JP2003039341A - Electro-hydraulic tightening tool - Google Patents
Electro-hydraulic tightening toolInfo
- Publication number
- JP2003039341A JP2003039341A JP2001235939A JP2001235939A JP2003039341A JP 2003039341 A JP2003039341 A JP 2003039341A JP 2001235939 A JP2001235939 A JP 2001235939A JP 2001235939 A JP2001235939 A JP 2001235939A JP 2003039341 A JP2003039341 A JP 2003039341A
- Authority
- JP
- Japan
- Prior art keywords
- pressure chamber
- oil
- liner
- output shaft
- high pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、電動モータにより
回転駆動されて衝撃トルクを発生するオイルパルス機構
を備えた電動油圧式締結工具に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electrohydraulic fastening tool equipped with an oil pulse mechanism that is driven to rotate by an electric motor to generate an impact torque.
【０００２】[0002]
【従来の技術】一般にオイルパルス機構は、電動モータ
により回転されるライナに形成した部屋内にオイルを充
填、密閉し、ライナ内に同軸に挿入された出力軸に２個
の挿入溝を設け、挿入溝内に羽根を挿入し、羽根を常時
出力軸の外周方向に付勢してライナに当接するように構
成し、ライナを回転駆動することにより、ライナの内周
面に形成したシール部と出力軸の外周面に形成したシー
ル部が合致した時オイルパルス機構内に圧力が発生し
て、出力軸から衝撃トルクが発生される。従って、金属
同士の衝突がないため従来から低騒音型として用いられ
ている。また、電動モータ用のオイルパルス機構を用い
た電動油圧式締結工具としては、特開昭５９−１２９６
７５号公報、実公平４−５１９８８号公報を挙げること
ができる。2. Description of the Related Art Generally, an oil pulse mechanism fills and seals oil in a room formed in a liner rotated by an electric motor, and two insertion grooves are provided on an output shaft coaxially inserted in the liner. By inserting the blade into the insertion groove and constantly biasing the blade in the outer peripheral direction of the output shaft to contact the liner, by rotating the liner, the seal portion formed on the inner peripheral surface of the liner When the seal portion formed on the outer peripheral surface of the output shaft is matched, pressure is generated in the oil pulse mechanism, and impact torque is generated from the output shaft. Therefore, since there is no collision between metals, it has been conventionally used as a low noise type. Further, as an electrohydraulic fastening tool using an oil pulse mechanism for an electric motor, Japanese Patent Laid-Open No. 59-1296 is available.
75 and Japanese Utility Model Publication No. 4-51988.
【０００３】[0003]
【発明が解決しようとする課題】前述のオイルパルス機
構を用いた電動油圧式締結工具では、電動モータの回転
力によりオイルパルス部内のオイルを急激に圧力上昇さ
せ、その時に発生する圧力を利用してネジやボルトを締
付ける。この圧力は、オイルパルス部の出力軸とライナ
の相対速度で決定され、ネジ締付とボルト締付では大き
く差があり、ネジ締付時はネジが常に回転しているため
相対速度が小さく、高いピーク圧力は発生せず、ボルト
締付時はボルトが回転しないため相対速度が大きく、常
に高いピーク圧力を発生し続け、ついにはオイルパルス
部がオイル洩れを発生し、締付トルクが低下するという
欠点があった。In the electrohydraulic fastening tool using the oil pulse mechanism described above, the rotational force of the electric motor causes the oil in the oil pulse portion to rapidly rise in pressure, and the pressure generated at that time is used. Tighten the screws and bolts. This pressure is determined by the relative speed of the output shaft of the oil pulse section and the liner, and there is a large difference between screw tightening and bolt tightening.When screw tightening, the relative speed is small because the screw is always rotating, High peak pressure does not occur, and the bolt does not rotate when tightening the bolt, so the relative speed is large, and constantly high peak pressure continues to be generated, eventually the oil pulse part leaks oil and the tightening torque decreases. There was a drawback.
【０００４】この欠点は、オイルパルス部内の発生圧力
を低くするという方法で改善できるが、ボルト締付時の
高いピーク圧力の低下と共に、ネジ締付時の圧力も低下
させてしまうことになり、ネジ締付スピードが遅くなる
という欠点がある。This drawback can be improved by lowering the pressure generated in the oil pulse portion, but the high peak pressure at the time of tightening the bolt is lowered and the pressure at the time of screw tightening is also lowered. There is a drawback that the screw tightening speed becomes slow.
