JPS6051999B2 - Electric screwdriver torque adjustment device - Google Patents
Electric screwdriver torque adjustment deviceInfo
- Publication number
- JPS6051999B2 JPS6051999B2 JP56204737A JP20473781A JPS6051999B2 JP S6051999 B2 JPS6051999 B2 JP S6051999B2 JP 56204737 A JP56204737 A JP 56204737A JP 20473781 A JP20473781 A JP 20473781A JP S6051999 B2 JPS6051999 B2 JP S6051999B2
- Authority
- JP
- Japan
- Prior art keywords
- ratchet
- spring receiver
- spring
- torque
- sun gear
- 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
Links
Landscapes
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
Description
【発明の詳細な説明】
本発明は、電動ドライバのトルク調整機構に関”する
ものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torque adjustment mechanism for an electric screwdriver.
従来のトルク調整装置は第9図及び第10図に示すよ
うに、伝動軸71の端部72に複数個の鋼球73を保持
するフランジ74を設け、該鋼球73に対向して山形突
起75を形成し、内径にスプライン溝76を持つラチエ
ツト 7を出力軸78に嵌合配設している。As shown in FIGS. 9 and 10, the conventional torque adjusting device includes a flange 74 that holds a plurality of steel balls 73 at an end 72 of a transmission shaft 71, and a chevron-shaped protrusion facing the steel balls 73. A ratchet 7 having a spline groove 76 on its inner diameter is fitted onto the output shaft 78.
一方ニツ割りハウジング79、80に保持されたフレー
ム81の端部82に円板83を設け、円板83とハウジ
ング79、80との間に内側端面に階段状の案内カム8
4を持Jつ調整筒85を配設し、調整筒85に隣接して
、バネ受け86及びクラッチバネ87並びにスラストニ
ードルベアリング88を介在して、ラチエツト77の山
形突起75をフランジ74に保持された鋼球73に圧接
する。この機構における作動は、モーターの回転力によ
り伝動軸71が回転し、クラッチバネ87の支持のもと
に鋼球73が山形突起75に係止して出力軸78を回転
する。On the other hand, a disc 83 is provided at the end 82 of the frame 81 held by the split housings 79, 80, and a stepped guide cam 8 is provided on the inner end surface between the disc 83 and the housings 79, 80.
An adjustment cylinder 85 having a diameter of 4 is disposed adjacent to the adjustment cylinder 85, and the chevron-shaped protrusion 75 of the ratchet 77 is held by the flange 74 through a spring receiver 86, a clutch spring 87, and a thrust needle bearing 88. The steel ball 73 is pressed against the steel ball 73. In operation of this mechanism, the transmission shaft 71 is rotated by the rotational force of the motor, and the steel ball 73 is engaged with the chevron-shaped protrusion 75 under the support of the clutch spring 87 to rotate the output shaft 78.
出力軸78に一定トルクが加わつた場合、伝動軸71の
回転力が鋼球73が山形突起75をクラッチバネ87の
押圧力に打ち勝つて、ラチエツト77を軸方向に移動さ
せ、これにより伝動軸71と出力軸78間の動力伝達が
断れる状態となる。設定トルクの調整は調整筒85を回
動することにより、バネ受け86が調整筒85の階段状
の案内カム84に案内され軸方向に移動して、クラッチ
バネ87の圧縮量を変えることにより押圧力が変化し、
トルク調整が行われる。また、調整筒85を最大回動さ
せ、クラッチバネ87が全圧縮し、ラチエツト77の山
形突起75が鋼球73に当接して、ラチエツト77の軸
方向の動きが阻止され、モーターの最大回転力が出力軸
78に伝達される。When a constant torque is applied to the output shaft 78, the rotational force of the transmission shaft 71 causes the steel ball 73 to push the chevron protrusion 75 over the pressing force of the clutch spring 87, and moves the ratchet 77 in the axial direction. The power transmission between the output shaft 78 and the output shaft 78 is cut off. The set torque can be adjusted by rotating the adjustment tube 85, and the spring receiver 86 is guided by the stepped guide cam 84 of the adjustment tube 85 and moves in the axial direction, changing the amount of compression of the clutch spring 87. pressure changes,
Torque adjustment is performed. Further, the adjusting cylinder 85 is rotated to the maximum, the clutch spring 87 is fully compressed, the chevron-shaped protrusion 75 of the ratchet 77 comes into contact with the steel ball 73, and the axial movement of the ratchet 77 is blocked, resulting in the maximum rotational force of the motor. is transmitted to the output shaft 78.
