small output shaft drive torque,
Will the gears, electric motors, and main body be made smaller and lighter? (3) eye in the bending angle of how to achieve in the electric the convenience of slowly while adjusting bending Ru manually tool in holding back while watching. (4) Carry the body to the position where you want to cut and bend it,
It is a hand-held dual-purpose machine that allows easy switch operation while holding it, and provides a tool that allows the main body to be lifted to the rebar after assembly for additional machining.
【０００８】（５）切断作業と曲げ作業を両方できる電
動式切断曲げ工具のレイアウト上の課題として、地面に
横たわった長尺の重い鉄筋を曲げまたは切断する際に、
いかに鉄筋を垂直に立てて振り回す等の労力を使わず、
水平状態のまま本体の高さ分僅かに持ち上げるだけで楽
に切断、曲げを行えるようにするか。
（６）従来の定置型の曲げ工具では本体が重く安定で、
本体を人間が押える必要は無かったが、上記課題の解決
策として本体を手持ちできるほど小型軽量化すると、何
等かの本体保持手段が必要になる。この解決策として曲
げ作業時に、一方の手でハンドルを握ってスイッチを操
作し、他方の手で曲げる鉄筋を受けピンと中心ピンにあ
てがい固定するようにした場合、曲げピンで０度から１
８０度まで曲げられながら旋回する鉄筋の自由端側が作
業者に触れないようにするか。
（７）既に設置された鉄筋の上向き端部や横向き端部の
曲げ作業において、本体をいかに安定かつ容易に保持す
るか。
（８）カムと曲げピンで共用する出力軸を所定角度回転
したところで戻す必要があるが、戻す位置を決めるリミ
ットスイッチの故障等予期せぬ事態に対して、鉄筋が１
８０°以上曲げられ使い物にならなくなったり、本体が
破損したり等の保護をいかに行うか。(5) Electric cutting capable of both cutting work and bending work As a layout problem of a bending tool, when bending or cutting a long heavy reinforcing bar lying on the ground,
Without using labor such as vertically erection of reinforcing bars,
Is it possible to easily cut and bend by simply lifting the main unit in the horizontal position by the height of the main unit? (6) The conventional stationary bending tool has a heavy and stable body,
It was not necessary for a human body to press the body, but if the body is made small and light enough to be held by hand as a solution to the above problem, some body holding means is required. As a solution to this problem, when bending the work, hold the handle with one hand to operate the switch, and use the other hand to attach and fix the reinforcing bar to the receiving pin and the center pin.
Does the free end of the rebar, which turns while being bent up to 80 degrees, touch the worker? (7) How to stably and easily hold the main body in the bending work of the upward end and the lateral end of the already installed rebar. (8) It is necessary to return the output shaft, which is shared by the cam and bending pin, after it has rotated by a predetermined angle. However, in case of an unexpected situation such as a limit switch failure that determines the returning position, the rebar is
How to protect the body from being bent by 80 ° or more and becoming unusable, or the body being damaged.
【０００９】[0009]
【課題を解決するための手段】上記した課題を達成する
ための本発明の手段は、上記課題の順に次の通りであ
る。
（１）テコの利用によるカムローラの押し上げ力の低減
とカムや腕金の工夫による部品数低減
曲げピンをカムの側面の軸心から偏心した位置に一体に
形成し、腕金をカムと共用化する。この場合、曲げピン
は出力軸の軸受に対して片持ち構造になるが、カムを曲
げピンの位置に配置するには、更にカムローラの押し上
げ力を以下手法で軽減し、出力軸の軸受に加わる力を軽
減する必要がある。すなわち、前記カムの外周を転動す
るカムローラ及び鉄筋を切断する切断刃を両端に有する
と共に中間部に支軸を持つ揺腕を設け、揺腕のテコの作
用（テコ比Ｋｔ＝カムローラと支軸間の距離：支軸と切
断刃間の距離＝数倍）により、切断刃を強大な力で上下
に揺動させる切断機構部を設ける。揺腕のテコの作用で
カムローラを押し上げる力を数分の１に軽減し、片持ち
カムの軸受の負担を軽減できるばかりかカムの回転トル
クも低減できるので、本体を小型軽量化できる。
（２）鉄筋切断では、上下一対の切断刃が開いた状態か
ら、閉じて切断を開始するまではほとんど力が不要で、
切断の開始と共に荷重は徐々に増加し、切断が終わると
共に荷重は下がり、更に切り離しのために送り込んで切
断が完了する荷重特性がある。この特性を利用し、出力
軸の中心から外周までの距離が
ａ．急激に半径の増す早送り面
ｂ．なだらかに半径の増す切断面（圧力角８０度以上）
の少なくとも二つの大きく異なる曲面を有するほぼ扇形
状のカムを設け、可動切断刃が閉じるまでの空送りは早
送り面ａで早送りし、切断に入った後は荷重特性に合わ
せた形状のカムのなだらかに半径を増す切断面ｂでカム
ローラを押し上げる。切断面ｂではカムの回転方向には
小さい力しか発生しなくても、ゆるやかな傾斜面すなわ
ち切断面ｂのくさび作用で、圧力角の設定次第では半径
方向には約４〜６倍の大きな力を発生する倍力作用があ
る。そしてこの倍力率Ｋｃはカム曲線の曲率の取り方で
任意に設定できる。従って、より少ないカムの駆動トル
クで大きい押し上げ力を得られ、本体をより小型軽量化
できる。またこの力でカムローラを押し上げ、揺腕の支
軸に対するテコ比Ｋｔで切断刃には鉄筋の切断に十分な
強大な力を発生できる。カムの曲線の設定次第でこの時
のカムの回転方向の力を発生させるのに必要な駆動トル
クは、曲げピンで鉄筋を曲げる際の必要なトルクに近い
ものに比較的自由に設定できる。すなわち、切断と曲げ
に必要な出力軸の駆動トルクがほぼ近い値となるので、
電動機、減速ギヤ、外枠を共用化し、切断と曲げのいず
れかのために電動機やギヤを大きくすることなくバラン
スよく最小限の大きさで作れる。[Means for Solving the Problems] Means of the present invention for achieving the above-mentioned problems are as follows in the order of the above-mentioned problems. (1) Reducing the pushing force of the cam roller by using the lever and reducing the number of parts by devising the cam and the braces The bending pin is integrally formed at a position eccentric from the side axis of the cam, and the braces are shared with the cam. To do. In this case, the bending pin is a cantilever structure relative to the bearing of the output shaft, to be placed in the position of the pin bending cams are further reduced by methods below upward pushing force of the cam roller, the bearing of the output shaft It is necessary to reduce the applied force. That is, a rocking arm having a cam roller that rolls around the outer periphery of the cam and a cutting blade that cuts a reinforcing bar at both ends and a swing shaft having a spindle in the middle are provided, and the lever action of the swing arm (lever ratio Kt = cam roller and spindle) is provided. The distance between them: the distance between the spindle and the cutting blade = several times) provides a cutting mechanism that swings the cutting blade up and down with a powerful force. The force of pushing the cam roller by the lever action of the rocking arm is reduced to a fraction, which not only reduces the load on the bearing of the cantilevered cam but also reduces the rotational torque of the cam, so that the main body can be made smaller and lighter. (2) In rebar cutting, almost no force is required from the state in which the pair of upper and lower cutting blades is open to the start of cutting,
There is a load characteristic in which the load gradually increases with the start of cutting, the load decreases with the end of cutting, and further, the load is sent for separation and the cutting is completed. Using this characteristic, the distance from the center of the output shaft to the outer circumference is a. Rapid feed surface with sharply increasing radius b. Gently provided substantially fan-shaped cam having at least two very different curved cutting surface to increase the radius (or pressure angle 80 degrees), the air feed rehearsal early <br/> feeding surface a for closing the movable cutting blade After fast-forwarding with, and after cutting, the cam roller is pushed up by the cutting surface b where the radius of the cam is increased gently according to the load characteristics. In the cutting plane b, the direction of rotation of the cam
Yet small forces only without occurring, a wedge action of gently inclined surface or cutting surface b, there is a boosting action which generates a large force of about 4-6 times the radial direction depending on the setting of the pressure angle. The boosting factor Kc can be arbitrarily set by taking the curvature of the cam curve. Therefore, a large pushing force can be obtained with a smaller cam drive torque, and the main body can be made smaller and lighter. Further, the cam roller is pushed up by this force, and a powerful force sufficient for cutting the reinforcing bar can be generated in the cutting blade with the lever ratio Kt with respect to the supporting shaft of the rocking arm. Depending on the setting of the cam curve, the driving torque required to generate the force in the rotational direction of the cam at this time can be relatively freely set to a value close to the torque required to bend the reinforcing bar with the bending pin. In other words, the driving torque of the output shaft required for cutting and bending becomes almost the same value,
The electric motor, reduction gear, and outer frame are shared, and it is possible to make a balanced and minimum size without increasing the electric motor and gear for either cutting or bending.
【００１０】（３）無段変速化
従来の手動式の操作感覚に近づけるために、トリガの引
き加減で、電動機の回転数を低速から高速に調整可能な
スピードコントロールスイッチをメインスイッチとす
る。これによりトリガの引き加減で、強く引けば速く回
転し、軽く引くとゆっくり回転するので、曲げ角を目で
見ながら手加減で超低速でゆっくり回し、微妙に曲げ角
度をコントロールできる。(3) Continuously variable transmission In order to approximate the conventional manual operation feeling, the main switch is a speed control switch capable of adjusting the rotation speed of the electric motor from low speed to high speed by adjusting the trigger. This allows the trigger to be adjusted so that if you pull hard, it will rotate quickly, and if you pull lightly, it will rotate slowly, so you can control the bending angle subtly by slowly turning it at an extremely low speed while watching the bending angle.
【００１１】（４）ハンドル位置とスイッチ内蔵
電動機や減速部、切断曲げ機構部の総てを含む本体の重
心が垂下する位置の極力近くに片手で保持可能なハンド
ルを設け、ハンドル内（またはハンドルを握ったまま指
の届く範囲）に、電動機の起動、停止等の制御を行うス
イッチを配置する。これにより本体重心の真上で本体を
持ち支えることが可能になり、容易に移動できるばかり
か、本体を持ち上げたままハンドルを握った手でスイッ
チの操作が可能となり、切断個所あるいは曲げたい所に
本体を持ち上げてあてがいながら、現物合わせで手持ち
作業ができる。(4) A handle that can be held with one hand is provided as close as possible to the position of the handle and the position where the center of gravity of the main body including the electric motor with built-in switch, the speed reducer, and the cutting / bending mechanism is suspended as close as possible to the inside of the handle (or the handle). Within the reach of your finger while grasping, place a switch that controls the start and stop of the electric motor. This makes it possible to hold and support the main body just above the center of gravity of the body, and not only can it be moved easily, but also the switch can be operated with the hand holding the handle while lifting the main body, making it possible to cut or bend it. While lifting and applying the main body, you can hand-hold work by matching the actual thing.