【０００５】本発明の目的は、ボルト締付時、又はボル
ト締付に近い高負荷作業時にオイルパルス内で発生する
高いピーク圧力を低下させ、高いピーク圧力によるオイ
ル洩れを軽減し、締付トルクの低下を抑えた電動油圧式
締結工具を提供することにある。An object of the present invention is to reduce the high peak pressure generated in an oil pulse during bolt tightening or during high load work close to bolt tightening, reduce oil leakage due to high peak pressure, and tighten torque. It is to provide an electro-hydraulic fastening tool that suppresses the deterioration of
【０００６】[0006]
【課題を解決するための手段】前述の目的を達成するた
めに、本発明のオイルパルス機構では、電動モータと共
に回転駆動するライナ内に回転自在に出力軸を支持し、
出力軸に形成された出力軸の直角方向に挿入溝を貫通
し、挿入溝とライナとの間に配置された羽根を挾んでオ
イルを有する複数の室を形成し、ライナを回転駆動して
オイルを圧縮して複数の室の少なくとも１つに高圧室を
形成し、高圧室内のオイル圧が羽根を押圧して発生した
衝撃トルクにより出力軸を駆動し、この衝撃トルクを発
生する高圧室のオイル圧を低圧室に逃がす圧力緩和手段
を設け、オイル漏れと締付トルクの低下とを防止するこ
とを特徴とする。In order to achieve the above-mentioned object, in the oil pulse mechanism of the present invention, an output shaft is rotatably supported in a liner which is rotationally driven together with an electric motor,
A plurality of chambers containing oil are formed by penetrating the insertion groove formed in the output shaft in the direction perpendicular to the output shaft and sandwiching the blades arranged between the insertion groove and the liner to rotate the liner to drive the oil. Is compressed to form a high pressure chamber in at least one of the plurality of chambers, and the output shaft is driven by the impact torque generated by the oil pressure in the high pressure chamber pressing the blades, and the oil in the high pressure chamber that generates this impact torque It is characterized in that a pressure easing means for escaping the pressure to the low pressure chamber is provided to prevent oil leakage and a decrease in tightening torque.
【０００７】[0007]
【発明の実施の形態】即ち、本発明ではネジ締付時の発
生圧力に影響することなくボルト締付時の高いピーク圧
力のみ低下させる方法として、ライナを回転駆動するこ
とにより、ライナの内周面に形成したシール部と出力軸
の外周面に形成したシール部が合致した時、オイルパル
ス機構内に形成される高圧室と低圧室をつなぐように連
通路を設け、更に、連通路内に配置した開閉弁をボルト
締付時等の高いピーク圧力が発生した時に、開放するよ
うに設定することで達成される。BEST MODE FOR CARRYING OUT THE INVENTION That is, according to the present invention, as a method of lowering only a high peak pressure at the time of bolt tightening without affecting the pressure generated at the time of screw tightening, the inner circumference of the liner is rotated by rotating the liner. When the seal part formed on the surface and the seal part formed on the outer peripheral surface of the output shaft match, a communication passage is provided to connect the high pressure chamber and the low pressure chamber formed in the oil pulse mechanism, and further, in the communication passage. This is achieved by setting the placed on-off valve to open when a high peak pressure occurs such as when tightening bolts.
【０００８】以下、本発明の具体的な実施例について図
面を参照して説明する。図１は、この発明に係わる電動
油圧式締結工具の要部断面図である。Specific embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of an essential part of an electrohydraulic fastening tool according to the present invention.
【０００９】概略構造はハウジング２内に後方より電動
モータ１、遊星歯車機構部３、オイルパルス機構部４、
ハンマケース６が配置されている。オイルパルス機構部
４は、オイルの圧縮を利用した公知のものである。The general structure is as follows. The electric motor 1, the planetary gear mechanism 3, the oil pulse mechanism 4 are arranged in the housing 2 from the rear side.
A hammer case 6 is arranged. The oil pulse mechanism section 4 is a known one that utilizes compression of oil.
【００１０】衝撃トルク発生時の動作は、充電可能の電
池（図示せず）から電源を供給され電動モータ１が駆動
し、電動モータ１の動力はモータ１の先端に連結されて
いるピニオン３１を介して遊星歯車機構部３に伝達さ
れ、オイルパルス機構部４を駆動する。In the operation when the impact torque is generated, the electric motor 1 is driven by supplying power from a rechargeable battery (not shown), and the power of the electric motor 1 is supplied to the pinion 31 connected to the tip of the motor 1. It is transmitted to the planetary gear mechanism section 3 via the motor and drives the oil pulse mechanism section 4.
【００１１】図１及び図２(Ａ)，(Ｂ)にオイルパルス機
構部４を示し説明する。電動モータ１と共に回転駆動す
るライナ７内に回転自在に出力軸５を支持し、出力軸５
に出力軸５の直角方向に貫通する挿入溝５１を形成し、
挿入溝５１に２個の羽根８Ａ，８Ｂを配置し、２個の羽
根８Ａ，８Ｂは互いに反対方向に伸びてライナ７に当接
している。挿入溝内の羽根８Ａと羽根８Ｂとの間に羽根
押圧バネ５Ｃを配置し、圧縮された羽根押圧バネ５Ｃの
釈放力により羽根８Ａ，８Ｂがライナ７を押圧してシー
ル部を形成している。挿入溝５１とライナ７との間に配
置された羽根８Ａ，８Ｂを挾んでオイルを充填した複数
の部屋例えば高圧室７１及び低圧室７２を形成してい
る。高圧室内のオイル圧が低圧室を押圧して発生した衝
撃トルクにより出力軸５を回転駆動する。The oil pulse mechanism section 4 will be described with reference to FIGS. 1 and 2A and 2B. The output shaft 5 is rotatably supported in a liner 7 that is driven to rotate together with the electric motor 1,
Forming an insertion groove 51 penetrating in a direction perpendicular to the output shaft 5,
Two blades 8A and 8B are arranged in the insertion groove 51, and the two blades 8A and 8B extend in opposite directions and are in contact with the liner 7. A blade pressing spring 5C is arranged between the blade 8A and the blade 8B in the insertion groove, and the blades 8A and 8B press the liner 7 by the releasing force of the compressed blade pressing spring 5C to form a seal portion. . A plurality of chambers, for example, a high pressure chamber 71 and a low pressure chamber 72 filled with oil are formed by sandwiching the blades 8A and 8B arranged between the insertion groove 51 and the liner 7. The output shaft 5 is rotationally driven by the impact torque generated by the oil pressure in the high pressure chamber pressing the low pressure chamber.