以上のような機構において、出力軸78に衝撃的な荷重
が加わつた場合、前記フランジ74に保持されている鋼
球73が脱落することがある。In the above-described mechanism, when an impact load is applied to the output shaft 78, the steel ball 73 held by the flange 74 may fall off.
又、調整筒85を最大回動させラチエツト77の軸方向
の動きを阻止した場合、バネ受け86及び円板83が弾
性変形したり、全圧縮されたクラッチバネ87が座屈現
象を起し、ラチエツト77の軸方向移動阻止できなくな
り、伝動軸71と出力軸78が連結されなくなることが
ある。一方、ラチエツト77の山形突起75はラチエツ
ト77の側面に対して屈折して立ち上つているため銅球
73とは点接触となり、かみ合時や乗り越え時に衝撃を
与え動作が不安定になつたり、耐摩耗性が低下するとい
う問題がある。本発明の目的は、上記した従来技術の欠
点をなくし、併せて動作を安定し、信頼性を高めるトル
ク調整装置を提供することである。Further, when the adjustment cylinder 85 is rotated to the maximum and the axial movement of the ratchet 77 is blocked, the spring receiver 86 and the disk 83 are elastically deformed, and the fully compressed clutch spring 87 causes a buckling phenomenon. It may become impossible to prevent the ratchet 77 from moving in the axial direction, and the transmission shaft 71 and output shaft 78 may become disconnected. On the other hand, since the chevron-shaped protrusion 75 of the ratchet 77 is bent and stands up against the side surface of the ratchet 77, it comes into point contact with the copper ball 73, causing impact when engaging or crossing over, making the operation unstable. There is a problem that wear resistance decreases. SUMMARY OF THE INVENTION An object of the present invention is to provide a torque adjusting device that eliminates the above-mentioned drawbacks of the prior art, and also stabilizes the operation and increases reliability.
すなわち、本発明は伝動軸と出力軸との断続部に山形突
起状のかみ合部を相方に設け、山形突起の斜面の摩擦力
で動力の断続を行うようにし、尚かつ、最大トルクの伝
達時における確実な結合を得るため、バネ受けのボス部
をラチエツトのボス部当接させたものである。That is, in the present invention, an engaging part in the form of a chevron-shaped protrusion is provided at the intermittent part of the transmission shaft and the output shaft, so that the power is interrupted by the frictional force of the slope of the chevron-shaped protrusion, and the maximum torque is transmitted. The boss of the spring receiver is brought into contact with the boss of the ratchet in order to ensure a secure connection during operation.
又、インボリュートスプライン接手は、伝動軸が加わる
と自動調心性が良くなる点に着目し、差動遊星歯車減速
部の出力側フランジと出力軸との接続に用いたものであ
る。以下この発明の実施例を適用した電動ドライバーを
第1図から第8図に示す。In addition, the involute spline joint was used to connect the output side flange of the differential planetary gear reduction section and the output shaft, paying attention to the fact that self-alignment improves when a transmission shaft is added. An electric screwdriver to which an embodiment of the present invention is applied is shown in FIGS. 1 to 8 below.