【００１２】（５）２方向スタンド
切断と曲げの両用化に際して、切断刃の軸方向を水平に
した状態で本体を安定に地面に置けるスタンド（または
足またはそれに類する定置構造）と、曲げ機構部の曲げ
ピン、受けピン、中心ピンの３つのピンの成す平面が、
地面に水平に置かれた鉄筋と平行になるよう本体を安定
に地面におけるスタンドの、二つの方向で使えるスタン
ドとし、二つのスタンド方向が互いにほぼ直交する位置
関係に設ける。これにより、前者のスタンド部で本体を
地面に置いた場合、地面に平行に置かれた鉄筋を垂直に
立てることなくそのまま水平移動で切断刃にあてがって
切れる。また曲げる場合は、ハンドルを持って本体を９
０度立てかけるだけで、後者のスタンド部で本体を地面
に置いた場合、地面に平行に置かれた鉄筋を垂直に立て
ることなくそのまま水平移動でカバーの上に置いて曲げ
作業を行える。(5) Two-way stand For both cutting and bending, a stand (or foot or a stationary structure similar to that) which allows the main body to be stably placed on the ground with the axial direction of the cutting blade horizontal, and a bending mechanism section. The plane formed by the three pins of the bending pin, the receiving pin, and the center pin of
The main unit is a stand that can be used stably in two directions on the ground so that it is parallel to the reinforcing bars placed horizontally on the ground, and the two stand directions are arranged so that they are substantially orthogonal to each other. As a result, when the main body is placed on the ground by the former stand, the reinforcing bars placed parallel to the ground can be horizontally moved and applied to the cutting blade without vertical standing. When bending, hold the handle and pull the body
When the main body is placed on the ground with the latter stand, the bending work can be performed by placing it horizontally on the cover as it is without vertically standing the reinforcing bars placed parallel to the ground by simply leaning the body 0 degrees.
【００１３】（６）鉄筋の自由端が遠ざかる側にハンド
ルとスイッチを配置
受けピンと中心ピンからなる線上に固定された鉄筋に対
して、曲げられる鉄筋の自由端が遠ざかる側に、スイッ
チ及びスイッチを内蔵するハンドルとを配置する。そし
て作業者は本体に対してハンドルの側に立ち、左手でハ
ンドルを、右手で鉄筋の受けピン側を持って作業すれ
ば、曲げられた鉄筋の自由端側（中心ピンに対して旋回
運動する側）は作業者から遠ざかるので動いている鉄筋
の自由端に作業者が触れることはない。(6) A handle and a switch are arranged on the side where the free end of the reinforcing bar moves away. A switch and a switch are arranged on the side where the free end of the bendable reinforcing bar moves away from the reinforcing bar fixed on the line consisting of the receiving pin and the center pin. Place the built-in handle. If the worker stands on the side of the handle with respect to the main body and holds the handle with his left hand and the receiving pin side of the reinforcing bar with his right hand, the free end side of the bent reinforcing bar (moves with respect to the center pin) Since the side) moves away from the worker, the worker does not touch the free end of the moving rebar.
【００１４】（７）本体上部のハンドルの他に本体を挟
んで９０度から１８０度対称の位置に別のハンドルを平
行に設け、本体を重心を挟んで両手保持可能とし、本体
を様々な方向に向け手持ちで曲げ作業できるようにす
る。(7) In addition to the handle on the upper part of the main body, another handle is provided in parallel at a position symmetrical by 90 to 180 degrees with the main body sandwiched so that the main body can be held in both hands with the center of gravity sandwiched between them. To be able to bend by hand.
【００１５】（８）鉄筋の曲げは１８０度以下であるた
め、切断のモードにおける切断刃の最下死点の時の出力
軸回転角位置を、曲げの１８０度の位置よりも僅かに大
きい出力軸回転角位置とし、これ以上の回転角には出力
軸が回らないよう揺腕に突き当てストッパを設ければ良
い。(8) Since the bending of the reinforcing bar is 180 degrees or less, the output shaft rotation angle position at the bottom dead center of the cutting blade in the cutting mode is an output slightly larger than the position of 180 degrees of bending. The shaft rotation angle position may be set, and a stopper may be provided by abutting the swing arm so that the output shaft does not rotate at a rotation angle larger than this.
【００１６】[0016]
【発明の実施の形態】以下一実施形態を示した図面を参
照して本発明を説明する。
（全体配置）
図１において、直巻整流子電動機１が内蔵された樹脂製
のハウジング６から減速機構を内蔵したアルミ合金ダイ
カスト製のギヤカバー１４の上にかけては、持ち運びや
スイッチ操作に用いる樹脂製のハンドル４６が電動機１
の軸と略平行に配置されている。ハンドル４６は中空の
２つ割り構造で、中にメインスイッチ４１やリレー６
２、タイマ回路６３等が収納され、本体をハンドル４６
で支えながら、メインスイッチ４１のトリガ操作が可能
である。電源コード４８はハウジング６のギヤカバー１
４とは反対側の端部に出ているため、切断作業や曲げ作
業時に邪魔になることはない。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings showing one embodiment. (Overall Arrangement) In FIG. 1, from the resin housing 6 having the series-wound commutator motor 1 built-in to the aluminum alloy die-cast gear cover 14 having the speed reducing mechanism built-in, a resin-made housing used for carrying and switch operation is used. The handle 46 is the electric motor 1
Are arranged substantially parallel to the axis of. The handle 46 has a hollow structure that divides the main switch 41 and relay 6 inside.
2, the timer circuit 63 and the like are stored, and the main body is handled by the handle 46.
The main switch 41 can be operated while being supported by. The power cord 48 is the gear cover 1 of the housing 6.
Since it projects at the end opposite to 4, it does not interfere with cutting or bending work.
【００１７】（電源回路とスイッチ及び戻り制御部）
図１２は本発明切断曲げ工具の回路図である。電源コー
ド４８からはＡＣ１００Ｖの商用電源が供給される。電
源は常閉接点のリレー６２、メインスイッチ（スピード
コントロールスイッチ）４１を介して電動機１へ電流を
供給する。ソレノイドコイル３７は電動機１と並列に接
続され、メインスイッチ４１の操作に連動してオン・オ
フする。電動機１は、トリガの引き具合によって、トラ
イアック等で位相制御されて供給電力量を変える位相制
御端子４１ａに接続され、ソレノイドコイル３７は、ト
リガの引き具合に関係なく電源電圧のまま直接出力する
出力端子４１ｂに接続される。リレー６２のオン・オフ
はリミットスイッチ３４とタイマ回路６３によって行わ
れる。この回路は、通常リミットスイッチ３４がオフ状
態でリレー６２は導通し、リミットスイッチ３４がオン
になるとタイマ回路６３によって設定される３〜５秒リ
レー６２を遮断状態に保ち、この間メインスイッチ４１
のトリガが引かれても電動機１及びソレノイドコイル３
７を電源から遮断する機能を有する。(Power Supply Circuit, Switch and Return Control Section) FIG. 12 is a circuit diagram of the cutting and bending tool of the present invention. The power cord 48 supplies commercial power of AC100V. The power supply supplies a current to the electric motor 1 via a relay 62 having a normally closed contact and a main switch (speed control switch) 41. The solenoid coil 37 is connected in parallel with the electric motor 1 and is turned on / off in conjunction with the operation of the main switch 41. The electric motor 1 is connected to a phase control terminal 41a that is controlled in phase by a triac or the like to change the amount of supplied electric power depending on the pulling condition of the trigger, and the solenoid coil 37 outputs directly as the power supply voltage regardless of the pulling condition of the trigger. It is connected to the terminal 41b. The relay 62 is turned on and off by the limit switch 34 and the timer circuit 63. This circuit normally keeps the relay 62 conductive when the limit switch 34 is off, and keeps the relay 62 cut off for 3 to 5 seconds set by the timer circuit 63 when the limit switch 34 is turned on.
Even if the trigger is pulled, the electric motor 1 and the solenoid coil 3
7 has a function of cutting off the power supply.
【００１８】（動力部）
ハウジング６内の電動機１は、界磁２、界磁２の内側に
位置する電機子３、ブラシ４、整流子５等から構成さ
れ、毎分２００００回転の高速で回転する。(Power Unit) The electric motor 1 in the housing 6 is composed of a field 2, an armature 3 located inside the field 2, a brush 4, a commutator 5, etc., and rotates at a high speed of 20000 revolutions per minute. To do.
【００１９】（減速機構部）
電機子３の先端には軸と一体に第１ピニオン７が設けら
れ、第１ギヤ８とで約１／１３に減速する。同様に次の
第２ピニオン９、第２ギヤ１０で約１／１０に、第３ピ
ニオン１１とファイナルギヤ１２で１／８に減速し、最
終的に３段の歯車列で約１／１０００に減速し、出力軸
１３を無負荷全速で毎分約２０回転の低速で回転する。
これら歯車列はギヤカバー１４内に収納されている。な
お平歯車列を用いるとしたが、ハスバ歯車、傘歯車、遊
星歯車等他の歯車を用いてもよい。(Deceleration Mechanism Section) A first pinion 7 is provided at the tip of the armature 3 integrally with the shaft, and the speed is reduced to about 1/13 with the first gear 8. Similarly, the following second pinion 9 and second gear 10 reduce the speed to about 1/10, and the third pinion 11 and final gear 12 reduce the speed to 1/8. Finally, the three-stage gear train reduces the speed to about 1/1000. The output shaft 13 is decelerated, and the output shaft 13 is rotated at a full speed of no load at a low speed of about 20 rpm.
These gear trains are housed in the gear cover 14. Although the spur gear train is used, other gears such as a helical gear, a bevel gear, and a planetary gear may be used.
【００２０】（先端機構部）
ハウジング６の先端にはギヤカバー１４がねじ止め（図
示せず）されている。ギヤカバー１４も２つ割り構造
で、中に前記３段の平歯車列７〜１２を内蔵しボルト
（図示せず）で締め付けられている。ギヤカバー１４の
外側（図１中左側）に固定部材１９が固定され、固定部
材１９の図１中左側に揺腕２１が支軸２０を介して回動
可能に固定されている。固定部材１９から図１中左側に
突出した出力軸１３にはカム１８が一体に設けられてい
る。カム１８、揺腕２１、固定部材１９等からなる切断
機構部の更に先端側（図１中左側）には、カバー４９と
回転カバー５０を隔てて、外部（図１中左側）に突出す
る形で、カム１８の最大半径付近１８ｄから出た曲げピ
ン１６、出力軸１３から延びた出力軸１３と一体の中心
ピン２７、固定部材１９から出た受けピン３５が設けら
れる。すなわち歯車列７〜１２の左側に固定部材１９、
固定部材１９の左側にカム１８と揺腕２１、更にその左
側に回転カバー５０、カバー４９を介して曲げピン１
６、受けピン３５、中心ピン２７が並ぶ４層構造となっ
ている。(Tip Mechanism) A gear cover 14 is screwed (not shown) to the tip of the housing 6. The gear cover 14 is also divided into two parts, and the three-stage spur gear trains 7 to 12 are built therein and fastened with bolts (not shown). A fixing member 19 is fixed to the outside (left side in FIG. 1) of the gear cover 14, and a swing arm 21 is rotatably fixed to the left side in FIG. 1 of the fixing member 19 via a support shaft 20. A cam 18 is integrally provided on the output shaft 13 protruding from the fixing member 19 to the left side in FIG. On the further tip side (left side in FIG. 1) of the cutting mechanism portion including the cam 18, the swinging arm 21, the fixing member 19 and the like, the cover 49 and the rotary cover 50 are separated from each other and protruded to the outside (left side in FIG. 1). There are provided a bending pin 16 extending from the vicinity 18d of the maximum radius of the cam 18, a center pin 27 extending from the output shaft 13 and integral with the output shaft 13, and a receiving pin 35 extending from the fixing member 19. That is, on the left side of the gear trains 7 to 12, the fixing member 19,
The cam 18 and the swing arm 21 are provided on the left side of the fixing member 19, and the bending pin 1 is provided on the left side of the fixing member 19 via the rotary cover 50 and the cover 49.
6, a receiving pin 35, and a center pin 27 are arranged in a four-layer structure.