【００１２】即ち、ライナ７には、内周面に山形状に突
出した４個のシール部が形成されており、このうち、羽
根８Ａ，８Ｂの先端が接してライナ７に形成した部屋内
をシールする２個のシール部は、相互に１８０°回転対
象となるように設定し、出力軸５の外周面に形成したシ
ール部５Ａ，５Ｂに接してライナ７に形成した空洞内を
シールする他の２個のシール部７Ａ，７Ｂは、２個のシ
ール部が相互に１８０°回転対象となる中間に、相互に
１８０°回転非対象となるように設定している。That is, the liner 7 is formed with four seal portions projecting in a mountain shape on the inner peripheral surface. Of these, the insides of the chamber formed in the liner 7 are in contact with the tips of the blades 8A and 8B. The two sealing parts to be sealed are set so as to be rotated by 180 ° with respect to each other, and contact with the sealing parts 5A and 5B formed on the outer peripheral surface of the output shaft 5 to seal the inside of the cavity formed in the liner 7. The two seal portions 7A and 7B are set so that the two seal portions are 180 ° to each other and 180 ° to each other, while the two seal portions are not to be rotated by 180 °.
【００１３】また、ライナ７内に同軸に配置した出力軸
５は、２個の羽根８Ａ，８Ｂを挿入溝５１内に配置する
と共に、相互に１８０°回転対象となるように設定し、
更に、外周面に山形状に突出した２個のシール部５Ａ，
５Ｂを２個の相互に１８０°回転対象となる羽根８Ａ，
８Ｂの中間にそれぞれ１８０°回転非対象となるように
形成し、かつ、ライナ７に形成した２個のシール部と接
してライナ７に形成した空洞をシールするように設定す
る。つまり、２個の羽根８Ａ，８Ｂ及びシール部７Ａ，
７Ｂと出力軸５及びライナ７との間に高圧室７１及び低
圧室７２を各２個づつ形成している。The output shaft 5 coaxially arranged in the liner 7 has two blades 8A and 8B arranged in the insertion groove 51 and is set so as to be rotated by 180 ° with respect to each other.
Further, two seal portions 5A protruding in a mountain shape on the outer peripheral surface,
5B, two blades 8A that are to be rotated by 180 ° with respect to each other,
It is formed in the middle of 8B so as not to be rotated by 180 °, and is set so as to contact the two seal portions formed in the liner 7 to seal the cavity formed in the liner 7. That is, the two blades 8A, 8B and the seal portion 7A,
Two high pressure chambers 71 and two low pressure chambers 72 are formed between 7B and the output shaft 5 and the liner 7.
【００１４】これにより、電動モータ１にてライナ７を
回転駆動することにより、ライナ７のシール部７Ｃ，７
Ｄと出力軸５の羽根８Ａ，８Ｂの先端が合致し、ライナ
７のシール部７Ａ，７Ｂと出力軸５のシール部５Ａ，５
Ｂが合致した時、ライナ７に形成した空洞は図２（Ａ）
のように高圧室７１と低圧室７２の４室に分割され、ラ
イナ７の出力軸５に対する相対的な１回転に対し、出力
軸５に１回の間欠的な衝撃トルクを発生することができ
る。ただし、高圧室７１は、挿入溝５１により連通され
ている。As a result, by rotating the liner 7 by the electric motor 1, the seal portions 7C, 7C of the liner 7 are driven.
D and the tips of the blades 8A, 8B of the output shaft 5 match, and the seal portions 7A, 7B of the liner 7 and the seal portions 5A, 5 of the output shaft 5
When B is matched, the cavity formed in the liner 7 is shown in FIG. 2 (A).
As described above, the high pressure chamber 71 and the low pressure chamber 72 are divided into four chambers, and an intermittent impact torque can be generated once on the output shaft 5 for one rotation relative to the output shaft 5 of the liner 7. . However, the high pressure chamber 71 is communicated with the insertion groove 51.
【００１５】また、図２（Ｂ）のように電動モータ１を
逆転した時も、同じくライナ７の出力軸５に対する相対
的な１回転に対し、出力軸５に１回の間欠的な衝撃トル
クを発生することができる。この衝撃トルクを緩和する
ために、本発明のオイルパルス機構部４は、衝撃トルク
の大きさを調整するための出力調整機構４１を配設して
いる。Also, when the electric motor 1 is rotated in the reverse direction as shown in FIG. 2 (B), the output shaft 5 is intermittently impacted once per one rotation relative to the output shaft 5 of the liner 7. Can occur. In order to reduce the impact torque, the oil pulse mechanism unit 4 of the present invention is provided with an output adjusting mechanism 41 for adjusting the magnitude of the impact torque.
