JP2779749B2 - Impact torque generator for hydraulic torque wrench - Google Patents
Impact torque generator for hydraulic torque wrenchInfo
- Publication number
- JP2779749B2 JP2779749B2 JP5104998A JP10499893A JP2779749B2 JP 2779749 B2 JP2779749 B2 JP 2779749B2 JP 5104998 A JP5104998 A JP 5104998A JP 10499893 A JP10499893 A JP 10499893A JP 2779749 B2 JP2779749 B2 JP 2779749B2
- Authority
- JP
- Japan
- Prior art keywords
- liner
- sealing surfaces
- main shaft
- blade
- sealing
- 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 - Fee Related
Links
Landscapes
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、３個以上の羽根を用い
ライナー１回転に１打撃を生じさせることにより油圧式
打撃トルク発生装置内の油圧を高めることなく安定した
高トルクを得られるようになした油圧式トルクレンチに
関するものである。BACKGROUND OF THE INVENTION The present invention is intended to obtain a stable high torque without increasing the oil pressure in a hydraulic impact torque generator by generating one impact per rotation of a liner by using three or more blades. The present invention relates to a hydraulic torque wrench.
【０００２】[0002]
【従来の技術】ニューマチックツールのトルクレンチに
おいては、ロータの回転力により機械的な方法で打撃力
を発生せしめ、これを利用して所望のトルクに変換して
いる。したがって、この機械的な方法で打撃トルクを得
る方式では、打撃音が大きく、騒音公害の起因ともな
り、また打撃による振動も大きかった。2. Description of the Related Art In a torque wrench of a pneumatic tool, a striking force is generated by a mechanical method by the rotational force of a rotor, and the torque is converted into a desired torque by using the striking force. Therefore, in the method of obtaining the impact torque by this mechanical method, the impact sound is loud, causing noise pollution, and the vibration due to the impact is also large.
【０００３】このため最近では、打撃トルクを得る方式
として油圧を用い、騒音と振動を防ぐ方式のトルクレン
チが有望視され、開発されている。ところで、油圧打撃
トルク発生装置として主軸に１個の羽根を設けたものや
複数、例えば特公昭４１ー５８００号公報に開示される
如く４個の羽根を設けたもの等があるが、前者の場合、
高トルクを得ようとすれば主軸を嵌挿した回転自在なラ
イナー内、すなわち打撃トルク発生装置の油圧が高くな
りシール機構がより精密かつ強固な構造になるとともに
羽根には主軸内周方向に片寄った圧力が働き、これによ
る主軸の片寄りにより出力の損失、トルクのバラツキ、
焼付等を生じるさせる欠点がある。また後者の場合、ラ
イナーの１回転に対し少なくとも２回の打撃が発生する
ため、ライナー及びケースの回転質量の慣性が少なく打
撃トルクが低くなる。[0003] Therefore, recently, a torque wrench of a type that uses oil pressure as a method for obtaining a percussive torque and that prevents noise and vibration has been considered promising and has been developed. By the way, as a hydraulic impact torque generating device, there is a device provided with one blade on a main shaft or a plurality of devices, for example, a device provided with four blades as disclosed in Japanese Patent Publication No. 41-5800. In the former case, ,
If a high torque is to be obtained, the hydraulic pressure of the impact torque generating device is increased in the rotatable liner in which the main shaft is inserted, and the sealing mechanism becomes more precise and strong, and the blades are biased in the main shaft inner circumferential direction. Pressure, which causes the spindle to be offset, causing loss of output, torque variation,
There is a disadvantage of causing seizure and the like. In the latter case, since at least two hits are generated per one rotation of the liner, the inertia of the rotational mass of the liner and the case is small, and the hitting torque is low.
【０００４】これらの問題点を解決するため、本願出願
人は、先に、主軸に２個の羽根を設けるとともにライナ
ー１回転につきライナーのシール面と主軸のシール面及
び羽根とを１回のみシールして１回の打撃トルクを発生
するようにした油圧式トルクレンチを提案した（実公平
１ー２９０１２号公報参照）。しかしながら、作業効率
の向上のため、装置を大形化せずこの装置で得られる打
撃トルクよりも大きな打撃トルクを得られる装置が要請
されていた。In order to solve these problems, the applicant of the present application first provided two blades on the main shaft and sealed the seal surface of the liner, the seal surface of the main shaft and the blade only once per rotation of the liner. A hydraulic torque wrench that generates a single impact torque has been proposed (see Japanese Utility Model Publication No. 1-201212). However, in order to improve the working efficiency, there has been a demand for a device capable of obtaining an impact torque larger than that obtained by this device without increasing the size of the device.
