JPS62193780A - Driving blade for hydraulic wrench - Google Patents
Driving blade for hydraulic wrenchInfo
- Publication number
- JPS62193780A JPS62193780A JP61035679A JP3567986A JPS62193780A JP S62193780 A JPS62193780 A JP S62193780A JP 61035679 A JP61035679 A JP 61035679A JP 3567986 A JP3567986 A JP 3567986A JP S62193780 A JPS62193780 A JP S62193780A
- Authority
- JP
- Japan
- Prior art keywords
- liner
- driving blade
- main shaft
- hydraulic
- roller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000010720 hydraulic oil Substances 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 239000003921 oil Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000008961 swelling Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
- B25B21/026—Impact clutches
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は油圧レンチに備えるドライビングブレードの改
良に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an improvement in a driving blade provided in a hydraulic wrench.
［従来技術とその問題点］
油圧レンチは高圧空気により高速回転されるライナーの
偏心空洞に主軸の膨み部を嵌合し、主軸の膨み部に刳取
った凹所にドライビングブレードをばねと共に嵌挿し、
ライナーに充填した作動油の圧力変化（油圧パルス）に
より主軸に締付はトルクを発生するもので、すでに種々
の提案（特公昭４０−２０６３３号、同４１−５８００
号）がなされている。しかし従来の油圧レンチは作動油
を充填密封したるライナー内を高圧部と低圧部とにシー
ルするため主軸内に嵌挿されたばね圧により前記ドライ
ビングブレードの先端が直接ライナー内周面に圧接され
ている。従ってこの主軸は無負荷あるいは、ある程度の
負荷に達するまではライナーの回動により主軸はライナ
ー内面とドライビングブレードの抵抗によりライナーと
ともに等速もしくはほぼ等しい回転数で回動している。[Prior art and its problems] A hydraulic wrench fits the bulge of the main shaft into the eccentric cavity of a liner that is rotated at high speed by high-pressure air, and inserts the driving blade together with a spring into the recess cut out in the bulge of the main shaft. Insert,
Tightening generates torque on the main shaft due to pressure changes (hydraulic pulses) in the hydraulic oil filled in the liner, and various proposals have already been made (Japanese Patent Publications No. 40-20633, No. 41-5800).
No.) has been carried out. However, in conventional hydraulic wrenches, the tip of the driving blade is pressed directly against the inner peripheral surface of the liner by the spring pressure inserted into the main shaft in order to seal the high-pressure part and the low-pressure part in the liner, which is filled with hydraulic oil and sealed. There is. Therefore, the main shaft is unloaded or until a certain level of load is reached, due to the rotation of the liner, the main shaft rotates together with the liner at a constant speed or approximately the same rotational speed due to the resistance of the inner surface of the liner and the driving blade.
このときドライビングブレードとライナーとは摺擦する
ことはない。しかしねじ締付作業等に於て、ナツトやボ
ルトが締付体に着座する場合のように、主軸にある程度
の負荷がかかると、主軸は停止せんとするがライナーは
ロータの力で回転をつづけるため、主軸とライナーとの
間に急激な回転数差が生じて主軸は低速又は停止状態と
なってライナー内にてパルスが発生すると同時に、高速
回転するライナーはこれと圧接されたドライビングブレ
ード先端面を摺擦するものとなって摩擦熱が発生する。At this time, there is no rubbing between the driving blade and the liner. However, when a certain amount of load is applied to the main shaft during screw tightening work, such as when a nut or bolt is seated on a tightening body, the main shaft tries to stop, but the liner continues to rotate due to the force of the rotor. As a result, a sudden difference in rotational speed occurs between the main shaft and the liner, causing the main shaft to slow down or stop, generating pulses in the liner, and at the same time, the high-speed rotating liner is pressed against the driving blade tip surface. frictional heat is generated.
この発熱はライナー内の作動油温度を、その使用前のそ
れと比べて上昇させることになる。This heat generation causes the temperature of the hydraulic fluid in the liner to rise compared to that before its use.