【００１６】図３は本発明による出力調整機構４１の断
面図を示す。ライナ７に高圧室７１と低圧室７２を連絡
するように連通路９を設け、連通路９内にはピストン型
開閉弁１０、弾性手段であるスプリング１１、バルブ１
２を内蔵し構成されている。連通路９はシール部７Ａ，
７Ｂを設けたライナ７の肉厚の箇所に設けることによ
り、連通路９の形成作業が容易に出来る。FIG. 3 is a sectional view of the output adjusting mechanism 41 according to the present invention. A communication passage 9 is provided in the liner 7 so as to connect the high pressure chamber 71 and the low pressure chamber 72. Inside the communication passage 9, a piston-type on-off valve 10, a spring 11 serving as an elastic means, and a valve 1 are provided.
2 is built in and configured. The communication passage 9 has a seal portion 7A,
By providing the liner 7B at a thick portion of the liner 7, the work of forming the communication passage 9 can be facilitated.
【００１７】出力軸５が回転して羽根８Ａ，８Ｂがオイ
ルをシール部７Ｃ，７Ｄに押圧すると、オイルを圧縮さ
れた高圧室７１と高圧室７１より圧力の低い低圧室７２
とが形成される。高圧室７１の圧力は、高圧室側の連通
路口９１からの圧力により連通路９に押し出されたオイ
ルが流入し、ピストン型開閉弁１０に高圧室７１からの
圧力を伝達し、ピストン型開閉弁１０はスプリング１１
を圧縮しながら移動し、低圧室側連通路口９２から低圧
室７２内へオイルを流出させ、高圧室７１側の高いピー
ク圧力を低下させる。When the output shaft 5 rotates and the blades 8A, 8B press the oil against the seal portions 7C, 7D, the high pressure chamber 71 compressed with the oil and the low pressure chamber 72 lower in pressure than the high pressure chamber 71.
And are formed. As for the pressure in the high pressure chamber 71, the oil pushed out into the communication passage 9 by the pressure from the communication passage port 91 on the high pressure chamber side flows in, the pressure from the high pressure chamber 71 is transmitted to the piston type opening / closing valve 10, and the piston type opening / closing valve is opened. 10 is a spring 11
Is moved while being compressed, oil is caused to flow out from the low pressure chamber side communication passage port 92 into the low pressure chamber 72, and the high peak pressure on the high pressure chamber 71 side is reduced.
【００１８】この間にスプリング１１は圧縮エネルギー
を蓄積する。蓄積された圧縮エネルギーの方が高圧室側
のオイル圧より大きくなると、圧縮エネルギーが釈放さ
れ、この釈放力によりピストン型開閉弁１０、スプリン
グ１１、バルブ１２は元の位置に戻される。During this time, the spring 11 accumulates compression energy. When the accumulated compression energy becomes larger than the oil pressure on the high pressure chamber side, the compression energy is released, and the release force returns the piston-type on-off valve 10, the spring 11 and the valve 12 to their original positions.
【００１９】このように、スプリング１１の圧縮力と連
通路口９２の開放量とを設定し、高圧室７１内で発生す
る圧力に対してピストン型開閉弁１０の移動に伴う高圧
室側連通路口９２の開放量を調整することができるた
め、ボルト締付時に発生する圧力に合わせることで、ボ
ルト締付時のみ高いピーク圧力を連通路９により低下さ
せ、オイル洩れ発生を防ぐことが出来ると共に、オイル
洩れ発生による締付トルクの低下を抑えることができ
る。つまり、スプリング１１の圧縮力と連通路口９２の
開放量とを調整しオイル洩れが生じないように設定す
る。As described above, the compression force of the spring 11 and the opening amount of the communication passage port 92 are set, and the high pressure chamber side communication passage port 92 accompanying the movement of the piston type opening / closing valve 10 with respect to the pressure generated in the high pressure chamber 71 is set. Since it is possible to adjust the opening amount of the oil, by adjusting it to the pressure generated when the bolt is tightened, the high peak pressure can be reduced by the communication passage 9 only when the bolt is tightened, and the oil leakage can be prevented and the oil leakage can be prevented. It is possible to suppress a decrease in tightening torque due to the occurrence of leakage. That is, the compression force of the spring 11 and the opening amount of the communication passage port 92 are adjusted so as to prevent oil leakage.
【００２０】図４は、ピストン型開閉弁１０をバルブ１
２に圧接しているスプリング１１をバルブ１２側に配設
した実施例であり、この場合、高圧室側連通路口９２を
ピストン型開閉弁１０の後方に設置することで、図３の
実施例とは逆方向にピストン型開閉弁１０を動作するよ
うに構成し高いピーク圧力を低下させる。FIG. 4 shows a piston type on-off valve 10 with a valve 1.
This is an embodiment in which the spring 11 in pressure contact with 2 is arranged on the valve 12 side. In this case, by installing the high pressure chamber side communication passage port 92 behind the piston type on-off valve 10, the embodiment shown in FIG. Is configured to operate the piston-type on-off valve 10 in the opposite direction to reduce the high peak pressure.