胴体の中間部にハンドル部3を設けたニツ割方式の外枠
であるハウジング1,2内に、第2図のようにハウジン
グ1,2後端部には電池部4を配し、ハンドル部3には
、スイッチ5を配し、下部にはチャックハンドル6を収
納している。中間部には、モータ7を配し、前端部に本
発明のトルク調整装置8と、差動遊星歯車減速部9を有
している。ニツ割方式のハウジング1,2は、2個所で
ネジ結合されさらに後端は、吊り具10の取り付もかね
たバンド11て緊締されている。差動遊星歯車減速部は
第3図及び第4図のようにモーター7の回転力は2段の
遊星歯車減速機構により出力軸14に伝達される。ピニ
オン15がモーター軸16に圧入固着されたモーター7
は、モーターブラケット17にモーター7前端面18を
ネジ19で止めている。一方モーターブラケット17は
、歯車ケース20にネジ21で固定される。歯車ケース
20内には、内歯歯車部21及び山形突起部22を形成
した太陽歯車23が回動自在に配設され、太陽歯車23
内て伝動歯車24を持つた第1の遊星歯車部25と出力
フランジ26を持つた第2の遊星歯車部27がかみ合い
、さらに出力フランジ26の内径に形成されたインボリ
ュートスプライン接手28により出力軸14が連結され
、出力軸14の前端部にドリルチャック12が装着され
る。As shown in Fig. 2, a battery section 4 is disposed at the rear end of the housings 1, 2 inside the housings 1, 2, which are split-type outer frames in which a handle section 3 is provided in the middle of the body. A switch 5 is arranged at 3, and a chuck handle 6 is housed at the bottom. A motor 7 is disposed in the intermediate portion, and a torque adjustment device 8 of the present invention and a differential planetary gear reduction portion 9 are provided at the front end. The split-type housings 1 and 2 are screwed together at two places, and furthermore, the rear end is tightened with a band 11 which also serves as an attachment for a hanger 10. In the differential planetary gear reduction section, as shown in FIGS. 3 and 4, the rotational force of the motor 7 is transmitted to the output shaft 14 by a two-stage planetary gear reduction mechanism. Motor 7 with pinion 15 press-fitted onto motor shaft 16
The front end surface 18 of the motor 7 is fixed to the motor bracket 17 with screws 19. On the other hand, the motor bracket 17 is fixed to the gear case 20 with screws 21. A sun gear 23 having an internal gear portion 21 and a chevron-shaped protrusion 22 is rotatably disposed inside the gear case 20.
A first planetary gear part 25 having a transmission gear 24 therein meshes with a second planetary gear part 27 having an output flange 26, and an involute spline joint 28 formed on the inner diameter of the output flange 26 connects the output shaft 14. are connected to each other, and a drill chuck 12 is attached to the front end of the output shaft 14.
モーター軸16に圧入固着されたピニオン15は、第1
の遊星歯車25に中心位置でかみ合い、第]の遊星歯車
25の伝動歯車24は、第2の遊星歯車27に中心位置
でかみ合い、動力伝達している。尚、モーターブラケッ
ト17・と第1の遊星歯車25との間及ひ第1の遊星歯
車25の伝動歯車フランジ29と第2の遊星歯車27の
間にはそれぞれスラストプレート30,31が介在され
軸方向荷重を支持している。出力軸14の前端部は、ボ
ールベアリング32を介して調整筒33に保持され、後
端部は、太陽歯車23の前端部に圧入固着されたメタル
34により軸支される。太陽歯車23の前端面周縁に、
軸方向に山形突起部22を複数個形成し、山形突起部2
2に対向して、同じ形状の山形突起部35を面周縁に形
成するラチエツト36を配設し、クラッチバネ37の押
圧力で山形突起の形成する面を圧接する。The pinion 15 press-fitted onto the motor shaft 16 is connected to the first
The transmission gear 24 of the second planetary gear 25 meshes with the second planetary gear 27 at the center to transmit power. Incidentally, thrust plates 30 and 31 are interposed between the motor bracket 17 and the first planetary gear 25 and between the transmission gear flange 29 of the first planetary gear 25 and the second planetary gear 27, respectively. Supports directional loads. The front end of the output shaft 14 is held by the adjustment tube 33 via a ball bearing 32, and the rear end is supported by a metal 34 press-fitted into the front end of the sun gear 23. At the periphery of the front end surface of the sun gear 23,
A plurality of chevron-shaped protrusions 22 are formed in the axial direction, and the chevron-shaped protrusions 2
A ratchet 36 having a chevron-shaped protrusion 35 of the same shape formed on the periphery of the surface is disposed opposite to the chevron-shaped protrusion 35, and the pressing force of a clutch spring 37 presses the surface formed by the chevron-shaped protrusion.