【００２１】ハウジング６の下部から後部にはＬ字形に
略９０度に曲がったスタンド（ボトムスタンド５１とテ
ールスタンド５２が一体化）がギヤカバー１４とハウジ
ング６にねじ止め（図示せず）されている。本体を図１
のように側面から見た場合、ハウジング６とギヤカバー
１４を中心に、左側に切断及び曲げの機構部、下側にボ
トムスタンド５１及び右側にテールスタンド５２、上面
にハンドル４６が配置され、図２のように正面から見た
場合に、下辺に本体を支えるボトムスタンド５１があ
り、中央の出力軸１３の中心ピン２７を取り巻く形で下
側に半円状に曲げピン１６の動く範囲とこれの逃げ穴と
してカバー４９には円弧長穴４９ａがあり、右上側サイ
ドに固定切断刃２４ｂがギヤカバー１４から突出して配
置されている。カム１８や揺腕２１の配置を本実施形態
とは上下を軸にして鏡像のように反転し、固定切断刃２
４ｂが左上側サイドに突出するようにしてもよい。ハン
ドル４６に対して重心を挟んで反対側にあるボトムスタ
ンド５１は２本の棒状をしており、グリップ４７が設け
られているので（図１参照）、本体保持のために使え
る。なおスタンド５１は本実施形態のように鉄棒で作っ
ても良いし、鉄板を曲げて作ってもあるいはハウジング
６またはギヤカバー１４と一体に樹脂またはアルミダイ
カストで成形して作っても、足だけ出しても、水平また
は垂直に本体を置くことができれば効果は同様であリ、
その形態は問わない。From the lower part of the housing 6 to the rear part, an L-shaped stand (bottom stand 51 and tail stand 52 are integrated) is screwed (not shown) to the gear cover 14 and the housing 6. . Figure 1
When viewed from the side, the cutting and bending mechanism is located on the left side, the bottom stand 51 is located on the lower side, the tail stand 52 is located on the right side, and the handle 46 is located on the upper side, with the housing 6 and the gear cover 14 as the center. There is a bottom stand 51 for supporting the main body on the lower side when viewed from the front like, and the range of movement of the bending pin 16 in the shape of a semicircle downward around the center pin 27 of the central output shaft 13 and The cover 49 has an arcuate elongated hole 49a as an escape hole, and a fixed cutting blade 24b is arranged on the upper right side so as to project from the gear cover 14. The present embodiment <br/> the arrangement of the cam 18 and Yuraude 21 reversed like a mirror image by the vertical to the axis, the fixed cutting blade 2
4b may be projected to the upper left side. The bottom stand 51 on the opposite side of the handle 46 across the center of gravity is in the shape of two rods and is provided with a grip 47 (see FIG. 1), which can be used for holding the main body. The stand 51 may be made of an iron rod as in the present embodiment, may be made by bending an iron plate, or may be made integrally with the housing 6 or the gear cover 14 by resin or aluminum die casting, and only the legs should be exposed. Also, if the main body can be placed horizontally or vertically, the effect will be the same,
The form does not matter.
【００２２】（切断機構部）
図１において、出力軸１３には右側から軸受６５が圧入
され、ファイナルギヤ１２はキー１７で回り止めされ、
カム１８が上記した如く出力軸１３に一体に設けられて
いる。カム１８の外形は図３に示すように、中心から急
激に半径の増す早送り面１８ａ、ゆっくりと半径の増す
切断面１８ｂ、１８ａと１８ｄを結ぶ戻り面１８ｃの３
つの面から構成されたほぼ扇形状をしている。出力軸１
３のファイナルギヤ１２とカム１８の間の軸部は固定部
材１９のボス部１９ａに回転可能に嵌合され、固定部材
１９はギヤカバー１４にボルト（図示せず）で固定さ
れ、出力軸１３はボス部１９ａと軸受６５で両持ち支持
されている。図３において、固定部材１９の上方には支
軸２０によって回転可能に嵌合された揺腕２１がある。
揺腕２１の一端にはカムローラ２２がニードル２３で回
転可能に固定されている。揺腕２１の他端には鉄筋を切
断する可動切断刃２４ａが止めねじ２５で固定されてい
る。可動切断刃２４ａに対向する固定部材１９にも固定
切断刃２４ｂが止めねじ２５で固定されている。切断刃
２４の刃部２４ｃは平面ではなく、切断する鉄筋よりも
径の大きな半円に近い円弧状とされている。(Cutting mechanism section) In FIG. 1, a bearing 65 is press-fitted into the output shaft 13 from the right side, and the final gear 12 is stopped by a key 17 from rotating.
The cam 18 is provided integrally with the output shaft 13 as described above. As shown in FIG. 3, the external shape of the cam 18 is a rapid feed surface 18a whose radius increases rapidly from the center, a cutting surface 18b whose radius increases slowly, and a return surface 18c which connects 18a and 18d.
It is almost fan-shaped and consists of two surfaces. Output shaft 1
The shaft portion between the final gear 12 and the cam 18 of 3 is rotatably fitted to the boss portion 19a of the fixing member 19, the fixing member 19 is fixed to the gear cover 14 with a bolt (not shown), and the output shaft 13 is Both ends are supported by the boss portion 19a and the bearing 65. In FIG. 3, a swing arm 21 rotatably fitted by a support shaft 20 is provided above the fixing member 19 .
At one end of the rocking arm 21 the cam roller 22 is rotatably secured in the needle 23. A movable cutting blade 24 a for cutting the reinforcing bar is fixed to the other end of the rocking arm 21 with a set screw 25. The fixed cutting blade 24b is also fixed to the fixing member 19 facing the movable cutting blade 24a with a set screw 25. The blade portion 24c of the cutting blade 24 is not flat, but has an arc shape closer to a semicircle having a larger diameter than the reinforcing bar to be cut.
【００２３】（曲げ機構部）
図１において、カム１８の最大半径部付近１８ｄにはカ
ム１８の転動面よりも幅広のボス部が設けてあり、ボス
部に穴を設け、直径１５ｍｍ、長さ４０ｍｍ程度の曲げ
ピン１６が圧入固定されている（曲げピン１６を圧入と
したのは、カム１８を切削加工する際に偏心した位置に
棒状のピンを一体で削るのは工数がかかって単価が大幅
にアップするためであり、強度を優先するならば一体で
も良い。またボス部を肉厚としたのは曲げピン１６に加
わる曲げモーメントに穴の強度が耐えられるようにする
ためである）。曲げピン１６には曲げローラ６６が回転
可能に嵌合され、止めワッシャ６７で抜け止めされてい
る。出力軸１３の軸心上にはカム１８よりも外側に突出
した中心ピン２７が一体に形成されている（中心ピン２
７の直径は本実施形態では２６ｍｍであるが、これは１
３ｍｍの鉄筋の内曲げＲがこの程度であれば良いためで
あり、設定する曲げのＲによって変わる）。固定部材１
９のボス１９ａから上方８０ｍｍ程離れた位置に穴が設
けられ、直径１５ｍｍ、長さ６０ｍｍ程度の受けピン３
５が圧入固定され（受けピン３５を圧入としたのは、固
定部材１９を切削加工する際に偏心した位置に棒状のピ
ンを一体で削るのは工数がかかって単価が大幅にアップ
するためであり、強度を優先するならば一体でも良
い）、外周に受けローラ３６が回転可能に止めワッシャ
６８で固定されている。曲げローラ６６や受けローラ３
６は単なる円筒状ではなく、中央が凹んだ鼓状の形状と
されている（図２２参照）。受けピン３５をギヤカバー
１４ではなく鋼材製の固定部材１９に圧入するとしたの
は、受けピン３５に加わる曲げモーメントを固定部材１
９で受けることで穴の強度を容易に確保するためであ
り、これによりギヤカバー１４を肉厚としたり、補強の
リブを設ける必要がなく大型化せずにすむ。なお支軸２
０をカバー及び回転カバー５０の外側まで延ばし、受け
ピン３０の代わりとすることも可能である。(Bending mechanism portion) In FIG. 1, a boss portion wider than the rolling surface of the cam 18 is provided near the maximum radius portion 18d of the cam 18, a hole is provided in the boss portion, and the diameter is 15 mm and the length is long. A bending pin 16 of about 40 mm is press-fitted and fixed. (The bending pin 16 is press-fitted because it takes a lot of time to cut a rod-shaped pin integrally at an eccentric position when cutting the cam 18 because it takes a lot of time. If the strength is prioritized, they may be integrated, and the boss portion is made thick so that the strength of the hole can withstand the bending moment applied to the bending pin 16.) . A bending roller 66 is rotatably fitted to the bending pin 16 and is prevented from coming off by a stop washer 67. A center pin 27 is integrally formed on the shaft center of the output shaft 13 so as to project to the outside of the cam 18 (center pin 2
7 the diameter of which is 26mm in this embodiment, but this is 1
This is because the internal bending R of the 3 mm reinforcing bar should be within this range, and it depends on the bending R to be set). Fixed member 1
9. A receiving pin 3 having a diameter of 15 mm and a length of about 60 mm is provided with a hole at a position 80 mm upward from the boss 19a of FIG.
5 is press-fitted and fixed. (The reason why the receiving pin 35 is press-fitted is that when the fixing member 19 is cut, the bar-shaped pin is integrally shaved at an eccentric position because it takes a lot of man-hours and the unit price is significantly increased. However, if strength is prioritized, they may be integrated together), but the receiving roller 36 is rotatably fixed to the outer periphery by a stop washer 68. Bending roller 66 and receiving roller 3
Reference numeral 6 is not a simple cylindrical shape, but is a drum shape with a concave center (see FIG. 22). The reason why the receiving pin 35 is press-fitted into the fixing member 19 made of steel instead of the gear cover 14 is that the bending moment applied to the receiving pin 35 is fixed to the fixing member 1.
This is for the purpose of easily securing the strength of the hole by receiving it by means of 9, so that it is not necessary to make the gear cover 14 thick and to provide reinforcing ribs, and it is not necessary to increase the size. In addition, spindle 2
It is also possible to extend 0 to the outside of the cover and the rotary cover 50 and replace the receiving pin 30.
【００２４】（曲げ角度調整機構部）
中心ピン２７の端面にはダイヤル２８が回転可能に保持
され、ダイヤル２８の側面の凹凸３０は約１１．２５度
毎に設けられ、ボール３１と押しバネ３２により回転方
向に節度を出している。図１７において、ダイヤル２８
から出力軸１３を貫通して延びるロッド３１ａの後端に
は半径方向に突出した凸部３３を有するアクチュエータ
が装着され、出力軸１３がダイヤル２８によって設定さ
れた角度回転した時、凸部３３がギヤカバー１４の底に
設けられたリミットスイッチ３４をオンするようになっ
ている。ダイヤル２８の左側面には曲げ角度０度〜１８
０度までと切断を示す目盛が設けられ（図２参照）、目
盛にならってダイアル２８をセットすることで、欲しい
曲げ角度（０〜１８０度）の設定及び切断のモード（曲
げ角度の１８０度から更に１０度程進み、揺腕２１が上
がりきり、可動切断刃２４ａが最下死点に達する位置で
あり、これを切断のモードという）に任意に設定できる
（カム１８は図９の初期位置から５０度程右回りした位
置から曲げを開始し、この開始位置をダイヤル２８の０
度としてあり、更に１８０度進んだ２３０度の位置が曲
げの１８０度、更に１０度程進んだ２４０度の位置を切
断の位置としている）。(Bending Angle Adjusting Mechanism) A dial 28 is rotatably held on the end face of the center pin 27, and unevenness 30 on the side surface of the dial 28 is provided about every 11.25 degrees, and a ball 31 and a pressing spring 32 are provided. It has a moderation in the direction of rotation. In FIG. 17, the dial 28
An actuator having a convex portion 33 protruding in the radial direction is attached to the rear end of a rod 31a extending from the output shaft 13 to the convex portion 33 when the output shaft 13 is rotated by an angle set by a dial 28. A limit switch 34 provided on the bottom of the gear cover 14 is turned on. Bend angle 0 to 18 on the left side of dial 28
There is a scale indicating cutting up to 0 degrees (see Fig. 2), and by setting the dial 28 according to the scale, setting of the desired bending angle (0 to 180 degrees) and cutting mode (180 degrees of bending angle) From the position where the movable arm 21 reaches the bottom dead center by moving the oscillating arm 21 all the way further, and this can be arbitrarily set to the cutting mode (the cam 18 is at the initial position in FIG. 9). Start bending from a position that is rotated clockwise about 50 degrees from this position, and set this starting position to 0 on the dial 28.