【００２１】また、バルブ１２を移動させるための調整
ネジ１３を配設することにより、スプリング１１のセッ
ト時のたわみ量の調整が可能となり、調整ネジ１３を回
し荷重を変更することで、高圧室７１内で発生する圧力
に対してピストン型開閉弁１０の移動に伴う高圧室側連
通路口９２の開放量を調整することができるため、作業
内容に合わせて本機構の効果を容易に調整することがで
きる。Further, by disposing the adjusting screw 13 for moving the valve 12, it becomes possible to adjust the amount of deflection when the spring 11 is set, and by rotating the adjusting screw 13 to change the load, the high pressure chamber can be changed. Since the opening amount of the high pressure chamber side communication passage port 92 accompanying the movement of the piston type opening / closing valve 10 can be adjusted with respect to the pressure generated in 71, the effect of this mechanism can be easily adjusted according to the work content. You can
【００２２】図５は、図４のスプリング１１に替えて中
空の弾性体１４例えばゴム，弾性金属板を使用した場合
であり、同じく高いピーク圧力を低下させることができ
る。FIG. 5 shows a case where a hollow elastic body 14 such as a rubber or elastic metal plate is used in place of the spring 11 shown in FIG. 4, and a high peak pressure can be similarly reduced.
【００２３】図６は、バルブ１２の本体に連通路９を形
成した実施例である。ライナ７に高圧室７１と低圧室７
２を連絡するように連通路９を設け、高圧室側連通路口
９１に合わせてバルブ１２本体にも連通路９を形成し、
図３にあるピストン型開閉弁１０に替えてスチールボー
ル弁１５とし、前記スチールボール弁１５をバルブ１２
に圧接するためのスプリングガイド１６及びスプリング
１１にて構成することにより、片当りを避けるためにス
チールボール弁１５とスプリングガイド１６の曲率部１
６Ａとの接触状態を良くした。FIG. 6 shows an embodiment in which the communication passage 9 is formed in the main body of the valve 12. The liner 7 has a high pressure chamber 71 and a low pressure chamber 7.
The communication passage 9 is provided so as to connect the two, and the communication passage 9 is also formed in the valve 12 main body in accordance with the high pressure chamber side communication passage opening 91.
A steel ball valve 15 is used in place of the piston type on-off valve 10 shown in FIG.
The spring guide 16 and the spring 11 for press-contacting the steel ball valve 15 and the curvature portion 1 of the spring guide 16 are provided to avoid uneven contact.
The state of contact with 6A was improved.
【００２４】図３の実施例と同じく、ライナ７のシール
部と出力軸５の羽根８の先端が合致し、ライナ７のシー
ル部と出力軸５のシール部が合致し高圧室７１と低圧室
７２が形成され圧力が発生した時、高圧室側連通路口９
１から圧力により押し出されたオイルが流入し、バルブ
１２の連通路９を通過し、スチールボール弁１５に圧力
を伝達し、チールボール弁１５をバルブ１２に圧接させ
ているスプリング１１の荷重を超えると、スチールボー
ル弁１５が移動し、低圧室側連通路口９２から低圧室７
２内へオイルを流出させ、高圧室７１の高いピーク圧力
を低下させる。As in the embodiment of FIG. 3, the seal portion of the liner 7 and the tip of the blade 8 of the output shaft 5 are aligned with each other, the seal portion of the liner 7 and the seal portion of the output shaft 5 are aligned with each other, and the high pressure chamber 71 and the low pressure chamber 71 are aligned. When 72 is formed and pressure is generated, the high pressure chamber side communication passage port 9
The oil pushed out by the pressure from 1 flows in, passes through the communication passage 9 of the valve 12, transmits the pressure to the steel ball valve 15, and exceeds the load of the spring 11 that presses the steel ball valve 15 against the valve 12. When the steel ball valve 15 moves, the low pressure chamber side communication passage port 92 moves to the low pressure chamber 7
The oil is caused to flow out into the high pressure chamber 71 and the high peak pressure of the high pressure chamber 71 is reduced.
【００２５】また、バルブ１２を移動させるための調整
ネジ１３を配設することにより、図４の実施例と同じく
本機構の効果を容易に調整することができ、更にバルブ
１２本体にも連通路９を設けているため、バルブ１２の
移動に伴う高圧室側連通路口９１の開放量でオイルの流
量調整が可能となり、スプリング１１の荷重調整と合わ
せて細かい出力調整が可能となる。Further, by providing the adjusting screw 13 for moving the valve 12, the effect of the present mechanism can be easily adjusted as in the embodiment of FIG. Since the valve 9 is provided, the flow rate of oil can be adjusted by the opening amount of the high pressure chamber side communication passage opening 91 associated with the movement of the valve 12, and fine output adjustment can be performed together with the load adjustment of the spring 11.
【００２６】図３から図６までの実施例は、電動モータ
１によるライナ７の回転駆動方向が正転時のみ動作（連
通路口の高圧室７１側と低圧室７２側の位置を逆に構成
すれば逆転時のみ動作も可能）となっているが、図７は
正転時、逆転時とも動作可能とした実施例である。In the embodiment shown in FIGS. 3 to 6, the liner 7 is operated only when the electric motor 1 rotates in the forward direction (the high pressure chamber 71 side and the low pressure chamber 72 side of the communication passage port may be arranged in reverse positions). However, FIG. 7 shows an embodiment in which operation is possible both in forward rotation and in reverse rotation.