作動油温度が上昇すると当然オイル粘度及び熱膨張によ
る体積が変化し、ライナー室で発生するパルスの力とそ
の数を減少させ、またドライビングブレード先端面の摺
擦によりドライビングブレード先端が摩耗し、その寿命
を著しく損うものとなっている。さらに作動油温度の上
昇が繰り返し行われるとこの油の劣化をきたすものとな
る。As the hydraulic oil temperature rises, the oil viscosity and volume change due to thermal expansion, which reduces the force and number of pulses generated in the liner chamber, and also causes the driving blade tip to wear out due to friction on the driving blade tip surface. This significantly reduces lifespan. Furthermore, if the temperature of the hydraulic oil is repeatedly increased, this oil will deteriorate.
本発明は上述のような問題点を解決した油圧レンチのド
ライビングブレードを提供することを目的とする。An object of the present invention is to provide a driving blade for a hydraulic wrench that solves the above-mentioned problems.
［問題点の解決手段］
本発明は高圧空気により高速回転されるライナーの偏心
空洞に主軸の膨み部を嵌合し、主軸の膨み部に剖取った
凹所にドライビングブレードをばねと共に嵌挿し、ライ
ナー空洞内に充填した作動油の圧力変化により主軸に締
付はトルクを発生する油圧レンチにおいて、ドライビン
グブレードの先端に凹溝を切り、この凹溝に回転自由に
嵌込んだコロをライナーの内周面に圧接させる。[Means for Solving Problems] The present invention fits the bulge of the main shaft into an eccentric cavity of a liner that is rotated at high speed by high-pressure air, and fits the driving blade together with a spring into the recess cut out in the bulge of the main shaft. A hydraulic wrench that generates tightening torque on the main shaft due to changes in the pressure of the hydraulic oil filled in the liner cavity. A groove is cut at the tip of the driving blade, and a roller fitted freely into this groove is inserted into the liner. Press it against the inner circumferential surface of the
［実施例］
図面の実施例において、１は油圧レンチの本体で、この
本体内に高圧空気の供給にて回動するロータ２を納め、
かつ本体後部の下側に握り３を一体に設ける。握り３は
その前面に、本体内もしくは握り内に設けた主バルブ（
図示なし）を開閉するバルブレバー４を有し、主バルブ
を介して供給される高圧空気によりロータ２を高速回転
させ、また切替レバー５によりロータ２の回転方向を切
替える。６は筒状のライナーで、本体１の前部に納めた
ケース７に遊嵌し、このライナー６内にその中心とある
距離偏心して空洞８を刺抜いてこの空洞８内に作動油を
充填密封する。１０は本体１の前面から突出する主軸で
、これの後部に形成した膨み部１１をライナー６に遊嵌
する。ライナー６に固定された後蓋１３をロータ２に連
結する。１４は側面よりみて凸字形をなすドライビング
ブレードで、主軸の膨み部１１に剖取った偏平な凹所１
５に２本のばね１Ｂ、 １Ｂと共に緩ろく嵌挿し、この
ばねの弾力により常にドライビングブレード１４の先端
を押出す。[Embodiment] In the embodiment shown in the drawings, 1 is a main body of a hydraulic wrench, and a rotor 2 that rotates by supplying high-pressure air is housed in the main body.
Moreover, a grip 3 is integrally provided on the lower side of the rear part of the main body. On the front side of the grip 3, there is a main valve (
The rotor 2 is rotated at high speed by high pressure air supplied through a main valve, and the rotation direction of the rotor 2 is switched by a switching lever 5. A cylindrical liner 6 is fitted loosely into a case 7 housed in the front part of the main body 1, and a cavity 8 is punched out at a certain distance from the center of the liner 6 to fill the cavity 8 with hydraulic oil. Seal. Reference numeral 10 denotes a main shaft protruding from the front surface of the main body 1, and a bulge 11 formed at the rear of the main shaft is loosely fitted into the liner 6. A rear lid 13 fixed to the liner 6 is connected to the rotor 2. Reference numeral 14 denotes a driving blade that has a convex shape when viewed from the side, and has a flat recess 1 cut into the bulge 11 of the main shaft.
5 along with two springs 1B and 1B, and the elasticity of these springs always pushes out the tip of the driving blade 14.
本実施例はこのような油圧レンチにおいて、第２図 （
Ａ）に示すようにドライビングブレード１４の先端に、
その全長にわたる凹溝１７を切り、この凹溝に同じ長さ
のコロ１８を回転自由に嵌込んでライナー６の内周面に
圧接させる。This embodiment uses such a hydraulic wrench as shown in Fig. 2 (
As shown in A), at the tip of the driving blade 14,
A groove 17 extending over the entire length of the liner 6 is cut, and a roller 18 of the same length is freely rotatably fitted into the groove and brought into pressure contact with the inner circumferential surface of the liner 6.