The position is 230 °, which is further 180 °, and the position of 240 °, which is further 10 °, is the cutting position.
【００２５】図１６において、第１ギヤ８は第２ピニオ
ン９に回転可能に嵌合し、第１ギヤ８のボス部８ａと第
２ピニオン９の軸部９ａの外周をまたぐ形でスプリング
クラッチ１５が締め代の無い状態で巻き付いている。ス
プリングクラッチ１５の一端には、スプリングの巻き終
りの端部を外周方向に８ｍｍ程度突出させた係止部１５
ａがある。スプリングクラッチ１５は左巻きにピアノ線
を巻いたもので、スリーブ６４がソレノイドコイル３７
によって第１ギヤ８側に押し込まれた際に、スリーブ６
４の溝６４ａに係止部１５ａが噛み合うと、第１ギヤ８
が第２ピニオン９を左巻きに回そうとした際に、スプリ
ングクラッチ１５が締り勝手になり、第１ギヤ８と第２
ピニオン９は一体に回る。カム１８に設けられた曲げピ
ン１６が規定の角度に達した時、出力軸１３とはバネ３
２及びボール３１の力で一体に回るダイヤル２８に連動
した凸部３３がリミットスイッチ３４を押し、リミット
スイッチ３４がオン状態になり、これに連動してリレー
６２がタイマ回路６３で３〜５秒間オフ状態になる。こ
れによりソレノイドコイル３７がオフ状態になるとプラ
ンジャ３７ａは後退し、スプリング３８によりスリーブ
６４は第１ギヤ８のボス部８ａから離れる。この場合、
電動機１もオフ状態になるが慣性でまだ回っていて第１
ギヤ８が回転していても、スプリングクラッチ１５が瞬
時にゆるみ、軸部９ａから浮いた状態に戻るため、第２
ピニオン９に回転が伝わらず出力軸１３は回転を停止す
る。なおスプリングクラッチ１５を用いたクラッチを例
にあげたが、これ以外の例えば爪クラッチやボールクラ
ッチ、摩擦板クラッチ、電磁パウダークラッチ等を電気
信号でオン・オフし係脱可能なクラッチとしてもよい。In FIG. 16, the first gear 8 is rotatably fitted to the second pinion 9, and the spring clutch 15 straddles the outer periphery of the boss portion 8a of the first gear 8 and the shaft portion 9a of the second pinion 9. Is wrapped around with no tightening margin. At one end of the spring clutch 15, a locking portion 15 in which the end of the winding end of the spring is projected about 8 mm in the outer peripheral direction
There is a. The spring clutch 15 is a left-hand winding piano wire, and the sleeve 64 has a solenoid coil 37.
When pushed into the first gear 8 side by the sleeve 6
When the engaging portion 15a meshes with the groove 64a of No. 4, the first gear 8
Tries to turn the second pinion 9 counterclockwise, the spring clutch 15 becomes self-locking, and the first gear 8 and the second gear
The pinion 9 turns together. When the bending pin 16 provided on the cam 18 reaches a specified angle, the output shaft 13 and the spring 3
The convex portion 33 that is interlocked with the dial 28 that rotates integrally with the ball 2 and the ball 31 presses the limit switch 34, and the limit switch 34 is turned on. In conjunction with this, the relay 62 causes the timer circuit 63 to operate for 3 to 5 seconds. Turns off. As a result, when the solenoid coil 37 is turned off, the plunger 37a retracts, and the spring 38 separates the sleeve 64 from the boss portion 8a of the first gear 8. in this case,
The electric motor 1 is also turned off, but it is still spinning due to inertia
Even when the gear 8 is rotating, the spring clutch 15 instantly loosens and returns to the state of floating from the shaft portion 9a.
The rotation is not transmitted to the pinion 9, and the output shaft 13 stops rotating. Although the clutch using the spring clutch 15 has been described as an example, other clutches such as a claw clutch, a ball clutch, a friction plate clutch, an electromagnetic powder clutch, etc. may be used as an engageable / disengageable clutch by turning on / off by an electric signal.
【００２６】（戻り機構）
ファイナルギヤ１２の左側の凹部１２ａには、ねじりコ
イルバネ６０が設けられ、常にカム１８を電動機１から
の駆動方向とは逆方向に復元力で付勢している。ファイ
ナルギヤ１２の凹部１２ａ内にねじりコイルバネ６０を
内蔵することでファイナルギヤ１２の軽量化及び工具本
体の軸方向長さの短縮を図れる。(Return Mechanism) A torsion coil spring 60 is provided in the recess 12a on the left side of the final gear 12, and constantly biases the cam 18 in the direction opposite to the driving direction from the electric motor 1 with a restoring force. By incorporating the torsion coil spring 60 in the recess 12a of the final gear 12, it is possible to reduce the weight of the final gear 12 and the axial length of the tool body.
【００２７】次に本発明切断曲げ工具の動作について、
切断と曲げの夫々について説明する。
（切断作業）
５ｍ程の長尺の地面に横たわった鉄筋６９を切断する場
合が多く、地面に平行な鉄筋６９を固定切断刃２４ｂに
あてがい易くするため、図１３のように、ボトムスタン
ド５１が地面に接する状態に本体を置く。これにより、
出力軸１３や切断刃２４の刃部２４ｃの軸心を地面に水
平に置ける。次に、右手でハンドル４６を握ってスイッ
チ４１を操作し、左手で鉄筋６９を支えながら開口した
固定切断刃２４ｂの刃部２４ｃにあてがえば（図６参
照）、鉄筋６９は地面に対して水平のまま容易に切断作
業の態勢に入れる。この時ダイヤル２８は切断位置にセ
ットされているものとする。切断位置とは、カム１８が
右回りに最も大きく回転しカムローラ２２がカム１８の
最大半径部１８ｄの近くまで接した状態すなわち揺腕２
１が最も持ち上げられ可動切断刃２４ａが最下死点に達
する状態である（図８参照）。Next, regarding the operation of the cutting and bending tool of the present invention,
Each of cutting and bending will be described. (Cutting work) In many cases, the reinforcing bar 69 lying on the ground having a length of about 5 m is cut, and in order to easily apply the reinforcing bar 69 parallel to the ground to the fixed cutting blade 24b, as shown in FIG. Put the main body in contact with the ground. This allows
The shaft center of the output shaft 13 and the blade portion 24c of the cutting blade 24 can be placed horizontally on the ground. Next, if the handle 46 is grasped with the right hand and the switch 41 is operated, and the reed bar 69 is applied to the blade portion 24c of the fixed cutting blade 24b opened while supporting the rebar 69 with the left hand (see FIG. 6), the rebar 69 is against the ground. Ready for cutting work while it is horizontal. At this time, the dial 28 is assumed to be set to the cutting position. The cutting position is a state in which the cam 18 rotates the most clockwise and the cam roller 22 is in contact with the cam 18 near the maximum radius portion 18d, that is, the swing arm 2.
1 is the most raised and the movable cutting blade 24a reaches the bottom dead center (see FIG. 8).
【００２８】次にメインスイッチ４１のトリガを引く
と、カムローラ２２はカム１８の半径Ｒの急激に増す早
送り面１８ａで急激に押し上げられ、可動切断刃２４ａ
は鉄筋６９が挿入可能に開いた状態から閉じて切り始め
る位置まで早送りされる（図６参照・半径Ｒとはカム１
８の回転中心から接点Ｐまでの距離をいう）。早送り面
１８ａは、カム１８の中心から見た角度で約２０度の範
囲で半径が１０ｍｍから３５ｍｍに約２５ｍｍも増す略
直線に近い曲率の急斜面である。早送り面１８ａで可動
切断刃２４ａはほとんど無負荷状態で約０．２秒の短い
時間で閉じて次の切断行程に移れる。これは従来の油圧
式が大量の油をシリンダに送り込み長いストロークを移
動するのに要した時間に比べて著しく短くなる。Next, when the trigger of the main switch 41 is pulled, the cam roller 22 is suddenly pushed up by the rapid feed surface 18a of the radius R of the cam 18 which is rapidly increased, and the movable cutting blade 24a.
Is fast-forwarded from the open state where the reinforcing bar 69 can be inserted to the position where it starts closing and cutting (see FIG. 6; radius R is cam 1
8 is the distance from the center of rotation to the contact point P). The fast-forwarding surface 18a is a steep slope having a curvature close to a substantially straight line with the radius increasing from 10 mm to 35 mm by about 25 mm within a range of about 20 degrees when viewed from the center of the cam 18. On the rapid feed surface 18a, the movable cutting blade 24a closes in a short time of about 0.2 seconds and moves to the next cutting process with almost no load. Which is significantly shorter than the time required hydraulic large amount of oil traditional to move the long stroke fed into the cylinder.
【００２９】次にカムローラ２２はカム１８の半径Ｒの
なだらかに増す切断面１８ｂに入り切断を開始する。切
断面１８ｂは、カム１８の中心から見た角度で約１５０
度の範囲で半径Ｒが３５ｍｍから５５ｍｍに約２０ｍｍ
しか増さない複数の曲率の異なる円弧面で形成されたゆ
るやかな斜面である。出力軸１３に作用するトルクをＴ
cとすれば、これによりカム１８とカムローラ２２の接
点Ｐの円周方向に作用する力Ｆｂは、Ｆｂ＝Ｔc／（接
点Ｐの半径Ｒ）となり、カムローラ２２を半径方向に押
し上げる力Ｆｄは、カム１８の前記ゆるやかな斜面のく
さび作用でＦｂの５〜６倍の大きな値となる。これをカ
ム１８の倍力作用という。Next, the cam roller 22 enters the cutting surface 18b of the radius R of the cam 18 which gradually increases and starts cutting. The cutting surface 18b has an angle of about 150 when viewed from the center of the cam 18.
20mm radius R from 35mm to 55mm in the range of degrees
It is a gentle slope formed by a plurality of arcuate surfaces having different curvatures that increase. The torque acting on the output shaft 13 is T
Assuming c, the force Fb acting on the contact point P between the cam 18 and the cam roller 22 in the circumferential direction is Fb = Tc / (radius R of the contact point P), and the force Fd pushing up the cam roller 22 in the radial direction is Due to the wedge action of the gentle slope of the cam 18, the value becomes 5 to 6 times larger than Fb. This is called a boosting action of the cam 18.
【００３０】ＦｂとＦｄの関係は一般に次式で表せ、こ
れをカム１８の倍力率Ｋｃという（図１９参照）。The relationship between Fb and Fd is generally expressed by the following equation, which is called the power factor Kc of the cam 18 (see FIG. 19).
【００３１】Ｋｃ＝Ｆｄ／Ｆｂ＝ｃｏｓ（Ｘ＋ｔａｎ
−１Ｕ）／ｃｏｓ（Ｙ−ｔａｎ−１Ｕ）
ここで、Ｘ：揺腕２１の圧力角、Ｙ：カム１８の圧力
角、Ｕ：カムローラ２２の摩擦係数である。上式は支軸
２０や出力軸１３の摩擦係数の影響を省略した簡略式で
あるが傾向は厳密式と同等である。本実施形態ではＸ＝
５度、Ｙ＝８３度程度に設定してあり、この場合、倍力
率Ｋｃは６前後の値になる。Kc = Fd / Fb = cos (X + tan
−1 U) / cos (Y-tan −1 U) where X is the pressure angle of the rocking arm 21, Y is the pressure angle of the cam 18, and U is the friction coefficient of the cam roller 22. The above formula is a simplified formula in which the influence of the friction coefficient of the support shaft 20 and the output shaft 13 is omitted, but the tendency is the same as the strict formula. In this embodiment , X =
It is set to about 5 degrees and Y = 83 degrees, and in this case, the power factor Kc becomes a value of around 6.