クラッチバネ37の前端部はバネ受け38に支持される
。又、歯車ケース20の前端部は、内周面にl複数個の
凹部39を形成し、凹部39に対応した外周縁部に凸部
40を形成するラチエツト36及びバネ受け38が、軸
方向に移動自在に、かつ回転不可なるように嵌合されて
いる。一方、バネ受け38と調整筒33との嵌合部にJ
は、階段状の案内カム41を形成し、双方が該案内カム
41で当接しているため、調整筒33を回動することに
より、階段状の案内カム41がバネ受け38に対し、位
相がずれバネ受け38を軸方向に移動させる。A front end portion of the clutch spring 37 is supported by a spring receiver 38 . In addition, the front end of the gear case 20 has a plurality of recesses 39 formed on its inner circumferential surface, and a ratchet 36 and a spring receiver 38 having protrusions 40 formed on the outer circumferential edge corresponding to the recesses 39 are arranged in the axial direction. They are fitted so that they are movable but not rotatable. On the other hand, J
forms a step-like guide cam 41, and since both are in contact with each other, by rotating the adjustment tube 33, the step-like guide cam 41 can be set out of phase with respect to the spring receiver 38. The offset spring receiver 38 is moved in the axial direction.
2歯車ケース20は、ハ
ウジング1,2にネジ42で固定され、調整筒33が歯
車ケース20の前部外周面で嵌合し、さらに調整筒33
の後端部はハウジング1,2に挾持嵌合される。尚、調
整筒33の回動は、歯車ケース20との係止部60に冫
係合して、回動範囲が抑止される。上記の機構において
、トルク調整の作動はつぎのとおりである。The two gear case 20 is fixed to the housings 1 and 2 with screws 42, and the adjustment cylinder 33 is fitted on the front outer peripheral surface of the gear case 20.
The rear end portions of the housings 1 and 2 are clamped and fitted. Note that the rotation of the adjustment cylinder 33 is inhibited by the engagement with the locking portion 60 with the gear case 20, thereby restricting the rotation range. In the above mechanism, the torque adjustment operation is as follows.
すなわち、モーター軸に圧入固着されたピニオン15の
回動力は、第1の遊星歯車25及び第2の遊星歯車27
を伝わり出力軸14を回転させる。この場合、出力軸1
4にあるトルクが加わると、太陽歯車23が反作用力を
受けて回転しようとするが、太陽歯車23はその前端面
に形成された山形突起22と、ラチエツト36の山形突
起35に係合し、回転出来ない。しか.し、出力軸14
のトルクが増大するにつれて、一定トルクに達すると、
山形突起22,35による係止部が、クラッチバネ37
の押圧力に打ち勝つて、ラチエツト36を軸方向に移動
させて外れ、出力軸14は一定トルクを受けながら回転
停止する。このトルクの調整は、調整筒33の回動によ
りバネ受け38を軸方向に移動させ、クラッチバネ37
の圧縮量を変えることにより押圧力が変化して調整され
る。つぎに本考案による作用効果を説明する。That is, the rotational force of the pinion 15 press-fitted onto the motor shaft is transmitted to the first planetary gear 25 and the second planetary gear 27.
is transmitted to rotate the output shaft 14. In this case, output shaft 1
4, when a certain torque is applied, the sun gear 23 receives a reaction force and tries to rotate, but the sun gear 23 engages with the chevron-shaped protrusion 22 formed on its front end surface and the chevron-shaped protrusion 35 of the ratchet 36. Can't rotate. deer. and output shaft 14
As the torque of increases, when a constant torque is reached,
The locking portion formed by the chevron-shaped protrusions 22 and 35 is connected to the clutch spring 37.