またこの凹溝１７とコロ１８は第２図（Ｂ）に示すよう
にドライビングブレードが少くとも常にライナー内空洞
の内周面と接する位置に於て、すなわちドライビングブ
レード側部の先端に凹溝１７ａ、 １７ｂを形成し、こ
の凹溝１７ａ、 １７ｂ内にコ口１８ａ、 １８ｂを回
動自在に嵌合することもできる。Further, as shown in FIG. 2(B), these grooves 17 and rollers 18 are formed at a position where the driving blade is at least always in contact with the inner circumferential surface of the liner inner cavity, that is, at the tip of the side of the driving blade. , 17b may be formed, and the sockets 18a, 18b may be rotatably fitted into the grooves 17a, 17b.
さらにこの凹溝１７は断面をＶ字形、Ｕ字形、半円形の
に形成することもできるが、図示のようにすることがで
きる。図示の凹溝１７はコロ１８を嵌合するときこのコ
ロ１８が回動し易いように、その断面形状及び深さが定
められているが、コロ１８の径はコロ径より若干大きい
幅を有する溝幅とローラ半径よりも大きく、かつライナ
ー外形に対して偏心したライナー内の偏心した空洞８内
を回動する場合、ライナー空洞内周面にドライビングブ
レードの一部が接触しないようにしてその深さを定める
と共に、コロが円滑に回動するよう凹溝内面とコロとの
接触面積を可及的に小となるようにしてその断面形を定
められる。望ましくは図に示すよう内隅角部を円形の四
角形とする。またこのドライビングブレードの凹溝１７
内に嵌挿されるコロ１８はドライビングブレード長とほ
ぼ等しくなるようにして定めるが、このコロ外周面及び
凹溝の内面は定められた精度を有するように仕上げ、ラ
イナー空洞内に充填され、かつライナーの回動時、この
ドライビングブレードにて瞬間的に高圧室側と低圧室側
に区分される場合、高圧室側の作動油が低圧室側へ漏れ
ないよう密閉されるようになす。Further, the groove 17 can have a V-shaped, U-shaped, or semicircular cross section, but it can also be formed as shown in the drawing. The illustrated concave groove 17 has a cross-sectional shape and depth determined so that the roller 18 can easily rotate when the roller 18 is fitted, but the diameter of the roller 18 has a width slightly larger than the roller diameter. When rotating in an eccentric cavity 8 in the liner that is larger than the groove width and roller radius and eccentric to the liner outer shape, the depth of the driving blade must be adjusted so that a part of the driving blade does not come into contact with the inner peripheral surface of the liner cavity. At the same time, the cross-sectional shape is determined so that the contact area between the inner surface of the groove and the roller is as small as possible so that the roller rotates smoothly. Preferably, the inner corner portions are circular quadrangles as shown in the figure. Also, the concave groove 17 of this driving blade
The roller 18 to be inserted into the liner is set to be approximately equal to the length of the driving blade, and the outer circumferential surface of the roller and the inner surface of the groove are finished to a specified precision, and the liner cavity is filled with the liner. When the driving blade momentarily divides the chamber into a high-pressure chamber and a low-pressure chamber when the chamber rotates, the hydraulic oil in the high-pressure chamber is sealed to prevent it from leaking to the low-pressure chamber.
第３図に示す如く主軸の膨み部１１は上部を三角形に作
り、主軸１０の回転に伴って三角部の頂縁（主軸の頂縁
という）１２がライナー６の内周面に可及的に接近し、
ドライビングブレード凹溝内のコロ１８が回転しつつラ
イナー６の内周面を移動する。ライナー６の内周面には
突縁２０，２１を相対して隆出させ、突縁の両側に作動
油を高圧室から低圧室へ逃がすための浅い凹み面を削取
る。こ＼に主軸の頂縁１２が突縁２０に対向するとき、
コロ１８は突縁２１に接しライナー６の内部に高圧室と
低圧室が瞬間的に形成され、このときコロ１８はばね１
８．１８により突縁２１に強く圧接してこの部分をシー
ルし、高圧室と低圧室を確実に区分する。As shown in FIG. 3, the bulge 11 of the main shaft has a triangular upper part, and as the main shaft 10 rotates, the top edge 12 of the triangular part (referred to as the top edge of the main shaft) reaches the inner peripheral surface of the liner 6 as much as possible. approach,
The roller 18 in the driving blade groove moves on the inner circumferential surface of the liner 6 while rotating. Projections 20 and 21 are protruded from the inner circumferential surface of the liner 6, and shallow concave surfaces are cut on both sides of the projections to allow hydraulic oil to escape from the high pressure chamber to the low pressure chamber. When the top edge 12 of the main shaft faces the protruding edge 20,
The rollers 18 are in contact with the ridge 21, and a high pressure chamber and a low pressure chamber are momentarily formed inside the liner 6. At this time, the rollers 18 are in contact with the spring 1.