【００３２】鉄筋６９の切断荷重Ｆcと可動切断刃２４
ａのストロークδの関係は図２０のように変化する。そ
こで、切り始めの荷重の立ち上がりはＹをやや小さくし
てＫｃを小さめに設定すると共に、荷重のピークでＹを
最も大きくしてＫｃを最大にし、切り終りの荷重の下が
った点ではＹをやや小さめにしてＫｃも小さく設定す
る。これは、ストローク位置で変化する切断荷重Ｆcと
これに比例する押し上げ力Ｆｄの値に対して、限られた
カム１８の半径Ｒの中で必要な所でより大きなＫｃの値
をとり、出力軸１３の力ＦｂやトルクＴｃの変化を極力
小さくする工夫であり、これによって駆動トルクＴｃの
ピーク値を下げ、小形の電動機１やギヤで効率良く駆動
できる。このため、カム１８の切断面１８ｂは、同じゆ
るやかに半径Ｒの変化する面でも、場所によりカム１８
の圧力角Ｙを変化させるよう曲率の異なる円弧の組み合
わせで構成されている。Cutting load Fc of the reinforcing bar 69 and the movable cutting blade 24
The relationship of the stroke δ of a changes as shown in FIG. Therefore, at the start of the load at the start of cutting, Y is set to be slightly smaller and Kc is set to be smaller , Y is maximized at the peak of the load to maximize Kc, and Y is set at the point where the load at the end of cutting is lowered. Set a little smaller Kc. This takes a larger value of Kc at a necessary place within the limited radius R of the cam 18 with respect to the value of the cutting load Fc which changes at the stroke position and the pushing force Fd proportional thereto, and the output shaft has a larger value. This is a device for minimizing changes in the force Fb and the torque Tc of No. 13 by which the peak value of the drive torque Tc can be reduced and the small electric motor 1 and gears can efficiently drive. For this reason, the cut surface 18b of the cam 18, also at varying plane of the same gentle radius R, the cam by location 18
It is composed of a union <br/> Align the different that the circle arc of curvature so as to vary the pressure angle Y of.
【００３３】カムローラ２２を押し上げる力Ｆｄに対し
て、支軸２０を介して可動切断刃２４ａに作用する力Ｆ
c（これが切断力）は、カムローラ２２と支軸２０間の
距離Ｌｒ、支軸２０と可動切断刃２４ａ間の距離Ｌｓの
比で決まるテコ比で倍力され、これをテコの倍力率Ｋｔ
という。The force F acting on the movable cutting blade 24a via the support shaft 20 against the force Fd pushing up the cam roller 22.
c (this is the cutting force) is boosted by a lever ratio determined by the ratio of the distance Lr between the cam roller 22 and the support shaft 20 and the distance Ls between the support shaft 20 and the movable cutting blade 24a.
Say.
【００３４】本実施形態では
Ｋｔ＝Ｌｒ／Ｌｓ＝６０ｍｍ／３０ｍｍ＝２
従って、例えば直径１３ｍｍの鉄筋６９を切断する場合
鉄筋切断力 Ｆｃ＝５６０００Ｎ
カム１８の押し上げ力 Ｆｄ＝Ｆｃ／Ｋｔ＝５６０００
／２＝２８０００Ｎ
カム１８の回転力 Ｆｂ＝Ｆｄ／Ｋｃ＝２８０００
／６≒ ４６６０Ｎ
となり、カム１８を回す力は切る力の１／１２になるこ
とが分かる。すなわちカム１８とテコの倍力作用で、１
２倍の切断力が発生できる。この時の出力軸１３のトル
クはカム１８の接触位置の半径を４０ｍｍとして約１８
６Ｎｍである。従って鉄筋６９は出力軸１３の１８６Ｎ
ｍのトルクがカム１８とテコの倍力作用で５６０００Ｎ
ｍに増力され切断される。In this embodiment , Kt = Lr / Ls = 60 mm / 30 mm = 2 Therefore, for example, when cutting the reinforcing bar 69 having a diameter of 13 mm, the reinforcing bar cutting force Fc = 56000N the pushing force of the cam 18 Fd = Fc / Kt = 56000
/ 2 = 28000N Rotational force of the cam 18 Fb = Fd / Kc = 28000
/ 6≈4660N, and it can be seen that the turning force of the cam 18 is 1/12 of the cutting force. That is, the boosting action of the cam 18 and the lever 1
Double the cutting force can be generated. At this time, the torque of the output shaft 13 is about 18 when the radius of the contact position of the cam 18 is 40 mm.
It is 6 Nm. Therefore, the reinforcing bar 69 is 186N of the output shaft 13.
The torque of m is 56000N due to the boosting action of the cam 18 and lever.
m is increased and cut.
【００３５】図３に示すように、切断刃刃部２４ｃは鉄
筋６９の外径よりも径の大きい半円の円弧状をしている
が、これは、揺腕２１が支軸２０を中心に揺動運動する
際に、これが平行運動ではなく円弧運動するために、鉄
筋６９には支軸２０から離れる方向に力が作用する性質
があり、これに抗して鉄筋６９が逃げないよう滑り防止
にした形状である。As shown in FIG. 3, the cutting blade edge portion 24c has a semicircular arc shape having a diameter larger than the outer diameter of the reinforcing bar 69. When swinging, the reinforcing bar 69 has a property that a force acts in a direction away from the support shaft 20 because it moves in a circular arc rather than a parallel motion. To prevent this, the reinforcing bar 69 does not slip and prevents slipping. The shape is
【００３６】例えば曲げ作業で１８０度曲げを行う場
合、ダイヤル２８で１８０度を設定すると、カム１８は
初期位置（図９）の状態からスタートし、図中右回りに
５０度程回転した位置から曲げを開始し、更に１８０度
程曲げの進んだ２３０度の位置でＵ字曲げが終了する。
切断の場合は更に１０度進んだ２４０度の位置で可動切
断刃２４ａは最下死点に達し切断が終了する。上記した
ように揺腕２１はカム１８と同一高さの面上にあり、カ
ム１８が２５０度以上回転するとカム１８の最大半径１
８ｄ部が揺腕２１に衝突しこれ以上回転不可能な構造に
なっている。このため例えば１８０度曲げを行うとした
のに誤って切断モードをセットしてしまった場合、１８
０度曲げと切断のカム１８の回転角の差は１０度しかな
いので、曲がった鉄筋６９がクロスして使い物にならな
い等の不具合は発生しない。また万一リミットスイッチ
３４が故障してもカム１８と揺腕２１が衝突して２５０
度以上回らないので上記同様曲がった鉄筋６９がクロス
して使い物にならない等の不具合は発生しない。For example, when bending 180 degrees in bending work, if the dial 28 is set to 180 degrees, the cam 18 will start from the initial position (FIG. 9), and will rotate from the position rotated about 50 degrees clockwise in the drawing. The bending is started, and the U-shaped bending is finished at a position of 230 ° where the bending is further advanced by 180 °.
In the case of cutting, the movable cutting blade 24a reaches the bottom dead center at a position of 240 degrees, which is further advanced by 10 degrees, and the cutting ends. As described above, the swing arm 21 is on the same level surface as the cam 18, and when the cam 18 rotates 250 degrees or more, the maximum radius of the cam 18 is 1
The 8d portion collides with the rocking arm 21 and cannot rotate any more. For this reason, for example, if the cutting mode is mistakenly set even though 180 degree bending is performed,
Since the difference between the rotation angles of the cam 18 for 0-degree bending and cutting is only 10 degrees, there is no problem that the bent reinforcing bars 69 cross and become unusable. Even if the limit switch 34 fails, the cam 18 and the swaying arm 21 collide with each other and 250
Since it does not turn more than once, the problem that the bent reinforcing bars 69 cross and become useless as in the above does not occur.
【００３７】（切断後の戻り）
上記したようにカム１８は３６０度回転できない構造の
ため、カム１８で設定した回転角を回転し終ると逆回転
して元の初期位置に戻る必要がある。リミットスイッチ
３４がダイヤル２８に連結した凸部３３で押されオンす
ると、これに連動したタイマ回路６３は３〜５秒間リレ
ー６２をオフする。その結果電動機１及びソレノイドコ
イル３７への通電は瞬時に停止される。電動機１は慣性
を持っているため電源オフ後も数秒間回転を続けるが、
ソレノイドコイル３７はオフして第１ギヤ８から第２ピ
ニオン９への回転の伝達が遮断するので出力軸１３の回
転は瞬時に停止する。ファイナルギヤ１２のカム１８側
の側面に設けられた凹部１２ａ内のねじりコイルバネ６
０により、ファイナルギヤ１２を常に逆回転方向に付勢
し、カム１８に初期位置に戻る方向に力を与えている
（スプリングクラッチ１５がつながり出力軸１３が回転
する場合は、出力軸１３はねじりコイルバネ６０の逆回
転方向のトルクに抗してカム１８を回すことになる）の
で、ねじりコイルバネ６０の復元力で、ファイナルギヤ
１２から第２ピニオン９までの減速部、出力軸１３、カ
ム１８は逆回転し、カム１８の初期位置すなわちカム１
８の最少半径の位置にカムローラ２２が当接し（図６、
図９の状態）、揺腕２１がスプリング２６で引き戻され
可動切断刃２４ａが最も開いた状態で停止する。カム１
８の初期位置でカム１８の曲げピン１６の圧入された最
大半径１８ｄに近い戻り斜面１８ｃが揺腕２１のボス部
２１ａに当接し、これがストッパとなってこれ以上逆回
転しない。これはカム１８や揺腕２１を固定部材１９よ
り図１中左側の同一面上に配置している効果であり、部
品を追加することなく常に可動切断刃２４ａは最も開い
た状態で停止でき、次に切断する鉄筋６９を切断刃刃部
２４ｃの横から入れることが可能であり、また曲げピン
１６も鉄筋６９がセット可能な位置まで後退して安定し
て止まることができる。(Return after cutting) Since the cam 18 cannot rotate 360 degrees as described above, it is necessary to return to the original initial position by rotating backward after the rotation angle set by the cam 18 is finished. When the limit switch 34 is pushed by the convex portion 33 connected to the dial 28 and turned on, the timer circuit 63 linked with this turns off the relay 62 for 3 to 5 seconds. As a result, the power supply to the electric motor 1 and the solenoid coil 37 is instantaneously stopped. Since the electric motor 1 has inertia, it continues to rotate for several seconds after the power is turned off.
The solenoid coil 37 is turned off and the transmission of rotation from the first gear 8 to the second pinion 9 is cut off, so that the rotation of the output shaft 13 is instantaneously stopped. The torsion coil spring 6 in the recess 12a provided on the side surface of the final gear 12 on the cam 18 side.