Overcoming the pressing force, the ratchet 36 is moved in the axial direction and removed, and the output shaft 14 stops rotating while being subjected to a constant torque. This torque adjustment is achieved by moving the spring receiver 38 in the axial direction by rotating the adjustment cylinder 33, and then moving the clutch spring 37.
The pressing force is changed and adjusted by changing the amount of compression. Next, the effects of the present invention will be explained.
1)太陽歯車23とラチエツト36の断続部に、山形突
起状のかみ合部を設け、突起の斜面43で係止及び作動
するようにしたため、動作が安定し、耐摩耗性が向上す
る。1) A chevron-shaped engagement portion is provided at the intermittent portion of the sun gear 23 and the ratchet 36, and the engagement portion is locked and operated by the slope 43 of the projection, thereby stabilizing the operation and improving wear resistance.
併せて、山形突起面の立ち上り角度を正転方向と逆転方
向で異なわせることにより、切転時と逆転時の伝達トル
クを変えることが出来る。2)調整筒33の回動によつ
てバネ受け38を最大量ラチエツト36側に移動させる
と、バネ受け38のボス部端面44とラチエツト35の
ボス部端面45との透き間46がほとんどなくなるよう
に前記ボス部47,48を突出したため、出力軸14の
トルクが増大しても、ラチエツト36は軸方に移動出来
ない。In addition, by making the rising angle of the chevron-shaped protruding surface different in the forward rotation direction and the reverse rotation direction, the transmitted torque during turning and reverse rotation can be changed. 2) When the spring receiver 38 is moved to the ratchet 36 side by the maximum amount by rotating the adjustment cylinder 33, the gap 46 between the boss end face 44 of the spring receiver 38 and the boss end face 45 of the ratchet 35 is almost eliminated. Since the boss portions 47 and 48 are projected, the ratchet 36 cannot be moved in the axial direction even if the torque of the output shaft 14 increases.
したがつて太陽歯車23も回転出来ずトルク調整不可の
状態を達成出来る。3)太陽歯車23を軸支する部分4
9と、ラチエツト36及びバネ受け38が嵌合し回転不
可なるように内周面に凹部39を形成した部分をもつ一
体成形した歯車ケース20の内側に、遊星歯車減速部9
及びトルク調整機構部8を配設し、さらに駆動軸後端部
50の軸支を太陽歯車前端小内径部51に圧入固着され
たメタル34で支持させたため、駆動軸14の保持精度
が向上し、ドリルチャック12の振れが小さくなると共
に、トルク調整機構部8の外径が小さく出来るので、作
業時にドリルチャック12先端に把持されたビット13
の先端が硬認し易すく使い勝手が良いという効果がある
。4) 遊星歯車減速部9の出力フランジ26と出力軸
14との接続を、インボリュートスプライン接手により
結合したため、遊星歯車減速部9とトルク調整機構部8
の分割が出来るので、組立時にはそれぞれ部分組立が可
能となり組立し易すくなる。Therefore, the sun gear 23 also cannot rotate and a state in which torque cannot be adjusted can be achieved. 3) Portion 4 that pivotally supports the sun gear 23
A planetary gear reduction part 9 is installed inside a gear case 20 which is integrally molded and has a recess 39 formed on the inner peripheral surface so that the ratchet 36 and spring receiver 38 fit together and cannot rotate.
and torque adjustment mechanism 8 are provided, and the shaft support of the rear end portion 50 of the drive shaft is supported by the metal 34 press-fitted into the small inner diameter portion 51 of the front end of the sun gear, so that the holding accuracy of the drive shaft 14 is improved. Since the deflection of the drill chuck 12 is reduced and the outer diameter of the torque adjustment mechanism section 8 can be made small, the bit 13 held at the tip of the drill chuck 12 during work can be reduced.
The tip has the effect of being easy to recognize and easy to use. 4) Since the output flange 26 of the planetary gear reduction section 9 and the output shaft 14 are connected by an involute spline joint, the planetary gear reduction section 9 and the torque adjustment mechanism section 8 are connected.