【００２７】連通路９内にはピストン型開閉弁１０、バ
ルブ１２、スプリング１７，１８はピストン型開閉弁１
０の両端に配設し、連通路口は、図７（Ａ）のように高
圧室側連通路口９３、低圧室側連通路口９４、高圧室側
連通路口９５、低圧室側連通路口９６と交互に２ヵ所ず
つ計４ヵ所配設する（高圧室側連通路口、低圧室側連通
路口の位置は交互に配設されれば逆順でも可）。The piston type on-off valve 10, the valve 12, and the springs 17 and 18 are provided in the communication passage 9 by the piston type on-off valve 1.
7 and the communication passage ports are alternately the high pressure chamber side communication passage port 93, the low pressure chamber side communication passage port 94, the high pressure chamber side communication passage port 95, and the low pressure chamber side communication passage port 96 as shown in FIG. 7 (A). A total of four locations are provided for each two locations (the high-pressure chamber side communication passage openings and low-pressure chamber side communication passage openings can be placed in reverse order if they are arranged alternately).
【００２８】ピストン型開閉弁１０は、圧力が発生して
いない通常状態では常に中央の２ヵ所の連通路口９１，
９２を塞ぐように設定し、高圧室７１と低圧室７２が形
成され圧力が発生した時は高圧室側連通路口９３よりオ
イルが流入しピストン型開閉弁１０がスプリング１８を
圧縮して移動し、低圧室側連通路口９４から低圧室７２
内へオイルを流出させ、高圧室７１の高いピーク圧力を
低下させる。The piston-type on-off valve 10 has two communication passage ports 91, which are located at the center in the normal state where no pressure is generated.
When the high pressure chamber 71 and the low pressure chamber 72 are formed and pressure is generated, oil flows in from the high pressure chamber side communication passage port 93, the piston type on-off valve 10 compresses the spring 18 and moves, From the low-pressure chamber side communication passage port 94 to the low-pressure chamber 72
The oil is made to flow in, and the high peak pressure of the high pressure chamber 71 is lowered.
【００２９】逆転時は、図２（Ｂ）にあるように高圧室
７１と低圧室７２の構成が逆に入れ替わるため、連通路
口は図７（Ａ）の状態から図７（Ｂ）の状態になる。従
って、高圧室７１と低圧室７２が形成され圧力が発生し
た時は高圧室側連通路口９５からオイルが流入し、ピス
トン型開閉弁１０がスプリング１７を圧縮して移動し、
低圧室側連通路口９６から低圧室７２内へオイルを流出
させ、正転時と同様の効果が得られる。At the time of reverse rotation, the high pressure chamber 71 and the low pressure chamber 72 are reversed in configuration as shown in FIG. 2B, so that the communication passage port changes from the state of FIG. 7A to the state of FIG. 7B. Become. Therefore, when the high pressure chamber 71 and the low pressure chamber 72 are formed and pressure is generated, oil flows in from the high pressure chamber side communication passage port 95, the piston type opening / closing valve 10 compresses the spring 17 and moves,
The oil is caused to flow from the low pressure chamber side communication passage port 96 into the low pressure chamber 72, and the same effect as in the normal rotation can be obtained.
【００３０】また、バルブ１２を移動させるための調整
ネジ１３を配設することにより、図４の実施例と同じく
本機構の効果を容易に調整することができる。Further, by providing the adjusting screw 13 for moving the valve 12, the effect of this mechanism can be easily adjusted as in the embodiment of FIG.
【００３１】[0031]
【発明の効果】以上のように、本発明の電動油圧式締結
工具によれば、高いピーク圧力によるオイル洩れを軽減
し、締付トルクの低下を抑えることができるようになっ
た。As described above, according to the electrohydraulic fastening tool of the present invention, oil leakage due to high peak pressure can be reduced and the tightening torque can be prevented from lowering.
【図１】本発明の実施例として示した電動油圧式締結工
具の要部断面図である。FIG. 1 is a sectional view of essential parts of an electrohydraulic fastening tool shown as an embodiment of the present invention.
【図２】図１のオイルパルス機構部の正転時（Ａ）及び
逆転時（Ｂ）を示す横断面図である。FIG. 2 is a cross-sectional view showing a forward rotation (A) and a reverse rotation (B) of the oil pulse mechanism portion of FIG.
【図３】図１に使用した出力調整機構の断面図である。FIG. 3 is a cross-sectional view of the output adjusting mechanism used in FIG.
【図４】本発明による他の実施例を示す出力調整機構の
断面図である。FIG. 4 is a sectional view of an output adjusting mechanism showing another embodiment according to the present invention.
【図５】本発明による他の実施例を示す出力調整機構の
断面図である。FIG. 5 is a sectional view of an output adjusting mechanism showing another embodiment according to the present invention.
【図６】本発明による他の実施例を示す出力調整機構の
断面図である。FIG. 6 is a sectional view of an output adjusting mechanism showing another embodiment according to the present invention.
【図７】本発明による他の実施例を示す出力調整機構の
正転時（Ａ）及び逆転時（Ｂ）の断面図である。FIG. 7 is a cross-sectional view of an output adjusting mechanism according to another embodiment of the present invention during normal rotation (A) and reverse rotation (B).