【０００５】[0005]
【発明が解決しようとする課題】本発明はこれに鑑み
て、装置を大形化せず、騒音と振動が小さく、高い打撃
トルクを得られ、かつ、耐久性の高い油圧式トルクレン
チの打撃トルク発生装置を提供することを目的とする。SUMMARY OF THE INVENTION In view of the foregoing, the present invention provides a hydraulic torque wrench capable of obtaining a high impact torque while reducing noise and vibration without increasing the size of the device. It is an object to provide a torque generating device.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、本発明の油圧式トルクレンチの打撃トルク発生装置
は、ロータにより回動し、内部に空洞とシール面を有す
るライナーと、該ライナーの内部に同軸に配設し、羽根
とシール面を有する主軸とからなる油圧式トルクレンチ
の打撃トルク発生装置において、前記ライナーは、６以
上の複数２ｎ個のシール面を有し、該シール面のうちｎ
個のシール面は、各シール面が相互に３６０／ｎ度回転
対称となる位置に、他のｎ個のシール面は、それぞれの
シール面が前記ｎ個の相互に３６０／ｎ度回転対称のシ
ール面の略中間で、かつ、各シール面が相互に３６０／
ｎ度回転非対称となる位置に配設され、前記主軸は、ｎ
個の羽根とｎ個のシール面を有し、前記ｎ個の羽根は、
各羽根が相互に３６０／ｎ度回転対称となる位置に設け
た羽根挿入溝に出没自在に嵌挿され、前記ｎ個のシール
面は、それぞれのシール面が前記ｎ個の羽根の略中間
で、各シール面が相互に３６０／ｎ度回転非対称とな
り、かつ、ライナーの１回転につきライナーのｎ個の相
互に３６０／ｎ度回転対称のシール面と主軸のｎ個の羽
根とが合致する際、前記ライナーのｎ個の相互に３６０
／ｎ度回転非対称のシール面と同時に１回合致する位置
に配設されるとともに、前記主軸に設けた羽根挿入溝を
相互に連通しない有底の溝で構成するとともに、前記ラ
イナーのシール面と主軸の羽根及びシール面によって区
画される前記ライナー内部の空洞を１つ置きに相互に連
通する２組の連通孔を主軸の羽根挿入溝とシール面の間
に、羽根挿入溝と連通しないように穿設してなることを
特徴とする。In order to achieve the above object, the present invention provides a hydraulic torque wrench having an impact torque generating device which is rotated by a rotor and has a liner having a cavity and a sealing surface therein, In a striking torque generating device for a hydraulic torque wrench comprising a blade and a main shaft having a sealing surface, the liner has six or more 2n sealing surfaces, and the liner has a plurality of 2n sealing surfaces. Of which n
The seal surfaces are located at positions where each seal surface is rotationally symmetric with respect to each other at 360 / n degrees, and the other n seal surfaces are rotationally symmetric with respect to each other at the n seal surfaces with respect to each other. It is approximately halfway between the sealing surfaces, and each sealing surface is 360 /
The main shaft is disposed at a position that is rotationally asymmetrical by n degrees,
Blades and n sealing surfaces, wherein the n blades are:
Each of the blades is inserted into a blade insertion groove provided at a position where the blades are rotationally symmetric with respect to each other at 360 / n degrees, and the n sealing surfaces are substantially in the middle of the n blades. When the respective seal surfaces are mutually rotationally asymmetrical by 360 / n degrees, and the n rotationally symmetrical seal surfaces of the liner and n blades of the main shaft coincide with each other per rotation of the liner. 360 n of said liners
/ N degrees of rotation asymmetrical sealing surface and at the same time as the same position, and the blade insertion groove provided on the main shaft is formed of a bottomed groove that does not communicate with each other. Two sets of communication holes communicating with every other cavity inside the liner defined by the blades and the sealing surface of the main shaft are provided between the blade insertion groove and the sealing surface of the main shaft so as not to communicate with the blade insertion groove. It is characterized by being drilled.
【０００７】[0007]
【作用】本発明の油圧式トルクレンチの打撃トルク発生
装置によれば、ライナーの１回転につき１回、ライナー
のｎ個の相互に３６０／ｎ度回転対称のシール面と主軸
のｎ個の羽根とが合致する際、同時にライナーのｎ個の
相互に３６０／ｎ度回転非対称のシール面と主軸のｎ個
の相互に３６０／ｎ度回転非対称のシール面とが合致
し、この時打撃トルクを発生する。この場合において、
主軸には、３個以上のｎ個の羽根が羽根挿入溝に出没自
在に嵌挿されているため、受圧面を広く取ることがで
き、高い打撃トルクを得ることができる。また、主軸に
設ける羽根挿入溝の数を３個以上にすることによる主軸
の強度の低下を緩和しながら、主軸に穿設した２組の連
通孔により正逆いずれの回転時にも３個以上の高圧室を
相互に連通することができる。According to the striking torque generator of the hydraulic torque wrench of the present invention, the n number of mutually 360 / n-degree rotationally symmetric sealing surfaces and the n number of blades of the main shaft are provided once per rotation of the liner. At the same time, the n mutually 360 / n-degree rotationally asymmetric sealing surfaces of the liner and the n mutually 360 / n-degree rotationally asymmetrical sealing surfaces of the main shaft coincide with each other. Occur. In this case,
Since three or more n blades are fitted to the main shaft so as to be able to come and go in the blade insertion grooves, a large pressure receiving surface can be obtained, and a high impact torque can be obtained. In addition, while reducing the strength of the main shaft by reducing the number of blade insertion grooves provided in the main shaft to three or more, two or more communication holes formed in the main shaft allow three or more blades to be inserted at any time in both forward and reverse rotations. The high pressure chambers can communicate with each other.