By 0, the final gear 12 is always biased in the reverse rotation direction, and a force is applied to the cam 18 in a direction to return to the initial position (when the spring clutch 15 is engaged and the output shaft 13 rotates, the output shaft 13 is twisted). Since the cam 18 is rotated against the torque of the coil spring 60 in the reverse rotation direction), the restoring force of the torsion coil spring 60 causes the speed reduction unit from the final gear 12 to the second pinion 9, the output shaft 13, and the cam 18 to Reverse rotation, the initial position of the cam 18, that is, the cam 1
The cam roller 22 comes into contact with the position of the minimum radius of 8 (see FIG. 6,
In the state of FIG. 9), the swing arm 21 is pulled back by the spring 26, and the movable cutting blade 24a is stopped in the most opened state. Cam 1
In the initial position of 8, the return slope 18c of the bending pin 16 of the cam 18 which is close to the maximum radius 18d of the press fits against the boss portion 21a of the rocking arm 21 and serves as a stopper to prevent further reverse rotation. This is an effect of arranging the cam 18 and the rocking arm 21 on the same plane on the left side of the fixing member 19 in FIG. 1, and the movable cutting blade 24a can always be stopped in the most opened state without adding parts, The rebar 69 to be cut next can be inserted from the side of the cutting blade portion 24c, and the bending pin 16 can also be retracted to a position where the rebar 69 can be set and stably stopped.
【００３８】（切断途中でメインスイッチ４１をオフし
た場合の戻り）
以上説明してきたのは、切断（あるいは曲げ）が完了
し、リミットスイッチ３４が作動した場合の戻りである
が、例えば途中で何等かの理由で作業を中断するためメ
インスイッチ４１をオフした場合も、電動機１とソレノ
イドコイル３７の電源はメインスイッチ４１に連動して
オフされるので、回転の伝達は遮断されカム１８や曲げ
ピン１６は上記同様戻りコイルばね６０の復元力で元に
戻る。(Return when the main switch 41 is turned off during cutting) The above is the return when the cutting (or bending) is completed and the limit switch 34 is actuated. Even if the main switch 41 is turned off to interrupt the work for some reason, the power supply of the electric motor 1 and the solenoid coil 37 is turned off in conjunction with the main switch 41, so that the rotation transmission is cut off and the cam 18 and the bending pin are cut off. 16 returns to the original state by the restoring force of the return coil spring 60 as described above.
【００３９】（リミットスイッチ３４作動後もメインス
イッチ４１をオフしない場合の戻り）
リミットスイッチ３４が作動するとリレー６２を介して
電源がオフされ戻りに入るのは前項で説明したが、もし
もすぐにメインスイッチ４１のトリガを放さず握ったま
までいると不都合なことが発生する。すなわち、戻りに
入ると出力軸１３が逆回転し、凸部３３がリミットスイ
ッチ３４から離れてリミットスイッチ３４が再びオフ状
態になり、リレー６２がオンとなりここでメインスイッ
チ４１がオン状態のままでいると再び電動機１が回転
し、スプリングクラッチ１５が回転伝達を開始し、カム
１８が正回転してしまい戻りが中断してしまう。そのた
め本実施形態では、リミットスイッチ３４で直接リレー
６２をオン・オフせず、リミットスイッチ３４が１度作
動したら、３〜５秒間リレー６２が電源の遮断を継続す
るようタイマ回路６３を設け、その間、戻り行程でリミ
ットスイッチ３４がオフされても初期位置に戻るまでの
時間、電動機１やソレノイドコイル３７が作動しないよ
うにしている。なお３〜５秒間の時間は、作業者が曲げ
や切断の終了に容易に気がついて、余裕を持ってメイン
スイッチ４１のトリガを放すために必要な時間として設
定した値である。(Return when the main switch 41 is not turned off even after the limit switch 34 is activated) When the limit switch 34 is activated, the power is turned off through the relay 62 to return to the operation as described in the previous section, but if the main switch immediately If the switch 41 is held without being released, an inconvenience may occur. That is, when returning, the output shaft 13 rotates in the reverse direction, the convex portion 33 separates from the limit switch 34, the limit switch 34 turns off again, the relay 62 turns on, and the main switch 41 remains on. If so, the electric motor 1 rotates again, the spring clutch 15 starts rotation transmission, the cam 18 rotates forward, and the return is interrupted. Therefore in this embodiment, not turned on and off directly relay 62 in the limit switch 34, when the limit switch 34 is actuated once, provided a timer circuit 63 so that 3-5 seconds relay 62 continues the cutoff of the power supply, during which Even when the limit switch 34 is turned off in the return stroke, the electric motor 1 and the solenoid coil 37 are prevented from operating during the time until the limit position is returned to the initial position. The time of 3 to 5 seconds is a value set as a time required for the operator to easily notice the end of bending or cutting and release the trigger of the main switch 41 with a margin.
【００４０】（曲げ作業）
次に鉄筋７０の曲げ作業について説明する。図１４にお
いて、切断の状態からハンドル４６を持って本体を９０
度回転させ、テールスタンド５２を地面に置くだけで、
その反対側に位置するカバー４９や曲げ機構部が上面と
なる位置関係になる。ダイヤル２８を所望の曲げ角度の
目盛りの位置にセットし、鉄筋７０をカバー４９の上に
置いて右手で鉄筋７０を水平状態で保持し位置決めする
と共に左手でハンドル４６を握りメインスイッチ４１を
操作し、右手で鉄筋７０を地面に対して水平のまま持っ
て保持する（図１４参照）。次にメインスイッチ４１の
トリガを引くと、切断時と同様に、この状態ではまだリ
ミットスイッチ３４は作動しない位置のため、リレー６
２はオン状態にあり、電流はリレー６２、メインスイッ
チ４１の位相制御端子４１ａ、界磁コイル２を介して電
機子３に流れ、電動機１はトリガの引き具合で調節され
た速度で回転する。ソレノイドコイル３７は、メインス
イッチ４１によりトリガを引くと同時に電源電圧が出力
端子４１ｂから供給され、トリガの引き具合に関係なく
強力にオン状態になり、発生した磁力でプランジャ３７
ａがスプリング３８の力に抗して第１ギヤ８側に突出
し、スリーブ６４が第１ギヤ８側に移動し、溝６４ａに
スプリングクラッチ１５の係止部１５ａが噛み合う。ス
リーブ６４は第２ピニオン９に対して軸方向には動ける
が回転方向には動かないスプライン溝４６ｂ等で回り止
めされているので、第１ギヤ８の回転でスプリングクラ
ッチ１５は締まり勝手の方向にねじられ、第１ギヤ８と
第２ピニオン９は強固に一体となり、出力軸１３に回転
が伝達されカム１８は回転する。ここでメインスイッチ
４１はトリガの引き加減で強く引くと速く、弱く引くと
ゆっくり回るよう電動機１の回転速度を変えられるスピ
ードコントロール機能内蔵型のスイッチであり、これに
より作業をゆっくりしたり、速くしたり手加減ができ
る。ソレノイドコイル３７へは、トリガの引き具合に関
係なく電源電圧が供給されるので、プランジャ３７ａの
吸引力が弱まる等の不具合はない。(Bending work) Next, the bending work of the reinforcing bar 70 will be described. In FIG. 14, hold the handle 46 to move the main body 90
Just rotate it and place the tail stand 52 on the ground.
The positional relationship is such that the cover 49 and the bending mechanism portion located on the opposite side are upper surfaces. The dial 28 is set at the position of the scale having the desired bending angle, the reinforcing bar 70 is placed on the cover 49, the reinforcing bar 70 is horizontally held and positioned by the right hand, and the handle 46 is grasped by the left hand to operate the main switch 41. , Hold the rebar 70 with the right hand while keeping it horizontal to the ground (see FIG. 14). Next, when the trigger of the main switch 41 is pulled, the limit switch 34 is still in the position in this state as in the case of disconnection.
2 is in the ON state, the current flows to the armature 3 via the relay 62, the phase control terminal 41a of the main switch 41, and the field coil 2, and the electric motor 1 rotates at a speed adjusted by the pulling condition of the trigger. The solenoid coil 37 is supplied with the power supply voltage from the output terminal 41b at the same time as the trigger is pulled by the main switch 41, and is strongly turned on regardless of how the trigger is pulled, and the generated magnetic force causes the plunger 37 to move.
a projects against the force of the spring 38 toward the first gear 8 side, the sleeve 64 moves toward the first gear 8 side, and the locking portion 15a of the spring clutch 15 meshes with the groove 64a. Since the sleeve 64 is prevented from rotating by the spline groove 46b or the like that can move in the axial direction but does not move in the rotation direction with respect to the second pinion 9, the rotation of the first gear 8 causes the spring clutch 15 to be tightened in the direction of its own preference. When twisted, the first gear 8 and the second pinion 9 are firmly integrated with each other, and the rotation is transmitted to the output shaft 13 so that the cam 18 rotates. Here, the main switch 41 is a switch with a built-in speed control function that can change the rotation speed of the electric motor 1 so that if the pulling force is increased or decreased by pulling the trigger strongly, it will be fast, and if the pulling force is weak, it will rotate slowly. It can be adjusted. Since the power supply voltage is supplied to the solenoid coil 37 irrespective of the pulling condition of the trigger, there is no problem such that the attraction force of the plunger 37a is weakened.
【００４１】カム１８上の曲げピン１６は図２で右横か
ら真下、左横へ移動するため、曲げる鉄筋７０の先端側
７０ｂはハンドル４６側に位置する作業者から離れる方
向に動き（図１４参照）、従って動く先端部が作業者に
接触する恐れは無い。図９において、鉄筋７０は受けピ
ン３５の受けローラ３６と中心ピン２７で回転方向の動
きを押えられ、中心ピン２７の周りを回転する曲げピン
１６の曲げローラ６６で、図中右側から右回りに出力軸
１３の１５０Ｎｍ程度の回転トルク（曲げ作業時の電動
機負荷は切断作業時の電動機負荷よりやや小さくなり、
出力軸１３の回転トルクは切断作業時よりやや小さくな
る）で押すことで、中心ピン２７に沿って任意の角度に
曲げられる（図１０、図１１参照）。ここで、曲げピン
１６と受けピン３５に外径の大きなローラ６６、３６を
設けたのは、曲げの際に鉄筋７０とピン１６、３５の間
の摩擦力をローラ６６、３６が回転することで少なく
し、小さいトルクで曲げられるようにするためである。
従って、ローラは中心ピン２７と曲げピン１６にあり、
受けピン３５に無くても効果は同様である。また、受け
ピン３５を円柱状のピンとし、その外周のローラを円形
断面にしたものは、鉄筋７０と受けピン３５の間に異物
（例えば鉄筋７０の短い切りかす）が挟まっても、円形
なので力が加わると容易に外れてしまうので、曲げ角が
狂う等の不具合が無い。また、図２２に示すように、ロ
ーラ６６、３６は単純な円筒でなく、両端が大きく中央
で凹んだ形状（この最少直径部がピン１６、３５の根元
側に近い方が片持ちのピン１６、３５に作用する曲げモ
ーメントが小さくなり更に良い）としている。これは、
本体を空中に持ちあげて曲げた際に、不安定でふらつく
鉄筋７０がローラ６６、３６から外れず、なるべくロー
ラ６６、３６の根元近くで保持できるよう鉄筋７０をロ
ーラ６６、３６の凹部へよび込むための工夫である。Since the bending pin 16 on the cam 18 moves from right side to right below and left side in FIG. 2, the tip side 70b of the bending rebar 70 moves in a direction away from the operator located on the handle 46 side (FIG. 14). Therefore, there is no risk of the moving tip contacting the operator. In FIG. 9, the reinforcing bar 70 is pressed by the receiving roller 36 of the receiving pin 35 and the center pin 27 in the rotational direction, and is bent by the bending roller 66 of the bending pin 16 that rotates around the center pin 27. In addition, the rotational torque of the output shaft 13 of about 150 Nm (the electric motor load during bending work is slightly smaller than the electric motor load during cutting work,
The rotational torque of the output shaft 13 is slightly smaller than that during the cutting work), so that the output shaft 13 is bent at an arbitrary angle along the center pin 27 (see FIGS. 10 and 11). Here, the rollers 66 and 36 having a large outer diameter are provided on the bending pin 16 and the receiving pin 35 so that the rollers 66 and 36 rotate due to the frictional force between the reinforcing bar 70 and the pins 16 and 35 during bending. This is to reduce the bending force with a small amount and to be able to bend with a small torque.