8.18 strongly presses against the flange 21 to seal this portion and reliably separate the high pressure chamber and the low pressure chamber.
本発明の実施例は以上の構成からなり、第３図（Ａ）に
示す如く主軸の頂縁１２とドライビングブレードのコロ
１８がライナーの突縁２０．２１から離れているとき、
ライナー６の左右の両室６ａ１６ｂの作動油の圧力はは
ゾ同じである。この状態から偏心した空洞８を有するラ
イナー６が矢印方向に回転するとライナー空洞内の左側
室６ａの容積が次第に減少し、右側室６ｂの容積が次第
に増加し、これに伴って左側室６ａの作動油の油圧が次
第に上昇し、この油圧が主軸の膨み部１１とドライビン
グプレート１４の左側面に働き、主軸１０の中心線がラ
イナー６の中心線の１−側に偏心しているので、主軸１
０も左回転される。The embodiment of the present invention has the above configuration, and when the top edge 12 of the main shaft and the roller 18 of the driving blade are separated from the ridge 20, 21 of the liner as shown in FIG. 3(A),
The pressure of the hydraulic oil in both the left and right chambers 6a16b of the liner 6 is the same. When the liner 6 having the eccentric cavity 8 rotates in the direction of the arrow from this state, the volume of the left chamber 6a in the liner cavity gradually decreases, the volume of the right chamber 6b gradually increases, and the operation of the left chamber 6a is accompanied by this. The oil pressure gradually increases, and this oil pressure acts on the bulge 11 of the main shaft and the left side of the driving plate 14, and the center line of the main shaft 10 is eccentric to the 1- side of the center line of the liner 6, so the main shaft 1
0 is also rotated to the left.
続いて第３図（Ｂ）に示す如く主軸の頂縁１２がライナ
ーの突縁２０の位置にくると同時にドライビングブレー
ドのコロ１Ｂがライナーの突縁２１と接するので、瞬間
的に左側室６ａが高圧室となり、右側室６ａは低圧室と
なる。この高圧室と低圧室の形成によりライナー空洞内
の作動油に油圧パルスが発生し、油圧パルスは主軸１０
に締付はトルクを与えるので主軸に取付けたソケット（
図示なし）を介してボルトの締付けが行われる。Subsequently, as shown in FIG. 3(B), at the same time that the top edge 12 of the main shaft comes to the position of the liner's ridge 20, the roller 1B of the driving blade comes into contact with the liner's ridge 21, so that the left chamber 6a momentarily opens. The right chamber 6a becomes a high pressure chamber, and the right chamber 6a becomes a low pressure chamber. The formation of this high pressure chamber and low pressure chamber generates a hydraulic pulse in the hydraulic fluid in the liner cavity, and the hydraulic pulse is generated by the main shaft 10.
The socket attached to the main shaft (
(not shown), the bolts are tightened.
その後ライナー６がさらに回転し、第３図（Ｃ）に示す
如く主軸の頂縁１２とコロ１８がライナーの突縁２０．
２１から離れ、左側室６ａの作動油が凹み面２２．２２
により右側室６ｂへ流れ、左右の両室はほり同じ圧力と
なる。Thereafter, the liner 6 further rotates, and as shown in FIG.
21, and the hydraulic oil in the left chamber 6a is on the concave surface 22.22.
As a result, the air flows to the right chamber 6b, and both the left and right chambers have the same pressure.