【０００８】[0008]
【実施例】以下、本発明を図示の実施例に基づいて説明
する。図において１は油圧式トルクレンチの本体で、本
体１内には、高圧空気の供給、停止を行うメインバルブ
２と正逆回転の打撃トルクを選択的に発生させるための
正逆回転切換バルブ３を設けるとともに、このバルブ群
より送気される高圧空気により回転トルクを発生するロ
ータ４を設ける。ロータ４の回転トルクを打撃トルクに
変換する油圧式打撃トルク発生装置５は本体１の先端部
に突設されたフロントケース６内に設ける。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the illustrated embodiments. In the figure, reference numeral 1 denotes a main body of a hydraulic torque wrench. A main valve 2 for supplying and stopping high-pressure air and a forward / reverse rotation switching valve 3 for selectively generating a forward / reverse rotation impact torque are provided in the body 1. And a rotor 4 for generating a rotational torque by high-pressure air supplied from the valve group. A hydraulic impact torque generating device 5 for converting the rotational torque of the rotor 4 into an impact torque is provided in a front case 6 protruding from the tip of the main body 1.
【０００９】この油圧式打撃トルク発生装置５はライナ
ーケース１２内にライナー８を主軸７に対して回動自在
に外嵌し、このライナー８内にトルクを発生せしめるた
めの作動油を充填密閉してなり、かつ主軸７には１２０
度回転対称となる位置に３個の羽根挿入溝１５を設け、
各溝１５内に３個の羽根９を嵌挿し、かつこの３個の羽
根９をばねＳにて常時主軸外周方向に付勢し、しかもこ
の羽根９の厚さを羽根挿入溝１５の溝幅より小なるよう
にして設けるとともに、この３個の羽根９の間の主軸外
周面には主軸外周面より少し突出した３個のシール面７
ａを形成する。この３個のシール面７ａは、それぞれの
シール面７ａが羽根挿入溝１５の略中間で、各シール面
７ａが相互に１２０度回転非対称となる位置に設ける。The hydraulic striking torque generating device 5 has a liner 8 rotatably fitted to a main shaft 7 inside a liner case 12 and fills and seals a hydraulic oil for generating a torque in the liner 8. And the spindle 7 has 120
The three blade insertion grooves 15 are provided at positions that are rotationally symmetrical in degrees,
Three blades 9 are inserted into each groove 15 and the three blades 9 are constantly urged in the outer peripheral direction of the main shaft by a spring S. In addition, the thickness of the blade 9 is determined by the groove width of the blade insertion groove 15. The three sealing surfaces 7 slightly projecting from the outer peripheral surface of the main shaft are provided on the outer peripheral surface of the main shaft between the three blades 9.
a is formed. The three sealing surfaces 7a are provided at positions where the respective sealing surfaces 7a are substantially at the center of the blade insertion groove 15 and the respective sealing surfaces 7a are rotationally asymmetric with each other by 120 degrees.
【００１０】主軸７を嵌挿するライナー８は、内部に空
洞を形成し、その内周面に山形状に突出せしめて６個の
シール面を形成し、このうち３個のシール面８ｂは、各
シール面８ｂが相互に１２０度回転対称となる位置に、
他の３個のシール面８ａは、それぞれのシール面８ａが
前記３個の相互に１２０度回転対称のシール面８ｂの略
中間で、かつ、各シール面８ａが相互に１２０度回転非
対称となる位置に設ける。The liner 8 into which the main shaft 7 is inserted has a cavity formed therein, and is formed on the inner peripheral surface thereof so as to protrude in a mountain shape to form six sealing surfaces. Of these, three sealing surfaces 8b are At a position where each seal surface 8b is rotationally symmetric with each other by 120 degrees,
The other three sealing surfaces 8a are substantially intermediate between the three sealing surfaces 8a that are rotationally symmetric with each other and the sealing surfaces 8a are rotationally asymmetric with each other by 120 degrees. Position.