Since it can be divided into parts, each part can be assembled at the time of assembly, making assembly easier.
又、組立費用も部分組立出来るので低減できる。尚分解
修理においても同様の効果を期特出来る。さらにインボ
リュートスプライン接手の採用により、自動調心性が働
き、第2の遊星歯車27は太陽歯車23と円滑にかみ合
い、歯面の片当りが防止出来るため、寿命が長くなると
共に、かみ合騒音が低くなるという効果がある。(5)
調整筒33の後端外径部52にハウジング1,2前端部
53と枢着する部分を設け、該ハウジング1,2に挟持
されるように支持したので、調整筒33取り付け部品点
数削減及びコスト低減を計れる。Furthermore, assembly costs can be reduced because partial assembly is possible. A similar effect can be expected in disassembly and repair. Furthermore, by adopting an involute spline joint, self-aligning properties work, and the second planetary gear 27 meshes smoothly with the sun gear 23, preventing uneven contact between the tooth surfaces, resulting in longer life and lower meshing noise. It has the effect of becoming. (5)
A portion that pivots to the front end portion 53 of the housings 1 and 2 is provided on the outer diameter portion 52 of the rear end of the adjustment tube 33, and is supported so as to be sandwiched between the housings 1 and 2, thereby reducing the number of parts to be attached to the adjustment tube 33 and reducing costs. You can measure the reduction.
さらに、調整筒33の内径と歯車ケース20の前側部外
径との嵌合部分54か軸方向に長くとれるので、調整筒
33の保持精度が向上し、ガタが少なくなることにより
出力軸14のガタ付きが抑止出来る。又、調整筒33で
トルク調整部8全体をおおうようにしたため、トルク調
整部8の防じん性が向上するという効果がある。Furthermore, since the fitting portion 54 between the inner diameter of the adjustment cylinder 33 and the outer diameter of the front side of the gear case 20 can be made longer in the axial direction, the holding accuracy of the adjustment cylinder 33 is improved, and play is reduced, so that the output shaft 14 It can prevent rattling. Further, since the entire torque adjustment section 8 is covered with the adjustment tube 33, there is an effect that the dust resistance of the torque adjustment section 8 is improved.
第1図は本発明の実施例を適用した電動ドライバーの外
観側面図、第2図はその一部縦断側面図、第3図は第2
図のトルク調整部及び差動遊星歯車減速部の詳細な縦断
側面図で締付トルクが1番弱い状態を示す。
第4図は第3図のトルク調整部及び差動遊星歯車減速部
の詳細な縦断側面図でトルク調整不可の状態を示す、第
5図はトルク調整部及び差動遊星歯車減速部の分解斜視
図、第6 ψIn図は第
3図及び第4図のA−A線断面図、第7図は太陽歯車及
びラチエツトの山形突起部のかみ合状態を示す拡大側面
図、第8図は出力フランジと出力軸の嵌合部を示す拡大
断面図、第9図は従来のトルク調整部の縦断側面図、第
10図は第9図の分解斜視図である。
図においては、1,2はハウジング(外枠)、7はモー
ター、8はトルク調整部、9は差動遊星歯車減速部、1
4は出力軸、20は歯車ケース、22は山形突起部、2
3は太陽歯車、26は出力フランジ、28はインボリュ
ートスプライン接手、32はボールベアリング、33は
調整筒、34はメタル、35は山形突起、36はラチエ
ツト、37はクラッチバネ、38はバネ受け、39は凹
部、40は凸部、41は案内カム、46は透き間、47
はバネ受けのボス部、48はラチエツトのボス部、49
は太陽歯車の外径部、55は太陽歯車の前端面周縁部、
56はラチエツトの後端面周縁部、57は調整筒とバネ
受けの嵌合部である。Fig. 1 is an external side view of an electric screwdriver to which an embodiment of the present invention is applied, Fig. 2 is a partially vertical side view thereof, and Fig. 3 is a second