１…電動モータ、２…ハウジング、３…遊星歯車機構
部、４…オイルパルス機構部、５…出力軸、５Ｃ…羽根
押圧バネ、６…ハンマケース、７…ライナ、８，８Ａ，
８Ｂ…羽根、９…連通路、１０…ピストン型開閉弁、１
１…スプリング、１２…バルブ、１３…調整ネジ、１４
…弾性体、１５…スチールボール弁、１６…スプリング
ガイド、１７…スプリング、１８…スプリング、３１…
ピニオン、４１…出力調整機構、５１…挿入溝、７１…
高圧室、７２…低圧室、９１…高圧室側連通路口、９２
…低圧室側連通路口、９３…高圧室側連通路口、９４…
低圧室側連通路口、９５…高圧室側連通路口、９６…低
圧室側連通路口。DESCRIPTION OF SYMBOLS 1 ... Electric motor, 2 ... Housing, 3 ... Planetary gear mechanism part, 4 ... Oil pulse mechanism part, 5 ... Output shaft, 5C ... Blade pressing spring, 6 ... Hammer case, 7 ... Liner, 8, 8A,
8B ... Blade, 9 ... Communication passage, 10 ... Piston type on-off valve, 1
1 ... Spring, 12 ... Valve, 13 ... Adjustment screw, 14
... Elastic body, 15 ... Steel ball valve, 16 ... Spring guide, 17 ... Spring, 18 ... Spring, 31 ...
Pinion, 41 ... Output adjustment mechanism, 51 ... Insertion groove, 71 ...
High pressure chamber, 72 ... Low pressure chamber, 91 ... High pressure chamber side communication passage port, 92
... Low pressure chamber side communication passage port, 93 ... High pressure chamber side communication passage port, 94 ...
Low pressure chamber side communication passage port, 95 ... High pressure chamber side communication passage port, 96 ... Low pressure chamber side communication passage port.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 斎藤 四郎 大阪府東大阪市西岩田３丁目５番55号 ヨ コタ工業株式会社内 Ｆターム(参考） 3C038 AA01 BC04 CA03 CA04 CB03 CB04 CC03 EA01 EA03 EA06 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Shiro Saito 3-5-55, Nishi-Iwata, Higashi-Osaka City, Osaka Prefecture Kota Industry Co., Ltd. F-term (reference) 3C038 AA01 BC04 CA03 CA04 CB03 CB04 CC03 EA01 EA03 EA06
Claims (4)
と、前記ライナ内に回転自在に支持された出力軸と、前
記出力軸に形成された前記出力軸の直角方向に対して貫
通する挿入溝と、前記挿入溝と前記ライナとの間に配置
された羽根を挾んで形成されたオイルを有する複数の室
と、前記ライナを回転駆動して前記オイルを圧縮して前
記複数の室の少なくとも１つに形成した高圧室とを備
え、前記高圧室内のオイル圧が羽根を押圧して発生した
衝撃トルクにより前記出力軸を駆動するオイルパルス機
構において、前記高圧室と前記低圧室との間に前記高圧
室のオイル圧を前記低圧室に逃がす圧力緩和手段を設け
ることを特徴とする電動油圧式締結工具。1. A liner that is driven to rotate together with an electric motor, an output shaft that is rotatably supported in the liner, and an insertion groove that is formed in the output shaft and that penetrates in a direction perpendicular to the output shaft. A plurality of chambers having oil formed by sandwiching blades arranged between the insertion groove and the liner, and rotationally driving the liner to compress the oil to at least one of the plurality of chambers. A high pressure chamber formed between the high pressure chamber and the low pressure chamber, wherein the oil pressure mechanism drives the output shaft by an impact torque generated by the oil pressure in the high pressure chamber pressing a blade. An electrohydraulic fastening tool, characterized in that a pressure relief means is provided for releasing the oil pressure of 1. to the low pressure chamber.
室との間を連通路で連絡し、前記連通路内に開閉弁及び
弾性手段を配置し、前記高圧室からオイル圧により開閉
弁が弾性手段を圧縮しながら前記低圧室と連通した連通
路に前記オイル圧を逃がし、前記オイル圧より弾性手段
の圧縮力が大きくなると、前記圧縮力により前記開閉弁
を元の位置に戻すようにしたことを特徴とする請求項１
に記載の電動油圧式締結工具。2. The pressure easing means connects the high pressure chamber and the low pressure chamber with a communication passage, and an opening / closing valve and an elastic means are arranged in the communication passage, and the opening / closing valve is operated by oil pressure from the high pressure chamber. Releases the oil pressure to the communication passage communicating with the low pressure chamber while compressing the elastic means, and when the compression force of the elastic means becomes larger than the oil pressure, the compression force causes the on-off valve to return to its original position. Claim 1 characterized in that
The electro-hydraulic fastening tool described in.