【００１１】そして、主軸７の３個の羽根９及び３個の
シール面９ａとライナー８の６個のシール面８ａ，８ｂ
は、ライナーの１回転につき、主軸７の３個の羽根９と
ライナー８の３個の相互に１２０度回転対称のシール面
８ｂとが合致する際、主軸７の３個の相互に１２０度回
転非対称のシール面７ａとライナー８の３個の相互に１
２０度回転非対称のシール面８ａが同時に１回合致する
ように設ける。The three blades 9 of the main shaft 7 and the three sealing surfaces 9a and the six sealing surfaces 8a and 8b of the liner 8 are provided.
When three blades 9 of the main shaft 7 and three mutually rotationally symmetrical sealing surfaces 8b of the liner 8 are aligned with each other for one rotation of the liner, the three rotations of the main shaft 7 are mutually rotated by 120 degrees. The three mutually asymmetrical sealing surfaces 7a and liner 8
It is provided so that the sealing surface 8a, which is asymmetrical by 20 degrees, coincides once at the same time.
【００１２】主軸７の３個の羽根９及び３個のシール面
９ａとライナー８の６個のシール面８ａ，８ｂの具体的
配置例を図５〜図９に示す。なお、（ａ）は主軸７を、
（ｂ）はライナー８を展開図として示したものである。
各図に示すとおり、主軸７の３個の羽根９及びライナー
８の３個の相互に１２０度回転対称のシール面８ｂは、
いずれも直線形状をして１２０度の等間隔に配置し、主
軸７の３個の相互に１２０度回転非対称のシール面７ａ
及びライナー８の３個の相互に１２０度回転非対称のシ
ール面８ａは、主軸７の３個の羽根９又はライナー８の
３個の相互に１２０度回転対称のシール面８ｂの略中間
の位置に、いずれも直線形状をして３個のうちの２個の
シール面７ａ，８ａを１２０度の等間隔の線上から前後
に位置をずらして配置したり（図５）、３個のうちの２
個のシール面７ａ，８ａを互いに向き合うクランク形状
としたり（図６）、３個のうちの２個のシール面７ａ，
８ａを形状の異なるクランク形状としたり（図７）、３
個のうちの２個のシール面７ａ，８ａを傾斜線形状とし
たり（図８）、３個のうちの２個のシール面７ａ，８ａ
を互いに向き合うＶ字形状としたり（図９）することが
できるが、これに限定されず、上述のとおり、ライナー
の１回転につき、主軸７の３個の羽根９とライナー８の
３個の相互に１２０度回転対称のシール面８ｂとが合致
する際、主軸７の３個の相互に１２０度回転非対称のシ
ール面７ａとライナー８の３個の相互に１２０度回転非
対称のシール面８ａが同時に１回合致するものであれば
どのようなものでもよい。FIGS. 5 to 9 show specific examples of the arrangement of the three blades 9 of the main shaft 7 and the three sealing surfaces 9a and the six sealing surfaces 8a and 8b of the liner 8. (A) shows the main shaft 7,
(B) is a development view of the liner 8.
As shown in each figure, the three blades 9 of the main shaft 7 and the three seal surfaces 8b of the liner 8 that are rotationally symmetric with each other by 120 degrees are
All of them are linear and arranged at equal intervals of 120 degrees, and the three seal faces 7a of the main shaft 7 which are rotationally asymmetric with respect to each other by 120 degrees.
And the three mutually 120-degree rotationally asymmetrical sealing surfaces 8a of the liner 8 are located substantially in the middle of the three mutually rotationally symmetrical sealing surfaces 8b of the main shaft 7 or the three blades 9 of the liner 8. Each of them has a linear shape, and two of the three sealing surfaces 7a and 8a are arranged so as to be shifted back and forth from a line at equal intervals of 120 degrees (FIG. 5).
The two sealing surfaces 7a, 8a are formed in a crank shape facing each other (FIG. 6), or two out of three sealing surfaces 7a, 8a are formed.
8a may be a crank shape having a different shape (FIG. 7);
Two of the three sealing surfaces 7a, 8a may be formed into inclined line shapes (FIG. 8), or two of the three sealing surfaces 7a, 8a.
Can be formed into a V-shape facing each other (FIG. 9), but is not limited thereto, and as described above, three rotations of the main shaft 7 and the three liners 8 of the liner 8 per one rotation of the liner. When the 120 ° rotationally symmetrical sealing surfaces 8b coincide with each other, the three mutually 120 ° rotationally asymmetrical sealing surfaces 7a of the main shaft 7 and the three mutually 120 ° rotationally asymmetrical sealing surfaces 8a of the liner 8 are simultaneously formed. Any one that matches once may be used.