The detailed longitudinal side view of the torque adjustment section and the differential planetary gear reduction section shown in the figure shows a state where the tightening torque is at its lowest. Fig. 4 is a detailed vertical side view of the torque adjustment section and differential planetary gear reduction section shown in Fig. 3, showing a state where torque adjustment is not possible. Fig. 5 is an exploded perspective view of the torque adjustment section and differential planetary gear reduction section. Fig. 6 ψIn is a sectional view taken along the line A-A in Figs. 3 and 4, Fig. 7 is an enlarged side view showing the engaged state of the chevron-shaped protrusions of the sun gear and ratchet, and Fig. 8 is the output flange. FIG. 9 is a longitudinal sectional side view of a conventional torque adjusting section, and FIG. 10 is an exploded perspective view of FIG. 9. In the figure, 1 and 2 are housings (outer frames), 7 is a motor, 8 is a torque adjustment section, 9 is a differential planetary gear reduction section, 1
4 is the output shaft, 20 is the gear case, 22 is the chevron-shaped protrusion, 2
3 is a sun gear, 26 is an output flange, 28 is an involute spline joint, 32 is a ball bearing, 33 is an adjustment tube, 34 is a metal, 35 is a chevron projection, 36 is a ratchet, 37 is a clutch spring, 38 is a spring receiver, 39 40 is a concave portion, 41 is a guide cam, 46 is a gap, 47
48 is the boss of the spring holder, 49 is the boss of the ratchet, and 49 is the boss of the ratchet.
55 is the outer diameter portion of the sun gear; 55 is the peripheral edge of the front end surface of the sun gear;
Reference numeral 56 represents a peripheral edge of the rear end surface of the ratchet, and reference numeral 57 represents a fitting portion between the adjustment cylinder and the spring receiver.
Claims (1)
速装置の太陽歯車を抑止し、前記減速装置の出力側に取
りつけられた出力軸に一定トルクを与えるクラッチ機構
付電動ドライバーにおいて、前記太陽歯車23の前端面
周縁部55に複数個の山形突起部22,22,・・・を
形成し、これに対向して、前記山形突起部22,22,
・・・と噛合する突起部35,35,・・・を後端面周
縁部56に備え、複数個の放射状凸部40,40,・・
・を外周縁部に形成したラチエツト36を配設し、該ラ
チエツト36に隣接して前記突起部22,35を圧接付
勢するクラッチバネ37を配設すると共に、前記外枠の
先端部には、前記クラッチバネ37を支持するバネ受け
38を介して前記クラッチバネ37の付勢力を調整する
調整筒33を枢着し、前記バネ受け38と前記調整筒3
3との係合部57には階段状の案内カム41,41を成
形し、前記バネ受け38の外周部には複数個の放射状凸
部40,40,・・・を成形して成り、前記調整筒33
の回動操作により前記クラッチバネ37の付勢力を調整
可能に構成したことを特徴とするトルク調整装置。 2 前記太陽歯車23の外周部49を軸支すると共に、
前記ラチエツト36とバネ受け38の放射状凸部40に
嵌合する凹部39を内径に一体成形した歯車ケース20
で前記太陽歯車23,ラチエツト36,クラッチバネ3
7,バネ受け38とを把持してなる特許請求の範囲第1
項記載のトルク調整装置。 3 前記出力軸14の前端部は、ボールベアリング32
を介して調整筒33に保持され、後端部は前記太陽歯車
23の内周面に圧入固着されたメタル34で軸支され、
かつ前記差動遊星歯車減速装置の出力フランジ26とは
インボリュートスプライン接手28により嵌着してなる
特許請求の範囲第1項記載のトルク調整装置。 4 前記調整筒33とバネ受け38の階段状の案内カム
41により、前記バネ受け38を軸方向に移動し前記ク
ラッチバネ37の押圧力を調整する場合において、モー
ター7の最大回転力を前記出力軸14に伝達するため、
上記最大回転力が加わつた時前記太陽歯車23とラチエ
ツト36の山形突起部22、35が離脱不可となるよう
に、前記バネ受け38のボス部47に対向した前記ラチ
エツト36のボス部48を当接してなる特許請求の範囲
第1項記載のトルク調整装置。[Scope of Claims] 1. A clutch mechanism that suppresses the rotational force of a motor housed in an outer frame from the sun gear of a differential planetary gear reduction device and applies a constant torque to an output shaft attached to the output side of the reduction device. In the electric screwdriver with an attached electric screwdriver, a plurality of chevron-shaped protrusions 22, 22, .