前記ドライビングブレード１４は主軸の膨み部の凹所１
５に緩るく嵌挿されており、このためコロ１８が突縁２
１に接するとき空洞内の高圧室側でライナーの回動力に
て強い衝撃を生じ、この衝撃が油圧パルスの発生を助成
するが、従来のドライビングブレードはその先端をライ
ナー６の内周面に直接圧接させているから、ドライビン
グブレード２１の先端が突縁２１に接触するときの摺擦
力が激しく、このため摩耗し寿命が短かった。又従来の
ドライビングブレードはその先端がライナーの内周面を
摺擦しており、このため摩擦熱を発生して作動油の温度
を上昇させ、パルス数、力の低下、油を劣化させていた
。本実施例においてはドライビングブレード１４の先端
に凹溝１７を切ってコロ１８を嵌込み、このコロをライ
ナーの突縁２１に接触させるから、その際の衝撃が著る
しく緩和され、従ってドライビングブレードの寿命が長
くなる。又コロ１８がライナー６の内周面を転動するか
ら、摩擦熱を発生せず従って作動油が劣化しない。The driving blade 14 is located in the recess 1 in the bulge of the main shaft.
5, so that the roller 18 is inserted into the protrusion 2.
1, the rotating force of the liner generates a strong impact on the high-pressure chamber side of the cavity, and this impact assists in generating hydraulic pulses, but conventional driving blades do not directly touch the inner peripheral surface of the liner 6 with the tip of the driving blade. Since the driving blade 21 is in pressure contact, the sliding force when the tip of the driving blade 21 comes into contact with the protrusion 21 is intense, resulting in wear and a short life span. In addition, the tip of the conventional driving blade rubs against the inner peripheral surface of the liner, which generates frictional heat and increases the temperature of the hydraulic oil, reducing the number of pulses, reducing force, and deteriorating the oil. . In this embodiment, a concave groove 17 is cut at the tip of the driving blade 14 and a roller 18 is fitted into it, and this roller is brought into contact with the ridge 21 of the liner, so that the impact at that time is significantly alleviated, and therefore the driving blade has a longer lifespan. Furthermore, since the rollers 18 roll on the inner circumferential surface of the liner 6, no frictional heat is generated and therefore the hydraulic oil does not deteriorate.
以上は本発明の一実施例を説明したもので、本発明はこ
の実施例に限定されることな〈発明の要旨内において設
計変更でき、例えばドライビングブレード１４を２枚以
上に増やしてもよく、又本発明は油圧レンチのほか油圧
ベーンモータや油圧ベーンポンプにも適用しうる。The above describes one embodiment of the present invention, and the present invention is not limited to this embodiment. The design may be changed within the scope of the invention, for example, the number of driving blades 14 may be increased to two or more. Furthermore, the present invention can be applied not only to hydraulic wrenches but also to hydraulic vane motors and hydraulic vane pumps.
［発明の効果］
本発明によるときは油圧レンチにおいてドライビングブ
レードの先端に凹溝を設け、この凹溝に回転自由に嵌込
んだコロをライナーの内周面に圧接させており、このコ
ロをライナーの突縁に接触させるように構成したから、
ロータの回転力がスムーズにロスなく均一に主軸側（出
力側）に伝達されるので主軸の出力トルクが増加すると
共にライナーの回転数（パルス数）が増加し、かつ締付
トルクが増大する。さらにドライビングブレードの先端
部の摩耗が減少し、かつ摩擦熱が少いので作動油劣化防
止になる等の効果を有する。[Effects of the Invention] According to the present invention, a groove is provided at the tip of the driving blade in a hydraulic wrench, and a roller fitted into the groove so as to rotate freely is brought into pressure contact with the inner circumferential surface of the liner. Because it is configured so that it comes into contact with the ridge of
Since the rotational force of the rotor is smoothly and uniformly transmitted to the main shaft side (output side) without loss, the output torque of the main shaft increases, the number of rotations (number of pulses) of the liner increases, and the tightening torque increases. Furthermore, wear at the tip of the driving blade is reduced and frictional heat is small, which has the effect of preventing deterioration of the hydraulic oil.