【００１３】主軸７の羽根９及びシール面７ａとライナ
ー８のシール面８ａ，８ｂとによって区画されるライナ
ー８内部の空洞を１つ置きに相互に連通する２組の連通
孔１６ａ，１６ｂを主軸７の羽根挿入溝１５とシール面
７ａの間に設ける。Two sets of communicating holes 16a and 16b are provided for communicating with every other cavity inside the liner 8 defined by the blades 9 and the sealing surface 7a of the main shaft 7 and the sealing surfaces 8a and 8b of the liner 8. 7 is provided between the blade insertion groove 15 and the sealing surface 7a.
【００１４】ライナー８の内部には、ライナー８の軸心
に平行に出力調整弁挿入孔１０を穿孔するとともに、出
力調整弁挿入孔１０にはシール面８ａ（又はシール面８
ｂ）を挟んで主軸７のシール面７ａ（又は羽根９）によ
り分割されるライナー８内部の空洞と出力調整弁挿入孔
１０とが導通するようポートＰ１，Ｐ２を形成し、かつ
該孔内に出力調整弁１１を可調整的に嵌合する。In the inside of the liner 8, an output adjustment valve insertion hole 10 is formed in parallel with the axis of the liner 8, and the output adjustment valve insertion hole 10 has a sealing surface 8a (or a sealing surface 8).
b) Ports P1 and P2 are formed so that the cavity inside the liner 8 divided by the sealing surface 7a (or the blade 9) of the main shaft 7 across the main shaft 7 and the power adjustment valve insertion hole 10 are connected to each other, and the holes P1 and P2 are formed in the holes. The output adjustment valve 11 is fitted in an adjustable manner.
【００１５】ライナー８はその外周を筒状のライナーケ
ース１２にて回動自在に支持され、ライナーケース１２
の両端面にライナー上蓋１３及びライナー下蓋１４を設
け、ライナー上蓋１３をさらにライナーケース蓋１８で
固定して、ライナー８の内部に充填される作動油を密封
するようになっている。作動油の注入及び排出は、ライ
ナー下蓋１４に設けた油蓋１７を開放することにより行
う。The liner 8 is rotatably supported on its outer periphery by a cylindrical liner case 12.
A liner upper lid 13 and a liner lower lid 14 are provided on both end surfaces of the liner 8, and the liner upper lid 13 is further fixed with a liner case lid 18 to seal the working oil filled in the liner 8. Injection and discharge of the hydraulic oil are performed by opening an oil cover 17 provided on the liner lower cover 14.
【００１６】なお、上記の実施例は、主軸７に３個の羽
根９と３個のシール面９ａを、ライナー８に６個のシー
ル面８ａ，８ｂを設けたものであるが、羽根及びシール
面の数はこれに限定されず、主軸に４個以上の羽根と４
個以上のシール面を、ライナー８に８個以上のシール面
８ａ，８ｂを上記の実施例に準じて設けることにより受
圧面をより広く取ることができる。In the above embodiment, the main shaft 7 is provided with three blades 9 and three sealing surfaces 9a, and the liner 8 is provided with six sealing surfaces 8a and 8b. The number of surfaces is not limited to this, and four or more blades and four
By providing at least eight sealing surfaces on the liner 8 in accordance with the above-described embodiment, eight or more sealing surfaces 8a and 8b can provide a wider pressure receiving surface.
【００１７】次に、上記の油圧式トルクレンチの打撃ト
ルク発生装置の作動状態について説明する。まず、メイ
ンバルブ２及び切換バルブ３を操作して高圧空気を本体
１内のロータ室へ導入するとロータ４は高速で回転す
る。このロータの回転力はライナー８に伝達される。Next, the operating state of the above-described hydraulic torque wrench impact torque generating device will be described. First, when the high pressure air is introduced into the rotor chamber in the main body 1 by operating the main valve 2 and the switching valve 3, the rotor 4 rotates at a high speed. The rotational force of this rotor is transmitted to the liner 8.
【００１８】ライナー８の回転により、ライナー８の内
部は、図４（ａ）→（ｂ）→（ｃ）→（ａ）・・・のと
おり変化する。図４（ａ）は、主軸７にパルスすなわち
打撃トルクが発生した状態を示し、これよりライナー８
が１２０度ずつ回転した状態を（ｂ）及び（ｃ）に示
す。As the liner 8 rotates, the inside of the liner 8 changes as shown in FIG. 4 (a) → (b) → (c) → (a). FIG. 4A shows a state in which a pulse, that is, an impact torque is generated on the main shaft 7.
(B) and (c) show a state where is rotated by 120 degrees.