The rear end surface peripheral edge part 56 is provided with protrusions 35, 35, .
A clutch spring 37 is provided adjacent to the ratchet 36 for pressing the projections 22, 35 into contact with each other, and a clutch spring 37 is provided adjacent to the ratchet 36. , an adjustment tube 33 for adjusting the biasing force of the clutch spring 37 is pivotally connected via a spring receiver 38 that supports the clutch spring 37, and the spring receiver 38 and the adjustment tube 3
Step-shaped guide cams 41, 41 are molded on the engagement portion 57 with the spring receiver 38, and a plurality of radial convex portions 40, 40, . . . are molded on the outer peripheral portion of the spring receiver 38. Adjustment tube 33
A torque adjusting device characterized in that the biasing force of the clutch spring 37 can be adjusted by a rotational operation. 2 pivotally supports the outer peripheral portion 49 of the sun gear 23, and
A gear case 20 whose inner diameter is integrally formed with a recess 39 that fits into the radial convex portion 40 of the ratchet 36 and spring receiver 38.
The sun gear 23, ratchet 36, clutch spring 3
7.Claim 1, which is formed by gripping the spring receiver 38
Torque adjustment device as described in section. 3 The front end of the output shaft 14 is connected to a ball bearing 32.
The rear end portion is supported by a metal 34 that is press-fitted into the inner circumferential surface of the sun gear 23.
2. The torque adjusting device according to claim 1, wherein the output flange 26 of the differential planetary gear reduction device is fitted with an involute spline joint 28. 4 When adjusting the pressing force of the clutch spring 37 by moving the spring receiver 38 in the axial direction using the adjustment cylinder 33 and the stepped guide cam 41 of the spring receiver 38, the maximum rotational force of the motor 7 is adjusted to the output. In order to transmit to the shaft 14,
The boss portion 48 of the ratchet 36 facing the boss portion 47 of the spring receiver 38 is pressed so that the sun gear 23 and the chevron-shaped protrusions 22, 35 of the ratchet 36 cannot be separated when the maximum rotational force is applied. A torque adjusting device according to claim 1, which is in contact with the torque adjusting device of claim 1.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56204737A JPS6051999B2 (en) | 1981-12-17 | 1981-12-17 | Electric screwdriver torque adjustment device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56204737A JPS6051999B2 (en) | 1981-12-17 | 1981-12-17 | Electric screwdriver torque adjustment device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS58109275A JPS58109275A (en) | 1983-06-29 |
JPS6051999B2 true JPS6051999B2 (en) | 1985-11-16 |
Family
ID=16495472
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP56204737A Expired JPS6051999B2 (en) | 1981-12-17 | 1981-12-17 | Electric screwdriver torque adjustment device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6051999B2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016121460A1 (en) * | 2015-01-29 | 2016-08-04 | 日立工機株式会社 | Screw-tightening device |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5136315U (en) * | 1974-09-10 | 1976-03-18 | ||
JPS5656313A (en) * | 1979-10-15 | 1981-05-18 | Matsushita Electric Works Ltd | Electric tool |
-
1981
- 1981-12-17 JP JP56204737A patent/JPS6051999B2/en not_active Expired
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5136315U (en) * | 1974-09-10 | 1976-03-18 | ||
JPS5656313A (en) * | 1979-10-15 | 1981-05-18 | Matsushita Electric Works Ltd | Electric tool |
Also Published As
Publication number | Publication date |
---|---|
JPS58109275A (en) | 1983-06-29 |
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