第１図は本発明の一実施例を示す縦断面図、第２図はド
ライビングブレードとコロの拡大斜視図、第３図（Ａ）
〜（Ｃ）は動作の説明図である。
なお、６はライナー、８は空洞、１０は主軸、１１はそ
の膨み部、１４はドライビングブレード、１５は凹所、
１６はばね、１７は凹溝、１８はコロである。Fig. 1 is a longitudinal sectional view showing one embodiment of the present invention, Fig. 2 is an enlarged perspective view of the driving blade and roller, Fig. 3 (A)
-(C) are explanatory diagrams of the operation. In addition, 6 is a liner, 8 is a cavity, 10 is a main shaft, 11 is the swelling part, 14 is a driving blade, 15 is a recess,
16 is a spring, 17 is a groove, and 18 is a roller.
Claims (1)
軸の膨み部を嵌合し、主軸の膨み部に刳取った凹所にド
ライビングブレードをばねと共に嵌挿し、ライナーの中
心に対し偏心した空洞内に充填した作動油の圧力変化に
より主軸に締付けトルクを発生する油圧レンチにおいて
、ドライビングブレードの先端に凹溝を切り、この凹溝
に回転自由に嵌込んだコロをライナーの内周面に圧接さ
せたことを特徴とする油圧レンチのドライビングブレー
ド。The bulge of the main shaft is fitted into the eccentric cavity of the liner, which is rotated at high speed by high-pressure air, and the driving blade is fitted with a spring into the recess cut out in the bulge of the main shaft, and the cavity is eccentric to the center of the liner. In a hydraulic wrench that generates tightening torque on the main shaft due to changes in the pressure of hydraulic oil filled in the wrench, a groove is cut at the tip of the driving blade, and a roller fitted freely into the groove and pressed against the inner peripheral surface of the liner. The driving blade of the hydraulic wrench is characterized by:
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61035679A JPS62193780A (en) | 1986-02-19 | 1986-02-19 | Driving blade for hydraulic wrench |
| SE8604458A SE8604458L (en) | 1986-02-19 | 1986-10-20 | HYDRAULIC TIGHTENING DRIVE SHEET |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61035679A JPS62193780A (en) | 1986-02-19 | 1986-02-19 | Driving blade for hydraulic wrench |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62193780A true JPS62193780A (en) | 1987-08-25 |
Family
ID=12448569
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61035679A Pending JPS62193780A (en) | 1986-02-19 | 1986-02-19 | Driving blade for hydraulic wrench |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPS62193780A (en) |
| SE (1) | SE8604458L (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5113360A (en) * | 1989-10-31 | 1992-05-12 | Kabushiki Kaisha Toshiba | Portable apparatus with a structure to secure a printed circuit board to a base unit |
| JPH04109867U (en) * | 1991-03-07 | 1992-09-24 | 瓜生製作株式会社 | Torque control type impact wrench |
| JP2008254135A (en) * | 2007-04-06 | 2008-10-23 | Yokota Kogyo Kk | Hydraulic pulse generator |
| JP2010269424A (en) * | 2009-05-22 | 2010-12-02 | Hitachi Koki Co Ltd | Oil pulse tool |
| JP2019042919A (en) * | 2017-08-31 | 2019-03-22 | 瓜生製作株式会社 | Impact torque generator for hydraulic torque wrench |
-
1986
- 1986-02-19 JP JP61035679A patent/JPS62193780A/en active Pending
- 1986-10-20 SE SE8604458A patent/SE8604458L/en not_active Application Discontinuation
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5113360A (en) * | 1989-10-31 | 1992-05-12 | Kabushiki Kaisha Toshiba | Portable apparatus with a structure to secure a printed circuit board to a base unit |
| JPH04109867U (en) * | 1991-03-07 | 1992-09-24 | 瓜生製作株式会社 | Torque control type impact wrench |
| JP2008254135A (en) * | 2007-04-06 | 2008-10-23 | Yokota Kogyo Kk | Hydraulic pulse generator |
| JP2010269424A (en) * | 2009-05-22 | 2010-12-02 | Hitachi Koki Co Ltd | Oil pulse tool |
| JP2019042919A (en) * | 2017-08-31 | 2019-03-22 | 瓜生製作株式会社 | Impact torque generator for hydraulic torque wrench |
| TWI770255B (en) * | 2017-08-31 | 2022-07-11 | 日商瓜生製作股份有限公司 | Impact torque generator for hydraulic power wrench |
Also Published As
| Publication number | Publication date |
|---|---|
| SE8604458L (en) | 1987-08-20 |
| SE8604458D0 (en) | 1986-10-20 |
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