【００１９】打撃時、図４（ａ）に示すように、主軸７
のシール面７ａと羽根９は、それぞれライナー８のシー
ル面８ａと８ｂに接し、ライナー８内部の空洞は、６室
に分けられ、それぞれの室は交互に高圧室Ｈと低圧室Ｌ
になる。そして、ロータ４の回転によってライナー８を
回転させると衝撃の瞬間の直前において高圧室Ｈの体積
は減少され、低圧室Ｌの体積は増加し、羽根９を挟んだ
２室が完全に封止状態になったとき高圧室にて高圧を発
生せしめ、この油圧をもって羽根９の側面を低圧室側へ
瞬間的に押圧し、羽根９を嵌挿した主軸７にその打撃力
を伝達し、主軸７に所望の間歇的な打撃トルクを発生さ
せて主軸７を回転させ、所望の作業を行なわしめる。At the time of impact, as shown in FIG.
Of the liner 8 are in contact with the sealing surfaces 7a and 8b of the liner 8, respectively, and the cavity inside the liner 8 is divided into six chambers, each of which alternately has a high-pressure chamber H and a low-pressure chamber L.
become. When the liner 8 is rotated by the rotation of the rotor 4, the volume of the high-pressure chamber H is reduced and the volume of the low-pressure chamber L is increased immediately before the moment of the impact, and the two chambers sandwiching the blade 9 are completely sealed. When the pressure becomes high, a high pressure is generated in the high-pressure chamber, and the side surface of the blade 9 is momentarily pressed toward the low-pressure chamber with the hydraulic pressure, and the striking force is transmitted to the main shaft 7 into which the blade 9 is inserted, and A desired intermittent impact torque is generated to rotate the main shaft 7 to perform a desired operation.
【００２０】主軸に打撃トルクを発生させた後、さらに
ライナー８が１２０度回転すると図４（ｂ）に示すよう
に、主軸７の羽根９とライナー８のシール面８ｂとが合
致するも主軸７のシール面７ａとライナー８のシール面
８ａとが合致しないことから、ライナー８内部の空洞は
高圧室と低圧室に区分させず、全体として３室となり、
主軸７には打撃トルクが発生せず、ライナー８はロータ
４の回転によりさらに回転する。このようにしてライナ
ーがさらに１２０度、すなわち打撃トルク発生時より２
４０度回転すると図４（ｃ）に示すようになる。この状
態においても、図４（ｂ）と同様に、主軸７の羽根９と
ライナー８のシール面８ｂとが合致するも主軸７のシー
ル面７ａとライナー８のシール面８ａとが合致しないこ
とから、ライナー８内部の空洞は高圧室と低圧室に区分
させず、全体として３室となり、主軸７には打撃トルク
が発生せず、ライナー８はロータ４の回転によりさらに
回転して、図４（ａ）の打撃トルクを発生する状態に戻
り、以下これを繰り返す。After the impact torque is generated on the main shaft, when the liner 8 further rotates by 120 degrees, the blade 9 of the main shaft 7 and the sealing surface 8b of the liner 8 are aligned as shown in FIG. Since the sealing surface 7a of the liner 8 does not match with the sealing surface 8a of the liner 8, the cavity inside the liner 8 is not divided into a high-pressure chamber and a low-pressure chamber, and becomes three chambers as a whole.
No impact torque is generated on the main shaft 7, and the liner 8 is further rotated by the rotation of the rotor 4. In this manner, the liner is further extended by 120 degrees, that is, two times more than when the impact torque is generated.
When rotated by 40 degrees, it becomes as shown in FIG. In this state as well, as in FIG. 4B, the blade 9 of the main shaft 7 and the sealing surface 8b of the liner 8 match, but the sealing surface 7a of the main shaft 7 does not match the sealing surface 8a of the liner 8. The cavity inside the liner 8 is not divided into a high-pressure chamber and a low-pressure chamber, and has three chambers as a whole. No impact torque is generated on the main shaft 7, and the liner 8 is further rotated by the rotation of the rotor 4, and FIG. The procedure returns to the state in which the impact torque of a) is generated, and this is repeated thereafter.
【００２１】このようにしてこのライナー１回転により
強力な打撃トルクを１回発生せしめることができる。そ
してこの打撃力の調整は、上記出力調整弁１１によって
従来と同様の方法で行うものである。In this manner, a strong impact torque can be generated once by one rotation of the liner. The adjustment of the striking force is performed by the output adjusting valve 11 in the same manner as in the prior art.