と、前記ライナ内に回転自在に支持された出力軸と、前
記出力軸に形成された前記出力軸の直角方向に対して貫
通する挿入溝と、前記挿入溝と前記ライナとの間に配置
された羽根を挾んで形成されたオイルを有する複数の室
と、前記ライナを回転駆動して前記オイルを圧縮して前
記複数の室の少なくとも１つに形成した高圧室とを備
え、前記高圧室内のオイル圧が羽根を押圧して発生した
衝撃トルクにより、前記出力軸を正転駆動及び逆転駆動
して被締結物を締め付け及び締め外すオイルパルス機構
において、前記高圧室と前記低圧室との間を複数の連通
路により連絡し、前記連通路内の各々に開閉弁及び弾性
手段を配置し、正転時には前記高圧室からオイル圧によ
り開閉弁が弾性手段を圧縮しながら前記低圧室と連通し
た連通路に前記オイル圧を逃がし、逆転時には前記正転
時とは逆に前記高圧室を前記低圧室に前記低圧室を高圧
室にして前記オイル圧を逃がすことを特徴とする電動油
圧式締結工具。3. A liner rotatably driven together with an electric motor, an output shaft rotatably supported in the liner, and an insertion groove formed in the output shaft and penetrating in a direction perpendicular to the output shaft. A plurality of chambers having oil formed by sandwiching blades arranged between the insertion groove and the liner, and rotationally driving the liner to compress the oil to at least one of the plurality of chambers. An oil pulse mechanism comprising a high pressure chamber formed, wherein the output shaft is driven to rotate in the normal direction and reversely driven by the impact torque generated by the oil pressure in the high pressure chamber to tighten and unfasten the object to be fastened. , The high pressure chamber and the low pressure chamber are connected by a plurality of communication passages, and an on-off valve and elastic means are arranged in each of the communication passages. Pressure means Releasing the oil pressure to the communication passage communicating with the low pressure chamber while contracting, and making the high pressure chamber to be the low pressure chamber and the low pressure chamber to be the high pressure chamber to reverse the oil pressure at the time of reverse rotation, contrary to the forward rotation. An electro-hydraulic fastening tool characterized by.
整する調整手段を設けることを特徴とする請求項２又は
３に記載の電動油圧式締結工具。4. The electro-hydraulic fastening tool according to claim 2, wherein the communication passage is provided with adjusting means for adjusting the elastic force of the elastic means.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001235939A JP4820027B2 (en) | 2001-08-03 | 2001-08-03 | Electro-hydraulic fastening tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001235939A JP4820027B2 (en) | 2001-08-03 | 2001-08-03 | Electro-hydraulic fastening tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003039341A true JP2003039341A (en) | 2003-02-13 |
| JP4820027B2 JP4820027B2 (en) | 2011-11-24 |
Family
ID=19067298
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001235939A Expired - Lifetime JP4820027B2 (en) | 2001-08-03 | 2001-08-03 | Electro-hydraulic fastening tool |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4820027B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009255290A (en) * | 2007-09-11 | 2009-11-05 | Uryu Seisaku Ltd | Impact torque adjustment device of hydraulic torque wrench |
| JP2010269427A (en) * | 2009-05-22 | 2010-12-02 | Hitachi Koki Co Ltd | Oil pulse tool |
| JP2012055989A (en) * | 2010-09-07 | 2012-03-22 | Uryu Seisaku Ltd | Impact torque adjusting device of hydraulic torque wrench |
| WO2012091172A1 (en) | 2010-12-28 | 2012-07-05 | Hitachi Koki Co., Ltd. | Driving tool |
| JP2014079856A (en) * | 2012-10-17 | 2014-05-08 | Nitto Kohki Co Ltd | Oil rotation impact force generator |
| JP2017042839A (en) * | 2015-08-24 | 2017-03-02 | 株式会社マキタ | Rotary impact tool |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6102191B2 (en) * | 2012-11-07 | 2017-03-29 | マックス株式会社 | Pressure relief mechanism of oil pulse tool |
| JP6145993B2 (en) * | 2012-11-07 | 2017-06-14 | マックス株式会社 | Oil pulse tool |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5959356A (en) * | 1982-09-22 | 1984-04-05 | 日本ニユ−マチツク工業株式会社 | Torque wrench |
| JP2000079572A (en) * | 1998-09-01 | 2000-03-21 | Nippon Pneumatic Mfg Co Ltd | Hydraulic pulse wrench |
-
2001
- 2001-08-03 JP JP2001235939A patent/JP4820027B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5959356A (en) * | 1982-09-22 | 1984-04-05 | 日本ニユ−マチツク工業株式会社 | Torque wrench |
| JP2000079572A (en) * | 1998-09-01 | 2000-03-21 | Nippon Pneumatic Mfg Co Ltd | Hydraulic pulse wrench |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009255290A (en) * | 2007-09-11 | 2009-11-05 | Uryu Seisaku Ltd | Impact torque adjustment device of hydraulic torque wrench |
| JP2010269427A (en) * | 2009-05-22 | 2010-12-02 | Hitachi Koki Co Ltd | Oil pulse tool |
| JP2012055989A (en) * | 2010-09-07 | 2012-03-22 | Uryu Seisaku Ltd | Impact torque adjusting device of hydraulic torque wrench |
| WO2012091172A1 (en) | 2010-12-28 | 2012-07-05 | Hitachi Koki Co., Ltd. | Driving tool |
| JP2014079856A (en) * | 2012-10-17 | 2014-05-08 | Nitto Kohki Co Ltd | Oil rotation impact force generator |
| JP2017042839A (en) * | 2015-08-24 | 2017-03-02 | 株式会社マキタ | Rotary impact tool |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4820027B2 (en) | 2011-11-24 |
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