Therefore, the rollers are on the center pin 27 and the bending pin 16,
The effect is the same even if the receiving pin 35 is not provided. In addition, when the receiving pin 35 is a cylindrical pin and the roller on the outer periphery thereof has a circular cross section, even if a foreign matter (for example, a short scrap of the reinforcing bar 70) is caught between the reinforcing bar 70 and the receiving pin 35, it is circular. It will come off easily when a force is applied, so there is no problem such as bending angle deviation. Further, as shown in FIG. 22, the rollers 66, 36 are not simple cylinders, but have a shape in which both ends are largely recessed in the center (the smallest diameter portion closer to the root side of the pins 16, 35 is a cantilevered pin 16). , 35, and the bending moment acting on 35 becomes smaller. this is,
When the main body is lifted up in the air and bent, the unstable and unstable reinforcing bar 70 does not come off from the rollers 66 and 36, and the reinforcing bar 70 is held in the recesses of the rollers 66 and 36 so that it can be held as close to the roots of the rollers 66 and 36 as possible. It is a device to incorporate it.
【００４２】例えば直径１３ｍｍの鉄筋７０を曲げるの
に必要な出力軸１３のトルクは、１５０Ｎｍ程度であ
り、これは前記切断機構で説明した切断時のトルク１８
６Ｎｍよりやや小さいがおおよそ近い値である。これは
切断時のカム１８の倍力率Ｋｃとテコの倍力率Ｋｔの工
夫によって達成されたものであり、曲げ及び切断の際の
出力軸１３のトルクが０．７倍から１．５倍程度の差で
あれば、例えばギヤ等では、寸法を変えることなく熱処
理、材質、ハスバ歯車化等でこれに耐えるギヤを製造可
能であるし、電動機１では同じ大きさで巻線仕様や回転
数の変更で対応可能であり、切断または曲げいずれか一
方のためにギヤや電動機１を大きくする必要の無い範囲
である。これにより、電動機１やギヤの大きさもバラン
ス良く最少最軽量の物を選択できる。また、切断のため
の揺腕２１と曲げのための曲げピン１６は常に同時に動
いているので、曲げと切断の作業の切り換えは、ダイア
ル２８のセットと本体の向きを変えるだけでその手間は
非常に簡便である。そして同一出力軸１３から常に動力
を受け、この大きなトルクを切断用と曲げ用に切り換え
る機構が無いので、コストもかからず軽量で故障が少な
く信頼性が高い。For example, the torque of the output shaft 13 required for bending the reinforcing bar 70 having a diameter of 13 mm is about 150 Nm, which is the torque 18 at the time of cutting described in the cutting mechanism.
Although it is slightly smaller than 6 Nm, it is close. This is achieved by devising the boosting factor Kc of the cam 18 at the time of cutting and the boosting factor Kt of the lever, and the torque of the output shaft 13 at the time of bending and cutting is 0.7 to 1.5 times. If there is a difference in degree, it is possible to manufacture a gear that withstands heat treatment, material, helical gears, etc. without changing the dimensions of the gear etc. Can be dealt with by changing the above, and there is no need to increase the size of the gear or the electric motor 1 for either cutting or bending. As a result, the size of the electric motor 1 and the gear can be well balanced and the smallest and lightest one can be selected. Moreover, since the rocking arm 21 for cutting and the bending pin 16 for bending are always moving at the same time, the work of bending and cutting can be switched only by changing the direction of the dial 28 and the body. It is easy to use. Since there is no mechanism for constantly receiving power from the same output shaft 13 and switching this large torque between cutting and bending, the cost is low, the weight is low, the breakdown is low, and the reliability is high.
【００４３】図１５のように既設の上向きや横向きの鉄
筋７０の上端を曲げる場合、本体下部のボトムスタンド
５１のグリップ４７を上方に向け本体重量を支えなが
ら、対称に下部にくるハンドル４６で方向を合わせてメ
インスイッチ４１を操作して本体が安定した状態で曲げ
られる。これ以降停止して戻る行程は上記切断の場合と
全く同一であり説明を省略する。As shown in FIG. 15, when bending the upper end of an existing upward or horizontal reinforcing bar 70, the grip 47 of the bottom stand 51 at the bottom of the main body is directed upward while supporting the weight of the main body, and the handle 46 symmetrically comes to the lower direction. Then, the main switch 41 is operated to bend the main body in a stable state. The process of stopping and returning thereafter is exactly the same as in the case of the above disconnection, and the description thereof will be omitted.
【００４４】上記実施形態においては曲げ作業時の鉄筋
７０の反力を受ける曲げピン３５を独立して設けるとし
たが、上記した如く支軸２０をカバー４９より外側に突
出して設け、該支軸２０の突出部を受けピンと兼用させ
てもよく、この場合には構成を簡単にできると共に安価
な切断曲げ工具を提供できるようになる。また１３ｍｍ
の鉄筋を切断または曲げるとしたが、これ以上の例えば
１６、１９、２２ｍｍの鉄筋にも採用できることは明ら
かであり、この場合には電動機１、歯車列７〜１２を適
宜設定すればよい。更に切断曲げ工具として説明した
が、前記揺腕２１、カム１８、切断刃２４ａ、２４ｂ等
の切断機構部を取り除き、出力軸１３の軸心から離れた
偏心位置に曲げピン６６を設けた曲げ専用機としても同
様な効果が得られる。In the above-described embodiment , the bending pin 35 that receives the reaction force of the reinforcing bar 70 during bending work is provided independently, but as described above, the support shaft 20 is provided so as to project outside the cover 49, and the support shaft 20 is provided. The protruding portion of 20 may be used also as a receiving pin. In this case, the structure can be simplified and an inexpensive cutting and bending tool can be provided. Also 13 mm
Although the rebar of No. 1 was cut or bent, it is obvious that it can be applied to rebars of more than 16, 19 and 22 mm, and in this case, the electric motor 1 and the gear trains 7 to 12 may be appropriately set. Further, the cutting and bending tool has been described, but the bending mechanism in which the rocking arm 21, the cam 18, the cutting blades 24a, 24b, and the like are removed and a bending pin 66 is provided at an eccentric position away from the axis of the output shaft 13 The same effect can be obtained as a machine.
【００４５】[0045]
【発明の効果】以上説明したように本発明によれば以下
に示す作用効果を奏し得る。
（１）切断機構にカムのくさび作用と揺腕のテコの作用
を利用した倍力機構を用い、カム側面に曲げピンを設け
て曲げ機構を形成することで、出力軸、減速歯車列、電
動機等を曲げと切断で共用化でき、本体の軽量化と同時
に低価格にできる。また、揺腕のテコ比で切断に必要な
カムの押し上げ力を数分の１に低減でき、カム側面に曲
げピンを設けることにより、カムが片持ち構造となって
も強度上有利となり、またギヤや電動機を小型化でき
る。
（２）曲げピンをカムの側面に取り付けたことにより、
曲げピン取付用のクランク状の腕を別体に設ける必要が
なくなり、部品低減と出力軸の短縮による小型、軽量、
低価格化が可能である。As described above, according to the present invention, the following operational effects can be obtained. (1) An output shaft, a reduction gear train, and an electric motor are formed by using a boosting mechanism that uses the wedge action of a cam and the lever action of a rocking arm as a cutting mechanism, and forming a bending mechanism by providing a bending pin on the side surface of the cam. Bending and cutting can be shared, and the main body can be made lightweight and at a low price. In addition, the pushing force of the cam required for cutting can be reduced to a fraction of the lever ratio of the swaying arm, and by providing a bending pin on the side of the cam, it is advantageous in strength even if the cam has a cantilever structure. Gears and electric motors can be downsized. (2) By attaching the bending pin to the side of the cam,
It is not necessary to separately provide a crank-shaped arm for mounting the bending pin, and the number of parts is reduced and the output shaft is shortened.
The price can be reduced.
【００４６】（３）カム形状（荷重曲線に合わせた複数
円弧の組み合わせ）やてこ比を適度に設定することで曲
げも切断もほぼ近い値の駆動トルクで可能となり、電動
機やギヤが無駄なく最小限の大きさで最適化できる。(3) By appropriately setting the cam shape (combination of a plurality of arcs according to the load curve) and lever ratio, bending and cutting can be performed with a driving torque of almost the same value, and the electric motor and gear can be minimized without waste. It can be optimized with a limit size.
【００４７】（４）揺腕とカムを固定部材上に同一高さ
に配置したので、作業後カムが逆回転して戻った際に、
揺腕がカムのストッパになり、何等部品を追加すること
なく定位置で停止できる。カムが最も回転した位置で揺
腕がカムのストッパになり、この時の位置が１８０度曲
げよりも２０度程度しか進んだ位置でしかないので、リ
ミットスイッチの故障があっても電動機がロックするだ
けで、曲げた鉄筋がクロスする等の外部に与える不具合
が無い。(4) Since the rocking arm and the cam are arranged at the same height on the fixed member, when the cam reversely rotates and returns after the work,
The oscillating arm serves as a cam stopper and can be stopped at a fixed position without adding any parts . Cams are Yuraude becomes the stopper cam in the most rotated position, the position at this time is not only only advanced position about 20 degrees than the bending 180 degrees, there is a failure of re <br/>Mittosui' Ji Even if the electric motor only locks, the bent rebar crosses and other external problems
There is no .
【００４８】（５）スイッチをトリガの引き具合で速度
が変えられるスピードコントロールスイッチとし、この
スイッチをハンドル内に収納したので、重い鉄筋等の被
加工材を載せた本体をハンドルで支えながらトリガの引
き具合で、目で見ながらゆっくり曲げを行い、止めたい
時にはトリガを戻せば直ちに停止でき、手動工具に近い
感覚の手加減ができ作業性が良い。(5) Since the switch is a speed control switch whose speed can be changed depending on the pulling condition of the trigger, and the switch is housed in the handle, the handle is supported while the main body on which the work material such as heavy reinforcing bar is placed is supported by the handle. in pulling condition, have slowly Ri songs Geogyo while looking in the eyes, can be stopped immediately by returning the trigger when you want to stop, good workability can be easy on the senses close to the hand tools.
【００４９】（６）曲げ機構部のピンと、スイッチの付
いたハンドルの位置関係の工夫で、曲げられ移動する鉄
筋の先端は作業者から遠ざかる方向に動くので、鉄筋の
移動する先端が作業者に触れる恐れが無い。作業時には
本体を保持しスイッチを操作する必要があるが、スイッ
チ内蔵のハンドルは保持と操作を行うために必ずハンド
ル側に立つ必要があり、本体に対する作業者の立つ位置
を規定するので上記効果はより確実になる。(6) By devising the positional relationship between the pin of the bending mechanism and the handle with the switch, the tip of the rebar that is bent and moves moves away from the operator, so the tip of the rebar that moves moves to the operator. There is no fear of touching. It is necessary to hold the main body and operate the switch at the time of work, but the handle with a built-in switch must stand on the handle side in order to hold and operate it. Become more certain.
【図１】本発明電動式切断曲げ工具の一実施形態を示す
横断面図。FIG. 1 is a cross-sectional view showing an embodiment of an electric cutting and bending tool of the present invention.
【図２】図１の正面図。FIG. 2 is a front view of FIG.
【図３】図２のカバー、回転カバーを外した状態を示す
正面図。FIG. 3 is a front view showing a state in which the cover and the rotation cover of FIG. 2 are removed.
【図４】図１の斜視図。FIG. 4 is a perspective view of FIG.
【図５】住宅等の基礎や外構に用いる鉄筋の使用例を示
す斜視図。FIG. 5 is a perspective view showing a usage example of a reinforcing bar used for a foundation of a house or the like or an external structure.