【００２２】[0022]
【発明の効果】本発明の油圧式トルクレンチの打撃トル
ク発生装置によれば、主軸に設けた羽根挿入溝を相互に
連通しない有底の溝で構成するとともに、ライナーのシ
ール面と主軸の羽根及びシール面によって区画されるラ
イナー内部の空洞を１つ置きに相互に連通する２組の連
通孔を主軸の羽根挿入溝とシール面の間に、羽根挿入溝
と連通しないように穿設することにより、正逆回転の高
い打撃トルクを選択的に発生させることができる打撃ト
ルク発生装置を、装置を大形化せずに、かつ騒音と振動
を高めずに得ることができ、また、主軸に設ける羽根挿
入溝の数を３個以上にすることによる主軸の強度の低下
を、羽根挿入溝を相互に連通しない有底の溝で構成する
ことにより緩和して装置の耐久性を向上するとともに、
主軸に穿設した２組の連通孔により正逆いずれの回転時
にも３個以上の高圧室を相互に連通することができ、こ
れにより、高圧室相互間の圧力のばらつきを解消し、打
撃トルク発生装置を円滑に駆動することができるととも
に、精度の高い打撃トルクを発生させることができ、さ
らに、主軸の羽根挿入溝に出没自在に嵌挿する羽根の数
を３個以上にすることによる装置全体の構造の複雑化を
軽減することができる。According to the striking torque generating device for a hydraulic torque wrench of the present invention, the blade insertion groove provided on the main shaft is constituted by a bottomed groove which does not communicate with each other, and the seal surface of the liner and the main shaft blade are formed. And two sets of communication holes that communicate with each other every other cavity inside the liner defined by the sealing surface between the blade insertion groove of the main shaft and the sealing surface so as not to communicate with the blade insertion groove. Thus, it is possible to obtain a striking torque generating device capable of selectively generating a high striking torque with forward and reverse rotations without increasing the size of the device and without increasing noise and vibration. A decrease in the strength of the main shaft caused by providing three or more blade insertion grooves is reduced by configuring the blade insertion grooves with bottomed grooves that do not communicate with each other, thereby improving the durability of the device.
Three or more high-pressure chambers can communicate with each other during both forward and reverse rotations by two sets of communication holes formed in the main shaft, thereby eliminating pressure variations among the high-pressure chambers and reducing the impact torque. An apparatus by which the generator can be smoothly driven, a high-precision impact torque can be generated, and the number of blades that can be freely inserted into and retracted from the blade insertion groove of the main shaft is three or more. The complexity of the entire structure can be reduced.
【図１】本発明の打撃トルク発生装置を組み込んだ油圧
式インパクトレンチの全体を示す図である。FIG. 1 is a diagram showing an entire hydraulic impact wrench incorporating an impact torque generating device of the present invention.
【図２】本発明の打撃トルク発生装置の要部を示す図で
ある。FIG. 2 is a diagram showing a main part of a striking torque generating device according to the present invention.
【図３】図２の断面図であって、（ａ）はＡ−Ａ断面
を、（ｂ）はＢ−Ｂ断面を、（ｃ）はＣ−Ｃ断面を示す
図である。FIGS. 3A and 3B are cross-sectional views of FIG. 2, wherein FIG. 3A is a cross-sectional view taken along line AA, FIG. 3B is a cross-sectional view taken along line BB, and FIG.
【図４】本発明の打撃トルク発生装置の作動状態を示す
図である。FIG. 4 is a diagram showing an operation state of the impact torque generating device of the present invention.
【図５】主軸及びライナーの展開図である。FIG. 5 is a development view of a main shaft and a liner.
【図６】主軸及びライナーの展開図である。FIG. 6 is a development view of a main shaft and a liner.
【図７】主軸及びライナーの展開図である。FIG. 7 is a development view of a main shaft and a liner.
【図８】主軸及びライナーの展開図である。FIG. 8 is a development view of a main shaft and a liner.
【図９】主軸及びライナーの展開図である。FIG. 9 is a development view of a main shaft and a liner.
１ 本体 ２ メインバルブ ３ 正逆回転切換バルブ ４ ロータ ５ 打撃トルク発生装置 ７ 主軸 ７ａ シール面 ８ ライナー ８ａ シール面 ８ｂ シール面 ９ 羽根 １０ 出力調整弁挿入孔 １１ 出力調整弁 １２ ライナーケース １５ 羽根挿入溝 １６ａ 連通孔 １６ｂ 連通孔 Ｈ 高圧室 Ｌ 低圧室 Ｐ１ ポート Ｐ２ ポート Ｓ ばね DESCRIPTION OF SYMBOLS 1 Main body 2 Main valve 3 Forward / reverse rotation switching valve 4 Rotor 5 Impact torque generator 7 Main shaft 7a Seal surface 8 Liner 8a Seal surface 8b Seal surface 9 Blade 10 Output adjustment valve insertion hole 11 Output adjustment valve 12 Liner case 15 Blade insertion groove 16a communication hole 16b communication hole H high pressure chamber L low pressure chamber P1 port P2 port S spring
Claims (1)
ル面を有するライナーと、該ライナーの内部に同軸に配
設し、羽根とシール面を有する主軸とからなる油圧式ト
ルクレンチの打撃トルク発生装置において、前記ライナ
ーは、６以上の複数２ｎ個のシール面を有し、該シール
面のうちｎ個のシール面は、各シール面が相互に３６０
／ｎ度回転対称となる位置に、他のｎ個のシール面は、
それぞれのシール面が前記ｎ個の相互に３６０／ｎ度回
転対称のシール面の略中間で、かつ、各シール面が相互
に３６０／ｎ度回転非対称となる位置に配設され、前記
主軸は、ｎ個の羽根とｎ個のシール面を有し、前記ｎ個
の羽根は、各羽根が相互に３６０／ｎ度回転対称となる
位置に設けた羽根挿入溝に出没自在に嵌挿され、前記ｎ
個のシール面は、それぞれのシール面が前記ｎ個の羽根
の略中間で、各シール面が相互に３６０／ｎ度回転非対
称となり、かつ、ライナーの１回転につきライナーのｎ
個の相互に３６０／ｎ度回転対称のシール面と主軸のｎ
個の羽根とが合致する際、前記ライナーのｎ個の相互に
３６０／ｎ度回転非対称のシール面と同時に１回合致す
る位置に配設されるとともに、前記主軸に設けた羽根挿
入溝を相互に連通しない有底の溝で構成するとともに、
前記ライナーのシール面と主軸の羽根及びシール面によ
って区画される前記ライナー内部の空洞を１つ置きに相
互に連通する２組の連通孔を主軸の羽根挿入溝とシール
面の間に、羽根挿入溝と連通しないように穿設してなる
ことを特徴とする記載の油圧式トルクレンチの打撃トル
ク発生装置。1. A striking torque of a hydraulic torque wrench, which is rotated by a rotor and has a liner having a cavity and a sealing surface therein, and a main shaft coaxially disposed inside the liner and having a blade and a sealing surface. In the generator, the liner has a plurality of 2n or more sealing surfaces of 6 or more, and n sealing surfaces of the sealing surfaces are mutually 360
/ N degrees of rotational symmetry, the other n sealing surfaces are:
Each of the sealing surfaces is disposed at substantially the middle of the n number of mutually 360 / n-degree rotationally symmetrical sealing surfaces and at a position where each of the sealing surfaces is rotationally asymmetrical with respect to each other by 360 / n-degrees. , N blades and n sealing surfaces, and the n blades are removably fitted into blade insertion grooves provided at positions where each blade is rotationally symmetric with respect to 360 / n degrees, The n
The sealing surfaces are each approximately halfway between the n blades, the respective sealing surfaces are rotationally asymmetrical by 360 / n degrees with respect to each other, and the number of the liner is n per rotation of the liner.
360 / n-degree rotationally symmetric sealing surfaces and n of the main shaft
When the number of blades coincides with each other, the n pieces of the liner are disposed at the same position as the 360 ° / n-degree rotationally asymmetrical sealing surface once and at the same time, and the blade insertion grooves provided on the main shaft are connected to each other. With a bottomed groove that does not communicate with the
Two sets of communication holes communicating with one another in every other said liner inside the cavity defined by the sealing surface and the blade and the sealing surface of the spindle of the liner between the blade insertion groove and the sealing surface of the spindle, the blade insert The hitting torque generating device for a hydraulic torque wrench according to claim, wherein the hitting torque generating device is formed so as not to communicate with the groove .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5104998A JP2779749B2 (en) | 1993-04-06 | 1993-04-06 | Impact torque generator for hydraulic torque wrench |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5104998A JP2779749B2 (en) | 1993-04-06 | 1993-04-06 | Impact torque generator for hydraulic torque wrench |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06285770A JPH06285770A (en) | 1994-10-11 |
| JP2779749B2 true JP2779749B2 (en) | 1998-07-23 |
Family
ID=14395771
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5104998A Expired - Fee Related JP2779749B2 (en) | 1993-04-06 | 1993-04-06 | Impact torque generator for hydraulic torque wrench |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2779749B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7055291B2 (en) * | 2017-08-21 | 2022-04-18 | 不二空機株式会社 | Tightening torque generation mechanism and hydraulic pulse wrench |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62246481A (en) * | 1985-09-30 | 1987-10-27 | ヨコタ工業株式会社 | Two blade type impulse wrench |
| SE460713B (en) * | 1986-04-22 | 1989-11-13 | Atlas Copco Ab | HYDRAULIC TORQUE PULSE |
| JPS6327266U (en) * | 1986-07-30 | 1988-02-23 | ||
| JPS6429012U (en) * | 1987-08-17 | 1989-02-21 | ||
| JPH0627341Y2 (en) * | 1988-07-25 | 1994-07-27 | 株式会社空研 | Hydraulic torque wrench |
-
1993
- 1993-04-06 JP JP5104998A patent/JP2779749B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06285770A (en) | 1994-10-11 |
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