【図６】本発明切断曲げ工具の切断機構の動作を示す正
面図。FIG. 6 is a front view showing the operation of the cutting mechanism of the cutting and bending tool of the present invention.
【図７】本発明切断曲げ工具の切断機構の動作を示す正
面図。FIG. 7 is a front view showing the operation of the cutting mechanism of the cutting and bending tool of the present invention.
【図８】本発明切断曲げ工具の切断機構の動作を示す正
面図。FIG. 8 is a front view showing the operation of the cutting mechanism of the cutting and bending tool of the present invention.
【図９】本発明切断曲げ工具の曲げ機構の動作を示す正
面図。FIG. 9 is a front view showing the operation of the bending mechanism of the cutting and bending tool of the present invention.
【図１０】本発明切断曲げ工具の曲げ機構の動作を示す
正面図。FIG. 10 is a front view showing the operation of the bending mechanism of the cutting and bending tool of the present invention.
【図１１】本発明切断曲げ工具の曲げ機構の動作を示す
正面図。FIG. 11 is a front view showing the operation of the bending mechanism of the cutting and bending tool of the present invention.
【図１２】本発明切断曲げ工具の電気的接続を示す回路
図。FIG. 12 is a circuit diagram showing electrical connection of the cutting and bending tool of the present invention.
【図１３】本発明切断曲げ工具の切断作業の一例を示す
斜視図。FIG. 13 is a perspective view showing an example of a cutting operation of the cutting and bending tool of the present invention.
【図１４】本発明切断曲げ工具の曲げ作業の一例を示す
斜視図。FIG. 14 is a perspective view showing an example of bending work of the cutting and bending tool of the present invention.
【図１５】本発明切断曲げ工具の既設の上向き鉄筋の曲
げ作業を示す斜視図。FIG. 15 is a perspective view showing a bending operation of an existing upward reinforcing bar of the cutting and bending tool of the present invention.
【図１６】本発明切断曲げ工具を構成するクラッチ部分
を示す断面図。FIG. 16 is a sectional view showing a clutch portion constituting the cutting and bending tool of the present invention.
【図１７】リミットスイッチとダイヤルとの関係を示す
斜視図。FIG. 17 is a perspective view showing the relationship between limit switches and dials.
【図１８】本発明を構成するカムと曲げピンとの他の実
施形態を示す部分断面図。FIG. 18 is another example of the cam and the bending pin that constitute the present invention.
The fragmentary sectional view showing an embodiment .
【図１９】本発明を構成するカムの倍力機構の原理を示
す説明用正面図。FIG. 19 is an explanatory front view showing the principle of a cam boosting mechanism that constitutes the present invention.
【図２０】鉄筋の切断荷重と切断刃のストロークの関係
を示すグラフ。FIG. 20 is a graph showing the relationship between the cutting load of the reinforcing bar and the stroke of the cutting blade.
【図２１】本発明を構成する切断刃の軸方向の断面図。FIG. 21 is an axial cross-sectional view of a cutting blade that constitutes the present invention.
【図２２】本発明を構成する曲げローラと受けローラの
軸方向の断面図。FIG. 22 is an axial cross-sectional view of a bending roller and a receiving roller constituting the present invention.
１は直巻整流子電動機、６はハウジング、７、９、１１
はピニオン、８、１０はギヤ、１２はファイナルギヤ、
１３は出力軸、１４はギヤカバー、１５はスプリングク
ラッチ、１６は曲げピン、１８はカム、１８ａは早送り
面、１８ｂは切断面、１８ｃは戻り面、１８ｄはカムの
最大半径部、１９は固定部材、２０は支軸、２１は揺
腕、２２はカムローラ、２４ａ、２４ｂは切断刃、２７
は中心ピン、２８はダイヤル、３４はリミットスイッ
チ、３５は受けピン、３６は受けローラ、４１はメイン
スイッチ、４６はハンドル、４７はグリップ、４８は電
源コード、４９はカバー、５０は回転カバー、５１はボ
トムスタンド、５２はテールスタンド、６０はねじりコ
イルバネ、６２はリレー、６３はタイマ、６６は曲げロ
ーラ、６９は切断用鉄筋、７０は曲げ用鉄筋である。1 is a series-wound commutator motor, 6 is a housing, 7, 9, 11
Is a pinion, 8, 10 is a gear, 12 is a final gear,
Reference numeral 13 is an output shaft, 14 is a gear cover, 15 is a spring clutch, 16 is a bending pin, 18 is a cam, 18a is a rapid feed surface, 18b is a cutting surface, 18c is a return surface, 18d is a maximum radius portion of the cam, and 19 is a fixing member. , 20 is a support shaft, 21 is a rocking arm, 22 is a cam roller, 24a and 24b are cutting blades, 27
Is a center pin, 28 is a dial, 34 is a limit switch, 35 is a receiving pin, 36 is a receiving roller, 41 is a main switch, 46 is a handle, 47 is a grip, 48 is a power cord, 49 is a cover, 50 is a rotary cover, 51 is a bottom stand, 52 is a tail stand, 60 is a torsion coil spring, 62 is a relay, 63 is a timer, 66 is a bending roller, 69 is a cutting rebar, and 70 is a bending rebar.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 平６−39445（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) B21D 7/024 B21F 1/00 B21F 11/00 B23D 29/003 ─────────────────────────────────────────────────── ─── Continuation of front page (56) References JP-A-6-39445 (JP, A) (58) Fields investigated (Int.Cl. 7 , DB name) B21D 7/024 B21F 1/00 B21F 11 / 00 B23D 29/003
Claims (5)
機の回転を減速する歯車列と、歯車列のファイナルギヤ
によって駆動される出力軸と、出力軸に一体または別体
で設けられ、半径を急激に増す早送り面及び半径をゆる
やかに増す切断面の少なくとも二つの異なる曲率の転動
面を有するカムと、本体外枠に固定された固定部材と、
支軸を介して固定部材に回転可能に支持され、カムの転
動面に接するカムローラ及び可動切断刃を両端に装着
し、支軸を中心としてカムによって回転される揺腕と、
可動切断刃に対向する如く固定部材に装着された固定切
断刃と、出力軸の先端に一体または別体で設けられた中
心ピンと、カムの中心ピンから離れた位置に設けられた
曲げピンとを備え、前記可動切断刃及び固定切断刃によ
り被加工材を切断すると共に中心ピンの周りを回動する
曲げピンによって被加工材を曲げるようにしたことを特
徴とする電動式切断曲げ工具。1. An electric motor housed in an outer frame of a main body, a gear train for decelerating the rotation of the electric motor, an output shaft driven by a final gear of the gear train, and an output shaft integrally or separately provided, A cam having at least two rolling surfaces having different curvatures, a rapid feed surface that sharply increases the radius and a cutting surface that gently increases the radius; and a fixing member fixed to the outer frame of the main body.
A wobble arm that is rotatably supported by a fixed member via a support shaft, is equipped with cam rollers and movable cutting blades that contact the rolling surface of the cam at both ends, and is rotated by the cam around the support shaft.
A fixed cutting blade mounted on a fixed member so as to face the movable cutting blade, a center pin integrally or separately provided at the tip of the output shaft, and a bending pin provided at a position apart from the center pin of the cam. An electric cutting and bending tool characterized in that the work material is cut by the movable cutting blade and the fixed cutting blade, and the work material is bent by a bending pin that rotates around a center pin.
に受けピンを装着し、受けピンを曲げ作業時の反力受け
としたことを特徴とする請求項１記載の電動式切断曲げ
工具。2. The electric cutting and bending tool according to claim 1, wherein a receiving pin is mounted at a position apart from the center pin of the fixing member, and the receiving pin serves as a reaction force receiving member during bending work.
業時の反力受けとなる受けピンとしたことを特徴とする
請求項１記載の電動式切断曲げ工具。3. The electric cutting and bending tool according to claim 1, wherein the spindle is extended to the outside of the outer frame of the main body to form a receiving pin that receives a reaction force during bending work.
曲率を複数の円弧の集合で構成し、転動面に接触するカ
ムローラのくさび作用による倍力率Ｋｃ及び揺腕の支軸
に対するてこ比による倍力率Ｋｔの設定により、切断作
業時に出力軸に加えるべき駆動トルクＴｃと曲げ作業時
に曲げピンを回動させるために出力軸に加えるべき駆動
トルクＴｂとの比（Ｔｃ／Ｔｂ）を０．６７〜１．５の
範囲としたことを特徴とする請求項１記載の電動式切断
曲げ工具。4. A curvature factor of a rolling surface of the cam whose radius gradually increases is constituted by a set of a plurality of arcs, and a power factor Kc by a wedge action of a cam roller contacting the rolling surface and a supporting shaft of a rocking arm. By setting the power factor Kt based on the lever ratio, the ratio (Tc / Tb) between the driving torque Tc to be applied to the output shaft during cutting work and the driving torque Tb to be applied to the output shaft for rotating the bending pin during bending work. The range of 0.67-1.5 was set, The electric cutting tool according to claim 1 characterized by things.
同一面上に配置し、カムと揺腕の位置関係を、出力軸が
所定角度を超えて回転する時にカムの一部分が揺腕に当
設するように設定し、出力軸が１回転しないようにした
ことを特徴とする請求項１記載の電動式切断曲げ工具。5. The oscillating arm and the cam are arranged on substantially the same plane of the side surface of the fixing member, and the cam and the oscillating arm have a positional relationship such that when the output shaft rotates beyond a predetermined angle, a part of the cam becomes the oscillating arm. The electric cutting and bending tool according to claim 1, characterized in that it is set so as to be provided so that the output shaft does not rotate once.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08801696A JP3446467B2 (en) | 1996-04-10 | 1996-04-10 | Electric cutting or bending tool |
| US08/827,908 US5931039A (en) | 1996-04-10 | 1997-04-07 | Electrical bar cutting and bending tool |
| DE1997114663 DE19714663C2 (en) | 1996-04-10 | 1997-04-09 | Electric cutting and bending tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08801696A JP3446467B2 (en) | 1996-04-10 | 1996-04-10 | Electric cutting or bending tool |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2003107844A Division JP2003266128A (en) | 2003-04-11 | 2003-04-11 | Electrically-driven bending tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09271849A JPH09271849A (en) | 1997-10-21 |
| JP3446467B2 true JP3446467B2 (en) | 2003-09-16 |
Family
ID=13931050
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP08801696A Expired - Lifetime JP3446467B2 (en) | 1996-04-10 | 1996-04-10 | Electric cutting or bending tool |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3446467B2 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008173726A (en) * | 2007-01-19 | 2008-07-31 | Hitachi Koki Co Ltd | Portable cutting-off tool |
| DE202008012415U1 (en) * | 2008-09-18 | 2010-02-11 | Weidmüller Interface GmbH & Co. KG | drill intent |
| KR101440538B1 (en) * | 2013-04-22 | 2014-09-15 | 주식회사 나이스맥 | Cutting tools for Spring forming machine |
| JP7127377B2 (en) * | 2018-06-14 | 2022-08-30 | 工機ホールディングス株式会社 | Electric tool |
| JP7159632B2 (en) * | 2018-06-15 | 2022-10-25 | 工機ホールディングス株式会社 | work machine |
| CN111934246B (en) * | 2020-08-11 | 2021-07-20 | 国网山东省电力公司平原县供电公司 | Cable junction is with device of skinning |
| CN115971373B (en) * | 2023-03-22 | 2023-05-12 | 平山县交通运输局地方道路管理站 | Reinforcing bar cuts equipment for highway construction |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0639445A (en) * | 1993-06-08 | 1994-02-15 | Sone Kogu Seisakusho:Kk | Portable type bender |
-
1996
- 1996-04-10 JP JP08801696A patent/JP3446467B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH09271849A (en) | 1997-10-21 |
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